WO2003004877A1 - Side channel compressor - Google Patents

Side channel compressor Download PDF

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Publication number
WO2003004877A1
WO2003004877A1 PCT/EP2002/007031 EP0207031W WO03004877A1 WO 2003004877 A1 WO2003004877 A1 WO 2003004877A1 EP 0207031 W EP0207031 W EP 0207031W WO 03004877 A1 WO03004877 A1 WO 03004877A1
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WO
WIPO (PCT)
Prior art keywords
side channel
conveyed
medium
interrupter
impeller
Prior art date
Application number
PCT/EP2002/007031
Other languages
German (de)
French (fr)
Inventor
Thomas Grohmann
Original Assignee
Siemens Aktiengesellschaft
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens Aktiengesellschaft filed Critical Siemens Aktiengesellschaft
Publication of WO2003004877A1 publication Critical patent/WO2003004877A1/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
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/624—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/626—Mounting or removal of fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D23/00—Other rotary non-positive-displacement pumps
    • F04D23/008—Regenerative pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/51—Inlet

Definitions

  • the invention relates to a side channel compressor.
  • a generic side channel compressor sets the medium to be conveyed in a helical movement. In the further course in the circumferential direction of the side channel compressor this leads to an increase in pressure of the medium to be conveyed. To achieve good efficiency, it is necessary that the medium executes the corresponding helical movement as quickly and as quickly as possible after it has entered the side channel compressor.
  • the functional principle requires that the suction and pressure sides be separated by means of an interrupter. Due to the design, part of the medium to be compressed is continuously transported from the pressure side to the suction side via the interrupter during the compression process. At the breaker outlet of the impeller, i.e. in the area of the suction side, the pressure difference between the medium conveyed and the medium sucked in occurs in the side channel inlet, that is, in the region of the suction side, an expansion of the medium conveyed occurs. This expansion causes gas dynamic effects, which include lead to local impacts.
  • the interrupter With open impellers as known from DE 77 12 419, the interrupter is in two parts, i. H. on the one hand, it sits on the side of the impeller like the closed impeller. It is also located radially outside the impeller blades.
  • the medium conveyed by the interrupter is expanded in the same way as for interrupters on the closed impeller.
  • the expansion of the conveyed medium in the lower part of the breaker is based on the same principle of the side breaker.
  • the relaxation effects also occur radially outwards.
  • it is more difficult to fill the blade cells compared to the closed impellers since the centrifugal force on the medium to be pumped, for example. Gas acts and it is hardly possible to evenly fill, in particular the second passages of the side channel blower.
  • the invention is therefore based on the object of avoiding the abovementioned disadvantages in side-channel compressors, in particular with an open impeller, and also to reduce the expansion of the medium conveyed by the interrupter. so that refilling of the side channel is no longer impaired by the effects of relaxation.
  • a ' double-flow side channel compressor with at least one impeller, which is equipped with outward-pointing impeller blades and when the impeller rotates in the circumferential direction, a gaseous medium to be conveyed is compressed in the side channel, with an interrupter for separating suction - And pressure side, wherein means are available to reduce the relaxation effects, in particular of the medium conveyed via the interrupter to the suction side.
  • the medium to be conveyed is filled laterally and / or radially into the side channel during the filling.
  • the medium to be conveyed is immediately accelerated by the rotary movement and placed in the spiral path required for the pulse exchange radial filling, the formation of the spiral flow is initially prevented, since the medium entering cannot be accelerated by the impeller.
  • the medium to be conveyed is also preferably to be fed in laterally there. Due to the improved expansion behavior compared to conventional side channel compressors due to a slower gap enlargement, starting from the interrupter to the actual side channel, the medium to be pumped is guided in the circumferential direction and the energy released by the expansion can be used to drive the impeller according to a turbine principle , The dissipations caused by the interrupter are thus minimized and the efficiency of the side channel blower increases. The optimized expansion behavior also reduces noise. Further advantageous refinements can be found in the subclaims.
  • FIG. 1 shows a partial cross section of a side channel compressor
  • FIG. 2 shows a further cross section through the side channel of the compressor
  • FIG. 3 shows a molded part in the area of the suction side of the side channel compressor
  • FIG. 4 shows another molded part in the area of the suction part of the compressor.
  • 1 shows a side channel compressor, not shown. 1 shows the area of an interrupter 1 in the area of the suction side 2 of the side channel compressor and part of an impeller 3 with impeller blades 4.
  • the impeller blades 4 form individual ones
  • the compressed medium is e.g. Gas emitted.
  • a mass flow which is also conveyed is conveyed via the interrupter 1 to the suction side.
  • the gas that was also conveyed would now expand. This expansion is reduced by a slide-in plate or a cast-on web on the interrupter 6. This facilitates the supply of the medium to be conveyed in this area.
  • FIG. 2 shows another representation of the double-flow side channel 7 with the floods 7.1 and 7.2, in which the impeller 3 with its impeller blades 4 moves.
  • the medium to be pumped flows from the suction side 2 into the side channel.
  • the medium to be conveyed can thus penetrate both the first flood 8 and the second flood 9 almost unhindered and can immediately be set in the spiral rotation of the impeller 3.
  • FIG 3 shows an exemplary embodiment of a web or insert plate 6, which can be inserted or inserted into grooves 10 of the housing 11 of the side channel compressor.
  • the insertion of the web or insert plate 6 into the grooves is facilitated by the housing 11 being constructed in several parts.

