EP2104787B1 - Radial fan and a high-pressure cleaning device having a radial fan - Google Patents

Radial fan and a high-pressure cleaning device having a radial fan Download PDF

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Publication number
EP2104787B1
EP2104787B1 EP07819773.8A EP07819773A EP2104787B1 EP 2104787 B1 EP2104787 B1 EP 2104787B1 EP 07819773 A EP07819773 A EP 07819773A EP 2104787 B1 EP2104787 B1 EP 2104787B1
Authority
EP
European Patent Office
Prior art keywords
impeller
radial fan
peripheral wall
outlet area
wall section
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.)
Not-in-force
Application number
EP07819773.8A
Other languages
German (de)
French (fr)
Other versions
EP2104787A1 (en
Inventor
Ernst Claussen
Joachim Peetz
Gerd Wegner
Ralph Seitter
Lutz Bauer
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.)
Punker GmbH
Alfred Kaercher SE and Co KG
Original Assignee
Punker GmbH
Alfred Kaercher SE and Co KG
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 Punker GmbH, Alfred Kaercher SE and Co KG filed Critical Punker GmbH
Publication of EP2104787A1 publication Critical patent/EP2104787A1/en
Application granted granted Critical
Publication of EP2104787B1 publication Critical patent/EP2104787B1/en
Not-in-force legal-status Critical Current
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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
    • F04D17/04—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal of transverse-flow type
    • 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
    • F04D17/16—Centrifugal pumps for displacing without appreciable compression
    • F04D17/164—Multi-stage fans, e.g. for vacuum cleaners
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/422—Discharge tongues

