EP0863314B1 - Compresseur à canal latéral effilé - Google Patents

Compresseur à canal latéral effilé Download PDF

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Publication number
EP0863314B1
EP0863314B1 EP98103724A EP98103724A EP0863314B1 EP 0863314 B1 EP0863314 B1 EP 0863314B1 EP 98103724 A EP98103724 A EP 98103724A EP 98103724 A EP98103724 A EP 98103724A EP 0863314 B1 EP0863314 B1 EP 0863314B1
Authority
EP
European Patent Office
Prior art keywords
side channel
cross
section
channel
flow guide
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.)
Revoked
Application number
EP98103724A
Other languages
German (de)
English (en)
Other versions
EP0863314A1 (fr
Inventor
Reinhard Garczorz
Andreas Dr.-Ing. Basteck
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Dr-Ing K Busch GmbH
Original Assignee
Dr-Ing K Busch GmbH
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
Family has litigation
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Application filed by Dr-Ing K Busch GmbH filed Critical Dr-Ing K Busch GmbH
Publication of EP0863314A1 publication Critical patent/EP0863314A1/fr
Application granted granted Critical
Publication of EP0863314B1 publication Critical patent/EP0863314B1/fr
Anticipated expiration legal-status Critical
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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
    • F04D23/00—Other rotary non-positive-displacement pumps
    • F04D23/008—Regenerative pumps