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

Abstract

The invention relates to a side channel compressor comprising an open running wheel (3). The effects of a drop in pressure in the region of the suctioning side (2) are reduced by means of a double-flow side channel compressor with at least one running wheel (3) provided with blades (4), said blades being orientated towards the outside thereof. When the running wheel (3) rotates in the circumferential direction, the gaseous medium which is conveyed in the side channel (7) is compressed. Said compressor also comprises a interrupter (1) which separates the suctioning side and the pressure side, and means (6) are provided to reduce the effects of a drop in pressure, especially with respect to the medium conveyed to the suction side (2) by the interrupter (1).

Description

Beschreibung description
SeitenkanalverdichterSide Channel Blowers
Die Erfindung betrifft einen Seitenkanalverdichter.The invention relates to a side channel compressor.
Ein gattungsgemäßer Seitenkanalverdichter versetzt das zu fördernde Medium in eine schraubenförmige Bewegung. Dies führt im weiteren Verlauf in Umfangsrichtung des Seitenkanal- Verdichters zu einer Druckerhöhung des zu fördernden Mediums. Zur Erzielung eines guten Wirkungsgrades ist es notwendig, dass das Medium nach seinem Eintritt in den Seitenkanalverdichter auf kürzestem Weg und möglichst schnell die entsprechende schraubenförmige Bewegung ausführt.A generic side channel compressor sets the medium to be conveyed in a helical movement. In the further course in the circumferential direction of the side channel compressor this leads to an increase in pressure of the medium to be conveyed. To achieve good efficiency, it is necessary that the medium executes the corresponding helical movement as quickly and as quickly as possible after it has entered the side channel compressor.
Bei Seitenkanalverdichtern ist es aufgrund des Funktionsprinzips eine Trennung der Saug- und Druckseite mittels Unterbrecher erforderlich. Während des Verdichtungsvorgangs wird konstruktionsbedingt kontinuierlich ein Teil des zu verdichten- den Mediums über den Unterbrecher von der Druck- zur Saugseite transportiert. Am Unterbrecheraustritt des Laufrades, d.h. im Bereich der Saugseite tritt in Folge des Druckunterschie- des zwischen dem mitgeförderten Medium und dem angesaugten Medium im Seitenkanaleintritt, also im Bereich der Saugseite eine Expansion des mitgeförderten Mediums auf. Diese Expansion verursacht gasdynamische Effekte, die u.a. zu örtlichen Verdichtungsstößen führen.In the case of side channel compressors, the functional principle requires that the suction and pressure sides be separated by means of an interrupter. Due to the design, part of the medium to be compressed is continuously transported from the pressure side to the suction side via the interrupter during the compression process. At the breaker outlet of the impeller, i.e. in the area of the suction side, the pressure difference between the medium conveyed and the medium sucked in occurs in the side channel inlet, that is, in the region of the suction side, an expansion of the medium conveyed occurs. This expansion causes gas dynamic effects, which include lead to local impacts.
Diese Effekte verschlechtern die Befüllung des Seitenkanal- Verdichters mit einem zu fördernden Medium, da die Expansion diesem Eintritt des zu fördernden Mediums entgegenwirkt.These effects worsen the filling of the side channel compressor with a medium to be conveyed, since the expansion counteracts this entry of the medium to be conveyed.
