EP0602558B1 - Apparatus for transporting a gaseous medium - Google Patents

Apparatus for transporting a gaseous medium Download PDF

Info

Publication number
EP0602558B1
EP0602558B1 EP93119925A EP93119925A EP0602558B1 EP 0602558 B1 EP0602558 B1 EP 0602558B1 EP 93119925 A EP93119925 A EP 93119925A EP 93119925 A EP93119925 A EP 93119925A EP 0602558 B1 EP0602558 B1 EP 0602558B1
Authority
EP
European Patent Office
Prior art keywords
impeller
radial
radial compressor
compressor according
blades
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.)
Expired - Lifetime
Application number
EP93119925A
Other languages
German (de)
French (fr)
Other versions
EP0602558A1 (en
Inventor
Reinhold Hopfensperger
Rudolf Tungl
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.)
Motoren Ventilatoren Landshut GmbH
Original Assignee
Alcatel SEL AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Alcatel SEL AG filed Critical Alcatel SEL AG
Publication of EP0602558A1 publication Critical patent/EP0602558A1/en
Application granted granted Critical
Publication of EP0602558B1 publication Critical patent/EP0602558B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal 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
    • F04D23/00—Other rotary non-positive-displacement pumps
    • F04D23/008—Regenerative pumps

Definitions

  • the present invention relates to a radial fan for conveying a gaseous medium according to the preamble of claim 1.
  • Such a device is known from DE-A-39 24 281. That there The radial fan provided has one from a constriction Outlet opening towards a radially spiral-widening flow channel.
  • the Fan wheel designed as a paddle wheel is except in the area of the central one one-sided suction opening on both sides through a to the mouth of the Exit openings extending side wall formed closed.
  • a such a radial fan has a steep pressure-volume flow characteristic, i.e. that with major changes in the pressure generated, only a small one Change in volume flow occurs. Furthermore, the intrinsic noise relatively low.
  • This measure is intended to ensure that the pressure of the fan does not drop if the delivery number is low.
  • the object of the invention is to achieve the known radial fan to develop so that without increasing the dimensions in radial, pointing away from the axis of rotation an increase in static differential pressure and thus a speed reduction less noise emission is achieved.
  • Fig. 1 denotes a radial fan housing.
  • the housing 1 has a front side 3 and a rear side 4.
  • the impeller 2 consists - as can be seen from Fig. 3 - of the impeller rear wall 21, the impeller cover 20 and the rearward arranged therebetween curved blades 19.
  • the blades 19 are from the inside out tapered on the outside, and its length is on the rear impeller wall 21 larger than on the fan wheel cover 20.
  • a drive unit 5 for. B. an electric motor, preferably a DC motor, coupled.
  • At the front 3 of the housing 1 is a Intake nozzle 6 or an intake nozzle attached.
  • the inner contour 7 of the housing 1 is formed spirally and surrounds with a radial distance, the impeller 2, as can be seen from FIG. 4.
  • the remaining space forms the flow channel 8. From a narrow point 9 from, on the so-called housing tongue 10, the volume increases of the flow channel 8 to the medium outlet opening 11.
  • the diameter D of the impeller 2 is larger than the width B of the medium outlet opening 11.
  • the wall of the front side 3 of the impeller cover 20 facing Housing 1 and the inner surface facing the impeller rear wall 21 the rear 4 of the housing 1 are designed so that between them and the impeller 2 has only a small gap 13 or 13 '. This prevents backflow into the intake duct.
  • a labyrinth gap can be provided there or the shape be made such that an increased in the gap 13 or 13 ' Flow resistance in the radial direction is present.
  • the flow channel 8 is in the area of the peripheral outlet openings 15 of the impeller 2 enlarged in the radial and axial directions, such as 3 can be seen.
  • the enlargement of the flow channel 8 in axial direction extends to the front 3 of the housing 1, while the enlargement of the flow channel 8 in the radial direction the length 14 extends in the direction of the axis of rotation 16 of the impeller 2.
  • This creates transverse to the existing in the flow channel 8 Flow direction of the medium a backflow 17 in the formed Extension 18 through which a part of the emerging from the outlet openings 15 Medium is returned to the impeller 2. This gives it medium flowing through the flow channel 8 has a swirl.
  • the returned medium occurs Share on the length 14 again in the existing between two blades 19 Space 19.1 of the impeller 2 and experiences an additional one Acceleration.
  • the medium that then emerges from the outlet opening 11 of the flow channel 8 therefore has a greater energy potential as a once accelerated medium.
  • the impeller 2 So that this favorable circulation and swirl flow of the medium occurs, is with the impeller 2, the one with the blades 19 fixed connected impeller cover 20 and an impeller rear wall 21 contains, the existing on the suction side 22 impeller cover 20 um the length 14 shorter.
  • the outer diameter d of the cover 20 is therefore smaller than the diameter D of the rear wall 21 circulating portion of the medium from the open side 23 back in enter the impeller 2.
  • the impeller cover 20 With a sufficiently small gap 13 or / and Using a labyrinth gap, the impeller cover 20 can completely omitted.
  • the rear wall 21 serving as a carrier for the blades 19 is provided with a Provide bore 24 which expediently extends in a hub 25.
  • the energy turnover or the increase in the energy potential can by suitable design of the housing geometry, in particular the Dimensions and shape of the extension 18, and the blade geometry, for example, the entry angle ⁇ 1 and / or the exit angle ⁇ 2 Blades 19 of the impeller 2, set or controlled.
  • the housing geometry in particular the Dimensions and shape of the extension 18, and the blade geometry, for example, the entry angle ⁇ 1 and / or the exit angle ⁇ 2 Blades 19 of the impeller 2, set or controlled.
  • Each find backward curved or radial according to intended use ending or forward curved blade shapes application.
  • the shape of the extension shown rectangular in cross section in FIG. 3 18 of the flow channel 8 can be optimized in terms of flow technology. For example, the cross-section of the resulting backflow is adjusted, i.e. there are at least the corners of the visible in Fig. 3 Flow channel 8 rounded.
  • constriction 9 is expedient as well as counter to the direction of rotation Wedge gap 10.1 of the flow channel 8 for the air outlet 11 dimensioned such that none at the operating speeds Sound level peaks occur.
  • the constriction 9 can not be as narrow as desired be designed.
  • the radial fan according to the invention is particularly suitable for air or Gas pressure generation for gas burners that have a large flow resistance have. Have a large flow resistance z.
  • B. Gas burner which is a ceramic burner disc with a multitude of small ones Has holes (so-called surface burner) through which the combustible Medium must be pushed through.
  • Another preferred area of application is the area of mixing different gaseous Media. For example, it can serve to provide a fuel gas with the necessary Mix air proportion before both flow into the burner.
  • Radial blower swirl formation due to backflow of the medium in the flow channel including expansion.