Definitions

  • the invention relates to a side channel compressor according to the preamble of the claim 1.
  • an eddy current fan with a housing has an annular flow passage extending from an inlet opening extends to receive fluid up to a fluid outlet opening.
  • a flow reducer is arranged in the flow passage. This achieved thereby a noise reduction that in the corresponding area between Inlet opening and outlet opening through a constantly reduced cross section of the flow passage resulting from the breaking off of the flow Turbulence can be avoided and consequently the occurrence of noise and a loss of pressure is prevented.
  • the predetermined section, in which the cross-section reducer is arranged again a cross-sectional expansion, thus no restricted air volume with accordingly reduced delivery rate is present.
  • DE-PS 876 285 describes a ring compressor or rotary compressor Side channel.
  • the cross section of the work area should correspond to the increasing Compaction and the decreasing specific volume of the conveyed material Decrease steadily along the circumference in the direction of rotation.
  • US 4,325,672 describes a side channel compressor for compressing, pumping or blowing air or other gases.
  • Corresponding rotor blades are designed such that a fluid flow with respect to the rotor blades An angle greater than 90 degrees results.
  • Document GB 606 127 describes a centrifuge blower with an annular channel, the cross section of which decreases from the inlet to the outlet.
  • the ring channel In the ring channel is an impeller with wing blades arranged such that when the impeller rotates the air inside the ring channel not only in the axial direction along the Ring channel but also rotates about an axis of the ring channel, so that the air repeatedly comes into the area of influence of the wing blades.
  • the cross-sectional reduction is designed so that it follows the compression of the material to be conveyed.
  • the invention is based, to eliminate the side channel blower the task to design the disadvantages described so that improved Efficiency an increase in volume flow with a uniform Pressure increase in the side channel results.
  • the side channel compressor designed according to the invention has a modified one Cross section of the side channel, in such a way that the cross section of the side channel tapers from the suction side towards the pressure side.
  • the cross-sectional taper of the side channel based on the cross-section on Gas inlet has a value in the range of 20% to 40%, so that the Cross section of the side channel from 130% at the gas inlet to 100% at the gas outlet rejuvenated. This surprisingly achieves an optimal improvement in efficiency.
  • cross section of the side channel is continuous or continuously rejuvenated.
  • this advantageous embodiment results from this embodiment according to the invention achieved that the enlarged channel cross-section in the suction area improved Expansion of the gas ensures that the pressure side through the interrupter entry. This means that a vacuum can also be achieved at a lower level and the suction power increases.
  • the side channel Housing cover an inward-pointing flow guide edge for the pumped Media arranged.
  • This flow guide edge is in the form of a tapered Rib formed, advantageously the cross section of the flow leading edge adapted to the tapering cross section of the side channel is.
  • the flow guide edge can be formed in one piece with the wall of the side channel his. Instead, the flow leading edge can also be on a separate Guide ring formed in the side channel at the corresponding desired Place used on the inner wall or attached there.
  • a side channel compressor has impeller equipped with blades, which is used to compress gases in one Housing is rotatable.
  • the housing is provided with a cover 1, which has a gas inlet 2 and a Has gas outlet 3 and, as can be clearly seen from Fig. 2, on the impeller facing side a side channel 4 limited.
  • the cross section of the side channel 4 is bowl-shaped and designed such that he from the gas inlet 2 (suction side) towards the gas outlet 3 (pressure side) rejuvenated.
  • the tapering of the side channel cross section takes place in the illustrated Embodiment continuously or continuously.
  • the cross-sectional taper is in the embodiment shown such that the cross section of the side channel 4 at the point D - D according to 1 in the manner shown in FIG. 6 is 130%. Tapered from here then the cross section of the side channel 4 steadily over 122% of the Interface C - C according to FIG. 1 (see FIG. 5) and over 107% at the interface B - B according to FIG. 1 (see FIG. 4) except for 100% at the interface A - A or near the gas outlet 3 (see Fig. 3).
  • a flow guide edge 5 which tapers conically is formed and points inward in the manner shown.
  • This flow leading edge 5 is formed in one piece with the wall of the side channel 4 and serves for the corresponding redirection of the flow of the media to be conveyed the outer area of the side channel 4. This will result in a better deflection the flow, which results in an efficiency improvement of 5 to 9%.
  • the formation of the flow leading edge 5 over the entire circumference of the side channel 4 is selected such that the cross section of the flow guide edge 5 on the tapering cross section of the side channel 4 is adapted.
  • the flow guide edge 5 is integrally formed with the wall of the side channel 4, is in the modified embodiment according to FIGS. 8 and 9 on the flow guide edge 5 a separate guide ring 6 is provided, which in the manner shown in FIG. 8 is formed and inserted into the interior of the side channel 4 or there is attached that the flow guide edge 5 in the same manner as in the previously described Embodiment according to FIG. 7 shows inwards.
  • This one too Embodiment becomes the same effect in efficiency improvement as achieved in the embodiment of FIG. 7.
  • FIGS. 10 and 11, 12 serve as a supplementary explanation the operation of a side channel blower and show schematically in Fig. 10 a side channel blower with a single ring impeller 7 in radial Type with a semicircular cross section of the side channel 4, wherein the side channel is formed in the housing or cover 1.
  • the in Fig. 10 The arrows shown represent the flow of the media to be pumped, in such a way that the open impeller 7 with its blades to be promoted Medium pushes out of the impeller 7 and this against the wall of the in the cover 1 side channel 4 presses. From there the flow becomes like this deflected that the medium to be conveyed is pressed into the impeller 7 again.
  • a so-called double-flow side channel compressor is provided.
  • the impeller 7 is formed with a double blade ring, one blade assembly from the other blade assembly is averted.
  • Each blade ring unit is a side channel 4, which on one Lid is arranged, assigned.
  • FIG. 13 shows a development of the side channel 4 on the suction or pressure side can be seen.
  • the cross section of the side channel 4 at the gas inlet 2 is separated from the gas outlet 3 by an interrupter web 8, opposite the Cross section near the gas outlet expanded by the amount that by the hatched area 9 is marked.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (6)