Außerdem sind sie mit verantwortlich für die starke Geräuschbildung im Seitenkanalverdichter. Es wird dadurch zusätzlich der Wirkungsgrad des Seitenkanalverdichters verschlechtert. Bei Seitenkanalverdichtern mit geschlossenen Laufrädern wie aus DE 19 21 945 bekannt, sitzt der Unterbrecher seitlich des Laufrades und das zu fördernde Medium expandiert am Unterbrecher schlagartig in den Bereich in den das zu fördernde Medi- um in den Seitenkanal eintritt. Um dies zu verhindern, wird versucht, die schlagartige Entspannung des durch den Unterbrecher mitgeförderten Mediums und die daraus resultierende Dissipation durch Entspannungsnuten am Unterbrecher zu vermindern. Trotz des nur seitlich vorhandenen Unterbrechers treten immer noch die meisten Dissipationen am Unterbrecheraustritt auf. Geschlossene Laufräder haben außerdem den Nachteil, dass die aufgrund der hohen Masse und Konzentration am Laufradaußendurchmesser nicht für hohe Drehzahlen geeignet sind.They are also responsible for the high level of noise generated in the side channel blower. As a result, the efficiency of the side channel blower is also impaired. In side channel compressors with closed impellers as known from DE 19 21 945, the interrupter is located on the side of the impeller and the medium to be conveyed expands abruptly into the area into which the medium to be conveyed enters the side channel. In order to prevent this, an attempt is made to reduce the sudden relaxation of the medium conveyed by the interrupter and the resulting dissipation through relaxation grooves on the interrupter. Despite the breaker, which is only on the side, most dissipations still occur at the breaker exit. Closed impellers also have the disadvantage that they are not suitable for high speeds due to the high mass and concentration on the outer diameter of the impeller.
Bei offenen Laufrädern wie aus der DE 77 12 419 bekannt, ist der Unterbrecher zweiteilig, d. h. er sitzt einerseits wie bei dem geschlossenen Laufrad seitlich des Laufrades . Außerdem befindet er sich radial außerhalb der Laufradschaufeln . Eine Expansion des durch den Unterbrecher mitgeförderten Mediums erfolgt auf dieselbe Weise wie bei Unterbrechern am geschlossenen Laufrad. Die Entspannung des mitgeförderten Mediums im unteren Teil des Unterbrechers erfolgt nach dem gleichen Prinzip des seitlichen Unterbrechers . Im Gegenteil zum ge- schlossenen Laufrad treten die Entspannungseffekte auch radial nach außen auf . Bei offenen Lauf rädern erschwert sich im Vergleich zu den geschlossenen Laufrädern die Befüllung der Schaufelzellen, da die radial auftretende Fliehkraftwirkung auf das zu fördernde Medium z .B . Gas wirkt und eine gleichmä- ßige Befüllung insbesondere der zweiten Fluten des Seitenka- nalverdichters kaum möglich ist .With open impellers as known from DE 77 12 419, the interrupter is in two parts, i. H. on the one hand, it sits on the side of the impeller like the closed impeller. It is also located radially outside the impeller blades. The medium conveyed by the interrupter is expanded in the same way as for interrupters on the closed impeller. The expansion of the conveyed medium in the lower part of the breaker is based on the same principle of the side breaker. In contrast to the closed impeller, the relaxation effects also occur radially outwards. In the case of open impellers, it is more difficult to fill the blade cells compared to the closed impellers, since the centrifugal force on the medium to be pumped, for example. Gas acts and it is hardly possible to evenly fill, in particular the second passages of the side channel blower.
Der Erfindung liegt demnach die Aufgabe zugrunde, bei Seitenkanalverdichtern, insbesondere mit offenem Laufrad die oben- genannten Nachteile zu vermeiden, und außerdem die Expansion des mitgeförderten Mediums durch den Unterbrecher zu reduzie- ren, so dass eine Neubefüllung des Seitenkanals nicht mehr durch auftretende Entspannungseffekte beeinträchtigt wird.The invention is therefore based on the object of avoiding the abovementioned disadvantages in side-channel compressors, in particular with an open impeller, and also to reduce the expansion of the medium conveyed by the interrupter. so that refilling of the side channel is no longer impaired by the effects of relaxation.