Landscapes

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

Description

Die vorliegende Erfindung betrifft ein Radialgebläse zum Fördern eines gasförmigen Mediums gemäß dem Oberbegriff des Anspruchs 1.The present invention relates to a radial fan for conveying a gaseous medium according to the preamble of claim 1.

Eine derartige Vorrichtung ist bekannt aus der DE-A-39 24 281. Das dort vorgesehene Radialgebläse besitzt einen sich von einer Engstelle aus zur Austrittsöffnung hin radial spiralförmig erweiternden Strömungskanal. Das als Schaufelrad ausgebildete Gebläserad ist außer im Bereich der zentralen einseitigen Ansaugöffnung beidseitig durch eine sich bis zur Mündung der Austrittsöffnungen erstreckenden Seitenwand geschlossen ausgebildet. Ein derartiges Radialgebläse besitzt eine steile Druck-Volumenstrom-Kennlinie, d.h. daß bei größeren Änderungen des erzeugten Drucks eine nur geringe Änderung des Volumenstroms eintritt. Weiterhin ist das Eigengeräusch relativ gering.Such a device is known from DE-A-39 24 281. That there The radial fan provided has one from a constriction Outlet opening towards a radially spiral-widening flow channel. The Fan wheel designed as a paddle wheel is except in the area of the central one one-sided suction opening on both sides through a to the mouth of the Exit openings extending side wall formed closed. A such a radial fan has a steep pressure-volume flow characteristic, i.e. that with major changes in the pressure generated, only a small one Change in volume flow occurs. Furthermore, the intrinsic noise relatively low.