Definitions

  • the invention relates to a radial fan, which is designed as a so-called HG blower, with the features of the preamble of claim 1.
  • EP 1 002 958 A1 is a radial fan with a pot-like impeller provided with a blade ring at its circumference, and a housing receiving the impeller, which extends radially from an arcuately curved, directly along the blade ring extending peripheral wall area helically in the direction of rotation of the impeller to an outlet, known.
  • Axial end faces of the impeller are covered by side walls, wherein a partition wall, which engages in the cup-shaped impeller, is arranged on one of the side walls and divides its interior into a first and a second suction space.
  • Pump-blower units with a drive shaft are also made of DE 3001571 A1 and the DE 3115698 C1 known.
  • An object of the invention is to improve a radial fan in HG-technology with regard to the volume flow and pressure generated, in particular for use in a high-pressure cleaner, so that a smaller-volume design is achieved and / or operation at a lower speed is made possible.
  • the advantage of the radial blower according to the invention is, in particular, that the return flow to the second suction chamber is guided and improved in the manner of a flow guide element by the S-shaped peripheral wall region, which leads to an overall increase in the power of the blower.
  • a diffuser in cross-section widening outlet area which also contributes to increase the fan performance.
  • this outlet is integrated in or on the radial fan.
  • the improved achieved performance data make the radial fan particularly suitable for high-pressure cleaning devices, where it comes down to small-volume design at relatively low speed. The low speed is not only required by the common operation with a high-pressure pump, but it also contributes to a reduction in the noise emission. At the same time increases the life of the radial fan and possibly one arranged on a same drive shaft high-pressure pump.
  • the end regions of the second and the third peripheral wall regions remote from the impeller form opposite wall regions of the outlet region, so that the latter is completely integrated and seamlessly formed. This also leads to an improvement in the flow conditions.
  • the outlet region has at its housing-side beginning its smallest width, which is preferably less than half the diameter of the impeller. This dimensioning has proven to be particularly suitable for achieving a high pressure and a high volume flow. This is expediently achieved in that the third peripheral wall region on the housing-side beginning of the outlet region has a tongue-like design into the housing interior, so that this narrowing is achieved at the beginning of the outlet region by the peripheral wall regions and no additional elements are required.
  • the housing is preferably made of plastic to achieve a simple and cost-effective production, in principle, a metal version is possible.
  • the second peripheral wall region has a logarithmic spiral shape, which has proved to be particularly advantageous with regard to the desired objectives.
  • the radial fan according to the invention is particularly suitable for use in a high-pressure cleaning device in which the impeller of the radial fan and a high-pressure pump are fixed to the same drive shaft of a drive motor and form a pump-fan unit in view of the described properties and advantages.
  • Preferred is the arrangement of the radial fan on one side and that of the high-pressure pump on the other side of the drive motor.
  • the pump-blower unit is arranged on a particular mobile chassis together with a boiler, wherein the radial fan for supplying the combustion air for a burner is connected to the boiler and a liquid line from the high pressure pump for heating the liquid in the Boiler is running.
  • a cup-shaped impeller 10 rotatably mounted in a helical housing 11.
  • the impeller 10 consists of a circular disk-like bottom 12, the center of a hub 13 for connection to the drive shaft 16 of a only in FIG. 3 has shown drive motor 17.
  • At the radially outer peripheral region of the bottom 12 rises perpendicular to its plane a plurality of blades 14 which form a blade ring 15.
  • the housing 11 consists of a helically shaped peripheral wall 18, wherein a part-circular curved first peripheral wall portion 19 extends directly with a very small gap along the blade ring 15, in the embodiment over an angle of about 120 °. However, this angle may vary, wherein between the blade ring 15 and the first peripheral wall portion 19, a seal may be provided in the manner of a labyrinth seal.
  • a second circumferential wall area 20 connects, which extends in a spiral manner with increasing radial distance from the impeller 10 as far as an outlet area 21 which forms the fan outlet.
  • the second peripheral wall portion 20 has a logarithmic spiral shape.
  • a third circumferential wall region 22 which likewise extends as far as the outlet region 21.
  • This third peripheral wall region 22 is curved in an S shape as far as a tongue-like indentation 23, this indentation 23 forming the beginning of the outlet region 21, which has its smallest width at this beginning with respect to the outlet flow direction, and then in width in the outlet flow direction in the manner of a diffuser or expanded its cross section.
  • the two end regions of the second peripheral wall region 20 and of the third peripheral wall region 22 remote from the first peripheral wall region 19 form opposite walls of the outlet region 21, so that this is integrally formed with respect to the circumferential wall 18. He may also be recognized in an alternative embodiment.
  • the S-shaped curvature of the third outlet wall region 22, starting from the first peripheral wall region 19, has first an opposing curvature and then again an equidirectional curvature.
  • the same direction of curvature region 24 (with respect to the first peripheral wall portion 19) forms a flow guide for the return to the impeller 10 partial flow.
  • the indentation 23 promotes the division of the flow into this recirculated partial flow and the partial flow reaching the outlet region 21.
  • the peripheral wall 18 forms together with two the open sides of the peripheral wall 18 covering side walls 25, 26, the housing 11. According to FIG. 3 These side walls 25, 26 are each integrally connected to an axial portion of the peripheral wall 18, so that a two-part housing 11 is formed. The two parts are at a connecting line 27 screwed together or fixed together in some other way.
  • peripheral wall 18 may be integrally formed integrally on one of the two side walls 25, 26, or there is a three-piece housing, consisting of peripheral wall 18 and the two side walls 25, 26th
  • the impeller 10 is sealed to the two side walls 25, 26 towards labyrinth seal, as shown in the EP 1022469 B1 or in the EP 1022470 B1 is described in more detail.
  • a partition wall 28 extends into the interior of the cup-shaped impeller 10 and divides the interior thereof into a first suction chamber V1 and a second suction chamber V2, which faces the peripheral wall region 19.
  • This partition wall 28 extends from the side wall 26 obliquely out to the bottom 12 of the impeller 10, wherein in principle a parallel course to the axis of rotation of the impeller 10 is possible.
  • this edge may be provided with sealing elements, as described in more detail in the cited prior art.
  • the side wall 26 is provided with an air intake opening 29, which opens in the first suction chamber V1.
  • the air intake 29 may be in various shapes and configurations. Various variants and embodiments are described in detail in the prior art mentioned above and can be used accordingly in the present invention.
  • the impeller 10 acts in the region of the first suction chamber V1 as a radial fan. Outside air is sucked through the air intake opening 28 into the first suction chamber V1 and accelerated radially outward over the peripheral region of the first suction chamber V1 through the blade ring 15. This accelerated air flow is divided outside into a working flow A1 and a working flow A2. The working flow A1 returns to the first suction chamber V1 and is accelerated outwards again by the radial fan action, whereby a substantial part of this working flow reaches the spiral extension area at the opposite end of the first suction chamber V1.
  • the impeller In the region of the second suction chamber V2, the impeller is not closed at its two axial end faces by the side walls 25, 26. Towards the interior, the partition wall 28 forms a tight seal, and at the partition wall opposite the first peripheral wall portion 19, this forms the seal.
  • the impeller 10 therefore operates in the region of the second suction chamber V2 exclusively as a cross-flow fan, which sucks the working stream A2 and is supported by the S-shaped curvature of the third peripheral wall portion 22 and the indentation 23. This working stream A2 is then compressed and blown out again on the opposite side of the impeller 10.
  • the fan works thus partly as a two-stage blower with a first stage formed by the first suction chamber V1, working as a radial fan and a second stage formed by the second suction chamber V2, acting as a cross-flow fan.
  • outlet portion 21 as a discharge diffuser due to the described enlargement in width or in cross-section causes an increase in the static fan pressure.
  • high pressure cleaning device has a similar structure as that of the EP 0248282 B1 known high pressure cleaning device.
  • the drive motor has a vertical drive shaft, while the drive shaft 16 of the drive motor 17 is arranged horizontally according to Figures 2 and 3. It is of course possible to form the high-pressure cleaning device described in connection with the invention with a vertical drive shaft 16.
  • a pump-blower unit 30 On a chassis 40, which may be formed as a wheeled mobile chassis, a pump-blower unit 30 is mounted, which consists of the drive motor 17, the drive shaft 16 on one side of the impeller 10 of the radial fan 9 and on the opposite Side a high-pressure pump 31 drives.
  • the radial fan 9 or its outlet region 21 is connected to a cylindrical heating boiler 32, the cover 33 of which carries a fan burner 34 which is equipped with gas or liquid fuel is operated.
  • the high-pressure pump 31 is connected via a connecting line 35 to a pipe system 36 in the interior of the boiler 32, wherein the pipe system 36 extends in a plurality of turns along the cylindrical outer wall 37 of the boiler 32. These turns are formed in two layers in the illustrated embodiment, of course, a different number of layers is possible.
  • the air flow generated by the radial fan 9 flows upward in the boiler 32 along the outer wall 37 and supplies the required combustion air to the fan burner 34.
  • the burner flame extends vertically downward from the blower burner 34 and heats the pipe system 36 or the liquid therein.
  • the heated liquid is then passed in a continuous process through the high-pressure pump 31 to an outlet pump nozzle, not shown, which is usually mounted on a high-pressure hose.
  • a fuel pump 38 is still connected to the fuel supply to the fan burner 34 on the drive shaft 16 and the hub 13 of the impeller 10 and is driven simultaneously.
  • a regulating element 39 is arranged, by means of which the air flow generated can be regulated as required.
  • a 4-pole asynchronous motor is usually used, which causes a speed of less than 1,500 U / min in a 50 Hz alternating current.
  • electronically controlled motors can be used, which allow a greater variability of the speed.
  • the housing 11 of the radial fan 9 is suitably made of plastic, on the one hand to achieve a cost-effective production and on the other hand a low weight. In principle, however, a metal version is possible.