Die Lösung der gestellten Aufgabe gelingt durch einen ' zweiflutigen Seitenkanalverdichter mit zumindest einem Laufrad, das mit nach außen weisenden Laufradschaufeln besetzt ist und sich bei Drehung des Laufrades in Umfangsrichtung eine Verdichtung eines zu fördernden gasförmigen Mediums im Seitenkanal ergibt, mit einem Unterbrecher zur Trennung von Saug- und Druckseite, wobei Mittel vorhanden sind, die Entspannungseffekte insbesondere des über den Unterbrecher zur Saugseite mitgeförderten Mediums reduzieren.The problem is solved by a ' double-flow side channel compressor with at least one impeller, which is equipped with outward-pointing impeller blades and when the impeller rotates in the circumferential direction, a gaseous medium to be conveyed is compressed in the side channel, with an interrupter for separating suction - And pressure side, wherein means are available to reduce the relaxation effects, in particular of the medium conveyed via the interrupter to the suction side.
Das zu fördernde Medium wird erfindungsgemäß bei der Befül-" lung seitlich und/oder radial in den Seitenkanal eingeströmt. Bei der seitlichen Befüllung wird das zu fördernde Medium durch die Drehbewegung sofort beschleunigt und in die für den Impulsaustausch erforderliche spiralförmige Bahn versetzt wird. Bei der radialen Befüllung wird die Ausbildung der spi- ralförmigen Strömung vorerst verhindert, da das eintretende Medium nicht durch das Laufrad beschleunigt werden kann.According to the invention, the medium to be conveyed is filled laterally and / or radially into the side channel during the filling. When the filling is carried out from the side, the medium to be conveyed is immediately accelerated by the rotary movement and placed in the spiral path required for the pulse exchange radial filling, the formation of the spiral flow is initially prevented, since the medium entering cannot be accelerated by the impeller.
Es wird außerdem das Befüllen der zweiten Flut des Seitenka- nalverdichters erleichtert, da das zu fördernde Medium auch dorthin vorzugsweise seitlich zuzuführen ist. Durch das gegenüber herkömmlichen Seitenkanalverdichtern verbesserte Expansionsverhalten durch eine insbesondere langsamere Spaltvergrößerung, ausgehend vom Unterbrecher bis zum eigentlichen Seitenkanal, wird das zu fördernde Medium somit in Umfangs- richtung geführt und die durch die Expansion frei werdende Energie kann gemäß einem Turbinenprinzip zum Antrieb des Laufrades genutzt werden. Die Dissipationen, verursacht durch den Unterbrecher minimieren sich somit und der Wirkungsgrad des Seitenkanalverdichters steigt. Das optimierte Expansions- verhalten reduziert außerdem die Geräuschentwicklung. Weitere vorteilhafte Ausgestaltungen sind den Unteransprüclien zu entnehmen.It is also easier to fill the second flow of the side channel compressor, since the medium to be conveyed is also preferably to be fed in laterally there. Due to the improved expansion behavior compared to conventional side channel compressors due to a slower gap enlargement, starting from the interrupter to the actual side channel, the medium to be pumped is guided in the circumferential direction and the energy released by the expansion can be used to drive the impeller according to a turbine principle , The dissipations caused by the interrupter are thus minimized and the efficiency of the side channel blower increases. The optimized expansion behavior also reduces noise. Further advantageous refinements can be found in the subclaims.
Die Erfindung sowie weitere vorteilhafte Ausgestaltungen der Erfindung sind anhand der folgenden schematisch dargestellten Ausführungsbeispiele näher erläutert. Darin zeigen:The invention and further advantageous embodiments of the invention are explained in more detail with reference to the following schematically illustrated exemplary embodiments. In it show:
FIG 1 einen Teilquerschnitt eines Seitenkanalverdichters, FIG 2 einen weiteren Querschnitt durch den Seitenkanal des Verdichters,1 shows a partial cross section of a side channel compressor, FIG. 2 shows a further cross section through the side channel of the compressor,