Es ist auch ein Radialgebläse mit einem Gehäuse mit spiralförmiger Innenkontur und einem geschlossenen Gebläserad bekannt (GB-A-2 017 823), bei dem Gebläserad-Rückwand und Gebläserad-Deckel einen konstanten Abstand zueinander aufweisen und zwischen ihnen rückwärts gekrümmte Schaufeln angeordnet sind. Bei dem bekannten Radialgebläse sind die Abmessungen des Gehäuses in radialer Richtung wesentlich größer als der Durchmesser des Gebläserades. Die Gebläserad-Rückwand weist im Bereich der Schaufeln V-förmige Ausschnitte auf, so daß sich zwischen diesen und der Gehäuserückwand eine Rückströmung ausbilden kann.It is also a radial fan with a housing with a spiral inner contour and a closed impeller known (GB-A-2 017 823), with the fan wheel rear wall and fan wheel cover a constant Have a distance from each other and backwards curved between them Blades are arranged. In the known radial fan, the Dimensions of the housing in the radial direction much larger than that Impeller diameter. The rear wall of the impeller faces Area of the blades on V-shaped cutouts, so that between this and the rear wall of the housing can form a backflow.

Durch diese Maßnahme soll erreicht werden, daß der Druck des Gebläses bei niedriger Lieferziffer nicht abfällt.This measure is intended to ensure that the pressure of the fan does not drop if the delivery number is low.

Mit der Erfindung soll die Aufgabe gelöst werden, das bekannte Radialgebläse so weiterzubilden, daß ohne Vergrößerung der Abmessungen in radialer, von der Drehachse wegweisender Richtung eine Erhöhung des statischen Differenzdrucks und damit über eine Drehzahlabsenkung eine geringere Geräuschabstrahlung erreicht wird.The object of the invention is to achieve the known radial fan to develop so that without increasing the dimensions in radial, pointing away from the axis of rotation an increase in static differential pressure and thus a speed reduction less noise emission is achieved.

Gelöst wird diese Aufgabe durch die im Kennzeichen des Anspruchs 1 angegebenen Merkmale. Durch diese Ausgestaltung des Strömungskanals sowie des im Bereich der Erweiterung seitlich offenen Gebläserades ist die Strömungsrichtung des aus diesem austretenden Mediums nicht mehr streng radial gerichtet, sondern besitzt eine axiale Komponente. Dies bewirkt eine Mischung des in der Erweiterung zirkulierenden Mediums mit dem aus den Austrittsöffnungen des Gebläserades austretenden Medium. Durch das zwei- oder mehrmalige Beaufschlagen der Schaufeln im Radaußenbereich mit dem Strömungsmedium wird der Energieumsatz am Medium erhöht. Außerdem wird durch die Strömungsrückführung im erweiterten Strömungskanal eine ansonsten mögliche Erzeugung von Druckschwingungen im Medium (schwingende Luft- oder Gasgemischsäule), die im nachgeschalteten System (Brenner) zu Resonanzen anregen kann, vermieden. Außerdem ist eine gegenüber dem bekannten Radialgebläse weitere Geräuschminderung feststellbar.This problem is solved by the in the characterizing part of claim 1 specified characteristics. This configuration of the flow channel as well as the fan wheel which is open on the side in the area of the extension Flow direction of the medium emerging from this no longer strictly radially directed, but has an axial component. This causes a mixing of the medium circulating in the extension the medium emerging from the outlet openings of the impeller. By applying the blades two or more times in the The outer wheel area with the flow medium is the energy conversion on Medium increased. In addition, the flow return in the expanded Flow channel an otherwise possible generation of pressure vibrations in the medium (vibrating air or gas mixture column), the can stimulate resonances in the downstream system (burner) avoided. In addition, one is compared to the known radial fan further noise reduction noticeable.