  1. Compresseur à canal latéral comportant un rotor pourvu d'aubes qui, pour la compression de gaz, est en rotation dans un boítier équipé d'un canal latéral (4), sur un côté d'aspiration étant prévu un orifice d'admission (2) et sur un côté de pression étant prévu un orifice de sortie (3) en liaison fluidique avec le canal latéral (4), et partant du côté d'aspiration (2), la section transversale du canal transversal (4) se rétrécissant depuis l'orifice d'admission (2) en direction du côté pression jusqu'à l'orifice de sortie (3),
    caractérisé en ce que le rétrécissement de la section transversale du canal latéral (4) par rapport à la section transversale à l'admission de gaz (2) a une valeur dans la plage de 20 % à 40 % de sorte que la section transversale du canal latéral (4) se rétrécit de 130 % à l'admission de gaz (2) jusqu'à 100 % à la sortie de gaz (3).
  2. Compresseur à canal latéral selon la revendication 1, caractérisé en ce que la section transversale du canal latéral (4) se rétrécit de manière continue.
  3. Compresseur à canal latéral selon l'une des revendications précédentes, caractérisé en ce que dans le canal latéral (4) du couvercle (1) de boítier est agencé un bord d'attaque d'écoulement (5) pour les fluides à transporter.
  4. Compresseur à canal latéral selon la revendication 3, caractérisé en ce que la section transversale du bord d'attaque d'écoulement (5) est adaptée à la section transversale se rétrécissant du canal latéral (4).
  5. Compresseur selon l'une ou l'autre des revendications 3 et 4, caractérisé en ce que le bord d'attaque d'écoulement (5) est réalisé d'un seul tenant avec la paroi du canal latéral (4).
  6. Compresseur selon l'une ou l'autre des revendications 3 et 4, caractérisé en ce que le bord d'attaque d'écoulement (5) est réalisé sur un anneau conducteur (6) qui est mis en place et fixé dans le canal latéral (4) avec le bord d'attaque d'écoulement (5) tourné vers l'intérieur.
EP98103724A 1997-03-05 1998-03-03 Compresseur à canal latéral effilé Revoked EP0863314B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19708952A DE19708952A1 (de) 1997-03-05 1997-03-05 Seitenkanalverdichter mit sich verjüngendem Kanalquerschnitt
DE19708952 1997-03-05

Publications (2)

Publication Number Publication Date
EP0863314A1 EP0863314A1 (fr) 1998-09-09
EP0863314B1 true EP0863314B1 (fr) 2002-10-02

Family

ID=7822304

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98103724A Revoked EP0863314B1 (fr) 1997-03-05 1998-03-03 Compresseur à canal latéral effilé

Country Status (3)

Country Link
EP (1) EP0863314B1 (fr)
DE (2) DE19708952A1 (fr)
ES (1) ES2180084T3 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19913950A1 (de) * 1999-03-26 2000-09-28 Rietschle Werner Gmbh & Co Kg Seitenkanalverdichter
DE202004019506U1 (de) * 2004-12-17 2006-04-20 Nash_Elmo Industries Gmbh Seitenkanalverdichter
EP2027015A1 (fr) * 2006-06-12 2009-02-25 Mag Aerospace Industries, Inc. Pompe à vide régénérative pour avion et autres véhicules
DE102007053016A1 (de) 2007-11-05 2009-05-07 Gardner Denver Deutschland Gmbh Seitenkanalverdichter
DE112015003162T5 (de) * 2014-07-09 2017-04-27 Mag Aerospace Industries, Llc Vakuumerzeuger-Strömungsumlenkeinrichtung
US11441772B2 (en) 2018-07-19 2022-09-13 Brunswick Corporation Forced-draft pre-mix burner device

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE876285C (de) * 1940-09-29 1953-05-11 Siemens Ag Ringverdichter
GB606127A (en) * 1944-10-30 1948-08-06 Bendix Aviat Corp Blowers
DE2131952C3 (de) * 1971-06-26 1974-05-09 Siemens Ag, 1000 Berlin Und 8000 Muenchen Ringkanalgebläse
US4325672A (en) * 1978-12-15 1982-04-20 The Utile Engineering Company Limited Regenerative turbo machine
SU1359437A1 (ru) * 1986-03-25 1987-12-15 Ленинградский Кораблестроительный Институт Вихрева турбомашина
KR970005981B1 (ko) * 1991-06-18 1997-04-22 가부시기가이샤 히다찌세이사뀨쇼 와류블로워
DE4242474A1 (de) * 1992-12-16 1994-06-23 Sel Alcatel Ag Vorrichtung zum Fördern eines gasförmigen Mediums

Also Published As

Publication number Publication date
DE19708952A1 (de) 1998-09-17
EP0863314A1 (fr) 1998-09-09
ES2180084T3 (es) 2003-02-01
DE59805750D1 (de) 2002-11-07

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