FIG 3 ein Formteil im Bereich der Saugseite des Seitenkanalverdichters, FIG 4 ein weiteres Formteil im Bereich des Saugteils des Verdichters .3 shows a molded part in the area of the suction side of the side channel compressor, FIG. 4 shows another molded part in the area of the suction part of the compressor.
FIG 1 zeigt einen nicht näher dargestellten Seitenkanalverdichter. Der in FIG 1 dargestellte Ausschnitt zeigt den Bereich eines Unterbrechers 1 im Bereich der Saugseite 2 des Seitenkanalverdichters und ein Teil eines Laufrades 3 mit Laufradschaufeln 4. Die Laufradschaufeln 4 bilden einzelne1 shows a side channel compressor, not shown. 1 shows the area of an interrupter 1 in the area of the suction side 2 of the side channel compressor and part of an impeller 3 with impeller blades 4. The impeller blades 4 form individual ones
Kammern 5. Im Betrieb des Seitenkanalverdichters wird auf der nicht näher dargestellten Druckseite des Seitenkanalverdichters das verdichtete Medium z.B. Gas ausgestoßen. Über die Kammern 5 die durch den Unterbrecher 1 führen, wird aber ein mitgeförderter Massestrom über den Unterbrecher 1 zur Saugseite gefördert. Auf der Saugseite 2 würde nunmehr das mitgeförderte Gas expandieren. Durch ein Einschubblech oder einen angegossenen Steg am Unterbrecher 6 wird diese Expansion verringert. Dies erleichtert die Zufuhr des zu fördernden Medi- ums in diesem Bereich.Chambers 5. During operation of the side channel compressor, the compressed medium is e.g. Gas emitted. Via the chambers 5 leading through the interrupter 1, however, a mass flow which is also conveyed is conveyed via the interrupter 1 to the suction side. On the suction side 2, the gas that was also conveyed would now expand. This expansion is reduced by a slide-in plate or a cast-on web on the interrupter 6. This facilitates the supply of the medium to be conveyed in this area.
FIG 2 zeigt in einer anderen Darstellung den zweiflutigen Seitenkanal 7 mit den Fluten 7.1 und 7.2, in dem sich das Laufrad 3 mit seinen Laufradschaufeln 4 bewegt. Von der Saug- seite 2 strömt wie durch Pfeile dargestellt das zu fördernde Medium in den Seitenkanal. Durch den Steg 6 ist eine Expansion des über den Unterbrecher 1 mitgeförderten Gases nicht möglich. Das zu fördernde Medium kann somit sowohl in die erste Flut 8 als auch in die zweite Flut 9 nahezu ungehindert eindringen und sofort in die spiralförmige Rotation des Laufrades 3 versetzt werden.2 shows another representation of the double-flow side channel 7 with the floods 7.1 and 7.2, in which the impeller 3 with its impeller blades 4 moves. As shown by arrows, the medium to be pumped flows from the suction side 2 into the side channel. Through the web 6 there is no expansion of the gas conveyed via the interrupter 1 possible. The medium to be conveyed can thus penetrate both the first flood 8 and the second flood 9 almost unhindered and can immediately be set in the spiral rotation of the impeller 3.
FIG 3 zeigt eine beispielhafte Ausführung eines Steges bzw. Einschubbleches 6, das in Nuten 10 des Gehäuses 11 des Seitenkanalverdichters eingeschoben bzw. eingesetzt werden kann. Das Einsetzen des Steges bzw. Einschubbleches 6 in die Nuten wird erleichtert, in dem das Gehäuse 11 mehrteilig aufgebaut ist.3 shows an exemplary embodiment of a web or insert plate 6, which can be inserted or inserted into grooves 10 of the housing 11 of the side channel compressor. The insertion of the web or insert plate 6 into the grooves is facilitated by the housing 11 being constructed in several parts.
FIG 4 zeigt die Möglichkeit wie der Unterbrecher 1, der als Gussteil ausgeführt ist, durch eine Verlängerung 1.1 in den Bereich der Saugseite eine Expansion des mitgeförderten Mediums verhindert und somit den Wirkungsgrad des Seitenkanalverdichters erhöht . 4 shows the possibility of how the interrupter 1, which is designed as a cast part, prevents expansion of the medium conveyed by an extension 1.1 in the area of the suction side and thus increases the efficiency of the side channel compressor.