Weitere vorteilhafte Ausgestaltungen der Erfindung sind in den Unteransprüchen angegeben und nachfolgend anhand eines in der Zeichnung dargestellten Ausführungsbeispiels betrieben. Es zeigen:

Fig. 1
ein Radialgebläse in der Ansicht auf die Mediumsaustrittsöffnung,
Fig. 2
die Draufsicht auf ein Gebläserad,
Fig. 3
den Querschnitt bei offenem Gehäuse gemäß dem Schnitt 1-1 der Fig. 4 und
Fig. 4
eine Draufsicht auf das Radialgebläse-Gehäuse bei angenommenem Gehäusedeckel.
Further advantageous refinements of the invention are specified in the subclaims and are subsequently operated using an exemplary embodiment shown in the drawing. Show it:
Fig. 1
a radial fan in the view of the medium outlet opening,
Fig. 2
the top view of an impeller,
Fig. 3
the cross section with the housing open according to section 1-1 of Fig. 4 and
Fig. 4
a plan view of the radial fan housing with assumed housing cover.

In Fig. 1 ist mit 1 ein Radialgebläse-Gehäuse bezeichnet. Das Gehäuse 1 weist eine Vorderseite 3 und eine Rückseite 4 auf. Das Gebläserad 2 besteht - wie aus Fig. 3 zu erkennen ist - aus der Gebläserad-Rückwand 21, dem Gebläserad-Deckel 20 sowie den dazwischen angeordneten rückwärts gekrümmten Schaufeln 19. Die Schaufeln 19 sind sich von innen nach außen verjüngend ausgebildet, und ihre Länge ist an der Gebläserad-Rückwand 21 größer als am Gebläserad-Deckel 20. Mit einem Gebläserad 2 ist ein Antriebsaggregat 5, z. B. ein Elektromotor, vorzugsweise ein Gleichstrommotor, gekoppelt. An der Vorderseite 3 des Gehäuses 1 ist ein Ansaugstutzen 6 oder eine Ansaugdüse angebracht.In Fig. 1, 1 denotes a radial fan housing. The housing 1 has a front side 3 and a rear side 4. The impeller 2 consists - as can be seen from Fig. 3 - of the impeller rear wall 21, the impeller cover 20 and the rearward arranged therebetween curved blades 19. The blades 19 are from the inside out tapered on the outside, and its length is on the rear impeller wall 21 larger than on the fan wheel cover 20. With one fan wheel 2 is a drive unit 5, for. B. an electric motor, preferably a DC motor, coupled. At the front 3 of the housing 1 is a Intake nozzle 6 or an intake nozzle attached.

Die Innenkontur 7 des Gehäuses 1 ist spiralförmig ausgebildet und umgibt mit radialem Abstand das Gebläserad 2, wie anhand der Fig. 4 ersichtlich. Der verbleibende Raum bildet den Strömungskanal 8. Von einer Engstelle 9 aus, an der sogenannten Gehäusezunge 10, vergrößert sich das Volumen des Strömungskanals 8 bis zur Mediumaustrittsöffnung 11. Wie aus Fig. 1 erkennbar, ist der Durchmesser D des Gebläserades 2 größer als die Breite B der Mediumsaustrittsöffnung 11.The inner contour 7 of the housing 1 is formed spirally and surrounds with a radial distance, the impeller 2, as can be seen from FIG. 4. The remaining space forms the flow channel 8. From a narrow point 9 from, on the so-called housing tongue 10, the volume increases of the flow channel 8 to the medium outlet opening 11. As in FIG. 1 recognizable, the diameter D of the impeller 2 is larger than the width B of the medium outlet opening 11.

Die dem Gebläserad-Deckel 20 zugewandte Wand der Vorderseite 3 des Gehäuses 1 und die der Gebläserad-Rückwand 21 zugewandte Innenfläche der Rückseite 4 des Gehäuses 1 sind so ausgebildet, daß zwischen diesen und dem Gebläserad 2 nur ein geringer Spalt 13 bzw. 13' vorhanden ist. Hierdurch wird eine Rückströmung in den Ansaugkanal verhindert. Zweckmäßig kann dort jeweils ein Labyrinthspalt vorgesehen sein oder die Formgebung derart vorgenommen sein, daß im Spalt 13 bzw. 13' ein erhöhter Strömungswiderstand in radialer Richtung vorhanden ist.The wall of the front side 3 of the impeller cover 20 facing Housing 1 and the inner surface facing the impeller rear wall 21 the rear 4 of the housing 1 are designed so that between them and the impeller 2 has only a small gap 13 or 13 '. This prevents backflow into the intake duct. Appropriately a labyrinth gap can be provided there or the shape be made such that an increased in the gap 13 or 13 ' Flow resistance in the radial direction is present.

Der Strömungskanal 8 ist im Bereich der umfangsseitigen Austrittsöffnungen 15 des Gebläserades 2 in radialer und axialer Richtung vergrößert, wie aus Fig. 3 zu erkennen ist. Die Vergrößerung des Strömungskanals 8 in axialer Richtung erstreckt sich zur Vorderseite 3 des Gehäuses 1 hin, während sich die Vergrößerung des Strömungskanals 8 in radialer Richtung um die Länge 14 in Richtung zur Drehachse 16 des Gebläserades 2 erstreckt. Hierdurch entsteht quer zu der im Strömungskanal 8 vorhandenen Strömungsrichtung des Mediums eine Rückströmung 17 in der gebildeten Erweiterung 18, durch die ein Teil des aus den Austrittsöffnungen 15 austretenden Mediums zum Gebläserad 2 zurückgeführt wird. Dadurch erhält das den Strömungskanal 8 durchströmende Medium einen Drall.The flow channel 8 is in the area of the peripheral outlet openings 15 of the impeller 2 enlarged in the radial and axial directions, such as 3 can be seen. The enlargement of the flow channel 8 in axial direction extends to the front 3 of the housing 1, while the enlargement of the flow channel 8 in the radial direction the length 14 extends in the direction of the axis of rotation 16 of the impeller 2. This creates transverse to the existing in the flow channel 8 Flow direction of the medium a backflow 17 in the formed Extension 18 through which a part of the emerging from the outlet openings 15 Medium is returned to the impeller 2. This gives it medium flowing through the flow channel 8 has a swirl.

Durch die Zurückführung des beschleunigten Mediums tritt der rückgeführte Anteil auf der Länge 14 wieder in den zwischen zwei Schaufeln 19 vorhandenen Zwischenraum 19.1 des Gebläserades 2 ein und erfährt eine zusätzliche Beschleunigung. Das Medium, das dann aus der Austrittsöffnung 11 des Strömungskanals 8 austritt, besitzt daher ein größeres Energiepotential als ein nur einmal beschleunigtes Medium. Durch die Vermischung des rückgeführten Anteils mit dem angesaugten und erstmals durch das Gebläserad strömenden Anteil wird das Auftreten von periodischen Druckschwankungen, die zu Resonanzen in der angeschlossenen Anlage führen können, verhindert. Gleichzeitig tritt bei einem vorgegebenen Betriebspunkt durch die geringere notwendige Drehzahl eine Verringerung der Geräuschabstrahlung ein.By returning the accelerated medium, the returned medium occurs Share on the length 14 again in the existing between two blades 19 Space 19.1 of the impeller 2 and experiences an additional one Acceleration. The medium that then emerges from the outlet opening 11 of the flow channel 8, therefore has a greater energy potential as a once accelerated medium. By mixing the returned portion with the sucked in and for the first time through the Blower wheel flowing portion becomes the occurrence of periodic pressure fluctuations, that lead to resonances in the connected system can prevented. At the same time occurs at a given operating point due to the lower required speed, a reduction in Noise emission on.

Damit diese günstige Zirkulation und Drallströmung des Mediums eintritt, ist bei dem Gebläserad 2, das einen mit den Schaufeln 19 fest verbundenen Gebläserad-Deckel 20 und eine Gebläserad-Rückwand 21 enthält, der auf der Ansaugseite 22 vorhandene Gebläserad-Deckel 20 um die Länge 14 kürzer. Der Außendurchmesser d des Deckels 20 ist daher kleiner als der Durchmesser D der Rückwand 21. Dadurch kann der zirkulierende Anteil des Mediums von der offenen Seite 23 aus wieder in das Gebläserad 2 eintreten. Bei genügend kleinem Spalt 13 oder/und Anwendung eines Labyrinthspalts kann der Gebläserad-Deckel 20 ganz entfallen.So that this favorable circulation and swirl flow of the medium occurs, is with the impeller 2, the one with the blades 19 fixed connected impeller cover 20 and an impeller rear wall 21 contains, the existing on the suction side 22 impeller cover 20 um the length 14 shorter. The outer diameter d of the cover 20 is therefore smaller than the diameter D of the rear wall 21 circulating portion of the medium from the open side 23 back in enter the impeller 2. With a sufficiently small gap 13 or / and Using a labyrinth gap, the impeller cover 20 can completely omitted.