Claims

Patentansprüche claims
1. Zweiflutiger Seitenkanalverdichter mit zumindest einem Laufrad (3), das mit nach außen weisenden Laufradschaufeln (4) besetzt ist und sich bei Drehung des Laufrades (3) in Um- fangsrichtung eine Verdichtung eines zu fördernden gasförmigen Mediums im Seitenkanal (7) ergibt, mit einem Unterbrecher (1) zur Trennung von Saug- und Druckseite, wobei Mittel vorhanden sind, die Entspannungseffekte insbesondere des über den Unterbrecher (1) zur Saugseite mitgeförderten Mediums reduzieren.1. double-flow side channel compressor with at least one impeller (3) which is equipped with outward-pointing impeller blades (4) and when the impeller (3) rotates in the circumferential direction, a gaseous medium to be conveyed is compressed in the side channel (7), with an interrupter (1) for separating the suction and pressure side, means being provided to reduce the relaxation effects, in particular of the medium conveyed to the suction side via the interrupter (1).
2. Zweiflutiger Seitenkanalverdichter nach Anspruch 1, d a d u r c h g e k e n n z e i c h n e t , dass die Mittel derart gestaltet sind, dass nur eine seitliche Einströmung des zu fördernden Mediums in den Seitenkanal (7) im Bereich der Saugseite möglich ist.2. Double-flow side channel compressor according to claim 1, d a d u r c h g e k e n e z e i c h n e t that the means are designed such that only a lateral inflow of the medium to be conveyed into the side channel (7) in the area of the suction side is possible.
3. Zweiflutiger Seitenkanalverdichter nach Anspruch 1 oder 2, d a d u r c h g e k e n n z e i c h n e t , dass sich ein Einschubelement (6) radial außerhalb des Laufrades (3) insbesondere im Bereich der Saugseite befindet.3. Double-flow side channel compressor according to claim 1 or 2, so that a slide element (6) is located radially outside the impeller (3), in particular in the area of the suction side.
4. Zweiflutiger Seitenkanalverdichter nach Anspruch 1 oder 2, d a d u r c h g e k e n n z e i c h n e t , dass ein radial außerhalb der Laufradschaufeln (4) befindlicher Formteil als Teil des Gehäuses des Seitenkanalverdichters ausgebildet ist. 4. Double-flow side channel compressor according to claim 1 or 2, so that a radially outside of the impeller blades (4) molded part is formed as part of the housing of the side channel compressor.
PCT/EP2002/007031 2001-07-06 2002-06-26 Side channel compressor WO2003004877A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10132805.2 2001-07-06
DE10132805A DE10132805A1 (en) 2001-07-06 2001-07-06 Side Channel Blowers

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8150748B1 (en) * 2006-08-09 2012-04-03 United Services Automobile Association (Usaa) Systems and methods for dynamic configuration of software agents for transfer operations

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2724338A (en) * 1949-05-19 1955-11-22 Roth Co Roy E Combination centrifugal-turbine pump
US3788766A (en) * 1971-06-26 1974-01-29 Siemens Ag Ring canal blower
GB2068461A (en) * 1980-02-01 1981-08-12 Utile Eng Co Ltd Regenerative turbo machines
US4325672A (en) * 1978-12-15 1982-04-20 The Utile Engineering Company Limited Regenerative turbo machine
GB2239492A (en) * 1989-11-02 1991-07-03 Sundstrand Corp Side channel pump
DE19708953A1 (en) * 1997-03-05 1998-09-17 Busch Gmbh K Side channel compressor with bladed rotor wheel

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE902074C (en) * 1937-08-08 1954-01-18 Fritz Oesterlen Dr Ing Circulating compressor with a side channel coaxial to the impeller
US3095820A (en) * 1960-02-29 1963-07-02 Mcculloch Corp Reentry rotary fluid pump
DE7712419U1 (en) * 1977-04-20 1978-02-09 Siemens Ag, 1000 Berlin Und 8000 Muenchen SIDE CHANNEL COMPRESSOR
KR970005981B1 (en) * 1991-06-18 1997-04-22 가부시기가이샤 히다찌세이사뀨쇼 Vortex flow blower

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2724338A (en) * 1949-05-19 1955-11-22 Roth Co Roy E Combination centrifugal-turbine pump
US3788766A (en) * 1971-06-26 1974-01-29 Siemens Ag Ring canal blower
US4325672A (en) * 1978-12-15 1982-04-20 The Utile Engineering Company Limited Regenerative turbo machine
GB2068461A (en) * 1980-02-01 1981-08-12 Utile Eng Co Ltd Regenerative turbo machines
GB2239492A (en) * 1989-11-02 1991-07-03 Sundstrand Corp Side channel pump
DE19708953A1 (en) * 1997-03-05 1998-09-17 Busch Gmbh K Side channel compressor with bladed rotor wheel

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8150748B1 (en) * 2006-08-09 2012-04-03 United Services Automobile Association (Usaa) Systems and methods for dynamic configuration of software agents for transfer operations

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