Die als Träger für die Schaufeln 19 dienende Rückwand 21 ist mit einer Bohrung 24 versehen, die sich zweckmäßig in einer Nabe 25 erstreckt.The rear wall 21 serving as a carrier for the blades 19 is provided with a Provide bore 24 which expediently extends in a hub 25.

Der Energieumsatz bzw. die Erhöhung des Energiepotentials kann durch geeignete Gestaltung der Gehäusegeometrie, insbesondere der Abmessungen und Form der Erweiterung 18, und der Schaufelgeometrie, beispielsweise des Eintrittswinkels β1 und/oder des Austrittswinkels β2 der Schaufeln 19 des Gebläserades 2, festgelegt bzw. gesteuert werden. Je nach Verwendungszweck finden nach rückwärts gekrümmte oder radial endende oder vorwärts gekrümmte Schaufelformen Anwendung.The energy turnover or the increase in the energy potential can by suitable design of the housing geometry, in particular the Dimensions and shape of the extension 18, and the blade geometry, for example, the entry angle β1 and / or the exit angle β2 Blades 19 of the impeller 2, set or controlled. Each find backward curved or radial according to intended use ending or forward curved blade shapes application.

Die im Querschnitt der Fig. 3 rechteckig dargestellte Form der Erweiterung 18 des Strömungskanals 8 kann strömungstechnisch optimiert werden. Beispielsweise wird der Querschnitt der entstehenden Rückströmung angepaßt, d.h. es werden zumindest die in Fig. 3 sichtbaren Ecken des Strömungskanals 8 abgerundet.The shape of the extension shown rectangular in cross section in FIG. 3 18 of the flow channel 8 can be optimized in terms of flow technology. For example, the cross-section of the resulting backflow is adjusted, i.e. there are at least the corners of the visible in Fig. 3 Flow channel 8 rounded.

Zweckmäßig ist die Engstelle 9 sowie der entgegen der Drehrichtung bis zum Luftaustritt 11 vorhandene Keilspalt 10.1 des Strömungskanals 8 derart bemessen, daß bei den auftretenden Betriebsdrehzahlen keine Schallpegelspitzen auftreten. Die Engstelle 9 kann also nicht beliebig eng gestaltet werden.The constriction 9 is expedient as well as counter to the direction of rotation Wedge gap 10.1 of the flow channel 8 for the air outlet 11 dimensioned such that none at the operating speeds Sound level peaks occur. The constriction 9 can not be as narrow as desired be designed.

Das erfindungsgemäße Radialgebläse ist besonders geeignet zur Luft- oder Gasdruckerzeugung für Gasbrenner, die einen großen Strömungswiderstand besitzen. Einen großen Strömungswiderstand haben z. B. Gasbrenner, die eine Brennerscheibe aus Keramik mit einer Vielzahl kleiner Bohrungen aufweist (sog. Flächenbrenner), durch die das brennbare Medium hindurchgedrückt werden muß. Ein weiteres bevorzugtes Anwendungsgebiet ist das Gebiet der Mischung unterschiedlicher gasförmiger Medien. Beispielsweise kann es dazu dienen, ein Brenngas mit dem notwendigen Luftanteil zu vermischen, bevor beide in den Brenner einströmen. Die gute Vermischung der Gasanteile wird durch die bei dem erfindungsgemäßen Radialgebläse infolge der Rückströmung auftretende Drallbildung des Mediums im Strömungskanal einschließlich Erweiterung erreicht.The radial fan according to the invention is particularly suitable for air or Gas pressure generation for gas burners that have a large flow resistance have. Have a large flow resistance z. B. Gas burner, which is a ceramic burner disc with a multitude of small ones Has holes (so-called surface burner) through which the combustible Medium must be pushed through. Another preferred area of application is the area of mixing different gaseous Media. For example, it can serve to provide a fuel gas with the necessary Mix air proportion before both flow into the burner. The good mixing of the gas fractions is due to that in the invention Radial blower swirl formation due to backflow of the medium in the flow channel including expansion.

Claims (8)

  1. A radial compressor for conveying a gaseous medium, comprising a compressor (1) with a spiral-shaped inner contour, in which an impeller (2) with constant diameter and consisting of an impeller rear wall (21) and an intake-side impeller cover (20) with blades (19) arranged therebetween decreasing constantly in axial width radially from the inside to the outside is arranged in such a way that a flow channel (8) widening in the radial direction is present between the circumference of the impeller (2) and the inner contour of the housing (1), characterised by the following features:
    a) only a small gap (13) is present between the housing front (3) and the impeller cover (20) over the entire radial length of the cover,
    b) the radius of the impeller cover (20) is smaller than the radius of the impeller rear wall (21), such that the ends of the blades (19) are radially and axially open,
    c) the flow channel (8) is enlarged axially and radially at the circumference of the impeller (2) in the area of the open ends of the blades (19), wherein the axial enlargement begins where the impeller cover (29) ends.
  2. A radial compressor according to claim 1, characterised in that the impeller rear wall (21) comprises a central hub (25) and/or a central hole (24) to which a drive unit (5) may be coupled.
  3. A radial compressor according to one of claims 1 and 2, characterised in that the gap (13) between the front (3) and the rear (4) of the housing (2) and the impeller (2) is so constructed that increased flow resistance is present in the radial direction.
  4. A radial compressor according to one of claims 1 to 3, characterised in that the flow channel (8) is cross-sectionally conformed to the developing swirling flow of the recirculating medium, and in particular is circular or elliptical in shape.
  5. A radial compressor according to one of claims 1 to 4, characterised in that the blades (19) of the impeller (2) are rearwardly curved in the direction of rotation.
  6. A radial compressor according to one of claims 1 to 4, characterised in that the blades (19) of the impeller (2) are forwardly curved in the direction of rotation or are of radially terminating construction.
  7. A radial compressor according to one of claims 1 to 6, characterised by the use of said radial compressor to generate an air or gas mixture pressure for gas burners with a panel burner comprising a high flow resistance and a plurality of through-holes.
  8. A radial compressor according to one of claims 1 to 7, characterised by use as a mixer for uniform mixing of two or more gaseous media.
EP93119925A 1992-12-16 1993-12-10 Apparatus for transporting a gaseous medium Expired - Lifetime EP0602558B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4242474 1992-12-16
DE4242474A DE4242474A1 (en) 1992-12-16 1992-12-16 Device for conveying a gaseous medium

Publications (2)

Publication Number Publication Date
EP0602558A1 EP0602558A1 (en) 1994-06-22
EP0602558B1 true EP0602558B1 (en) 1998-01-28

Family

ID=6475435

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93119925A Expired - Lifetime EP0602558B1 (en) 1992-12-16 1993-12-10 Apparatus for transporting a gaseous medium

Country Status (3)

Country Link
EP (1) EP0602558B1 (en)
AU (1) AU5189493A (en)
DE (2) DE4242474A1 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6422808B1 (en) 1994-06-03 2002-07-23 Borgwarner Inc. Regenerative pump having vanes and side channels particularly shaped to direct fluid flow
CA2194209A1 (en) * 1996-02-05 1997-08-06 Norman Moss Regenerative pump having vanes and side channels particularly shaped to direct fluid flow
DE19708952A1 (en) * 1997-03-05 1998-09-17 Busch Gmbh K Side channel blower with tapering channel cross section
DE19913950A1 (en) * 1999-03-26 2000-09-28 Rietschle Werner Gmbh & Co Kg Side channel blower
ITTO20020370A1 (en) * 2002-05-06 2003-11-06 Varian Spa PUMPING STAGE FOR VACUUM PUMP.

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1650873A (en) * 1927-01-18 1927-11-29 Bertha C Ryan Rotary blower
GB606127A (en) * 1944-10-30 1948-08-06 Bendix Aviat Corp Blowers
US2471174A (en) * 1947-04-24 1949-05-24 Clark Bros Co Inc Centrifugal compressor stability means
DE1403579A1 (en) * 1961-03-04 1969-07-17 Obermaier & Cie Turbo blower
CH526223A (en) * 1971-01-13 1972-07-31 Bbc Brown Boveri & Cie Centrifugal fan
GB2017823B (en) * 1978-03-28 1982-09-15 Howden James & Co Ltd Centrifugal fans blowers compressors or the like
DE3786171D1 (en) * 1987-11-17 1993-07-15 Mulfingen Elektrobau Ebm RADIAL BLOWER WITH INTERNAL SPIRAL.
DE3924281A1 (en) * 1989-07-22 1991-01-31 Standard Elektrik Lorenz Ag DEVICE FOR CONVEYING A GASEOUS MEDIUM

Also Published As

Publication number Publication date
DE4242474A1 (en) 1994-06-23
EP0602558A1 (en) 1994-06-22
DE59308073D1 (en) 1998-03-05
AU5189493A (en) 1994-06-30

Similar Documents

Publication Publication Date Title
DE60117177T2 (en) HIGHLY EFFICIENT, EXTRACTION MATERIAL AXIAL FAN
EP1462658B1 (en) Radial fan
DE2648850A1 (en) AXIAL FAN
DE1428191A1 (en) Centrifugal blower
DE4006604C2 (en)
EP3702620B1 (en) Axial fan with noise reducing fan impeller vanes having bores
DE19946187A1 (en) Motor-driven blower with impeller to eject flowing medium has fluid transfer section with cooperating surfaces on housing and impeller to move a fluid radially outward
EP0896191A2 (en) Fuel gas admission device for a premix burner
EP2886874A1 (en) Radial impeller for a drum type ventilator and fan assembly having such a radial impeller
DE2925941A1 (en) DIFFERENTIAL FOR A FLUID DRIVE UNIT
DE19614580A1 (en) Ventilation device for motorised tools e.g. circular saw or screwdriver
DE3706772C2 (en)
DE60100983T2 (en) Guide wheel for centrifugal pumps
EP1757814A1 (en) Centrifugal compressor
EP0602558B1 (en) Apparatus for transporting a gaseous medium
DE19710606B4 (en) Fans, in particular for radiators of internal combustion engines
DE102008053144A1 (en) Fan arrangement for cooking appliance i.e. radial combi-steamer, has pin diaphragm limiting inflow opening for fluid to be conveyed from radial impeller, and guide vanes provided at surface of carrier ring that is opposite to support plate
DE102005012815A1 (en) Radial blower housing, e.g. for automotive applications, has a flow duct whose size increases radially in a direction between the input wall and the rear side wall
EP0316470B1 (en) Radial fan with an internal spiral
EP1582750B1 (en) Casing and radial blower having a casing and an impeller
DE10357289A1 (en) Compact diagonal fan
EP1538369A1 (en) Oil guiding contour in a gearbox
DE19881809C2 (en) Device for introducing suction air into an impeller of a fan
EP2100041B1 (en) Motor centrifugal pump
EP1288574A1 (en) Combustion chamber arrangement

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT NL

17P Request for examination filed

Effective date: 19940712

17Q First examination report despatched

Effective date: 19950613

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT NL

REF Corresponds to:

Ref document number: 59308073

Country of ref document: DE

Date of ref document: 19980305

ITF It: translation for a ep patent filed

Owner name: JACOBACCI & PERANI S.P.A.

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19980306

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
NLS Nl: assignments of ep-patents

Owner name: MOTOREN VENTILATOREN LANDSHUT GMBH

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

REG Reference to a national code

Ref country code: FR

Ref legal event code: TP

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20001123

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20001127

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20001204

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20011210

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020701

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20011210

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020830

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee

Effective date: 20020701

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20051210

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20110225

Year of fee payment: 18

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 59308073

Country of ref document: DE

Effective date: 20120703

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120703