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

Description

Die Erfindung betrifft ein Radialgebläse, das als sogenanntes HG-Gebläse ausgebildet ist, mit den Merkmalen des Oberbegriffs des Anspruchs 1.The invention relates to a radial fan, which is designed as a so-called HG blower, with the features of the preamble of claim 1.

Ein derartiges, beispielsweise aus der EP 1022469 B1 bekanntes Radialgebläse kann zwar relativ hohe statische Drücke erzeugen und besitzt eine gute P/V-Charakteristik, jedoch ist es aus Kosten- und Platzgründen immer wünschenswert, die Baugröße zu verkleinern und den erzeugten Druck und Volumenstrom zu vergrößern. Dabei ist es bei verschiedenen Anwendungen nicht möglich, die Drehzahl zu erhöhen, um diese Verbesserungen zu erreichen, beispielsweise bei Hochdruck-Reinigungsgeräten, bei denen ein Antriebsmotor sowohl ein Radialgebläse als auch eine Hochdruckpumpe antreibt. Hochdruckpumpen werden gewöhnlich bei Drehzahlen unter 1.500 U/min betrieben, sodass das Radialgebläse ebenfalls mit dieser Drehzahl arbeiten muss, will man nicht ein teures und aufwendiges Getriebe vorsehen.Such, for example from the EP 1022469 B1 Although known radial blower can produce relatively high static pressures and has a good P / V characteristic, but it is always desirable for cost and space reasons, to reduce the size and increase the pressure and flow generated. It is not possible in various applications to increase the speed in order to achieve these improvements, for example in high-pressure cleaning devices, in which a drive motor drives both a radial fan and a high-pressure pump. High-pressure pumps are usually operated at speeds below 1,500 rpm, so that the radial fan must also operate at this speed, you do not want to provide an expensive and expensive transmission.

Aus der EP 1 002 958 A1 ist ein Radialgebläse mit einem topfartigen Laufrad, das an seinem Umfang mit einem Schaufelkranz versehen ist, sowie ein das Laufrad aufnehmendes Gehäuse, das sich ausgehend von einem teilkreisartig gekrümmten, direkt entlang des Schaufelkranzes verlaufenden Umfangswandbereich schneckenartig in Drehrichtung des Laufrads radial zu einem Auslass erweitert, bekannt.From the EP 1 002 958 A1 is a radial fan with a pot-like impeller provided with a blade ring at its circumference, and a housing receiving the impeller, which extends radially from an arcuately curved, directly along the blade ring extending peripheral wall area helically in the direction of rotation of the impeller to an outlet, known.

Axiale Stirnseiten des Laufrads werden von Seitenwandungen abgedeckt, wobei eine Trennwand, die in das topfartige Laufrad eingreift, an einer der Seitenwandungen angeordnet ist und dessen Innenraum in einen ersten und einen zweiten Saugraum unterteilt.Axial end faces of the impeller are covered by side walls, wherein a partition wall, which engages in the cup-shaped impeller, is arranged on one of the side walls and divides its interior into a first and a second suction space.

Ein aus der EP 0248282 B1 bekanntes Hochdruck-Reinigungsgerät weist eine solche Pumpen-Gebläse-Einheit mit einer Antriebswelle auf. Bei einem solchen Gerät muss zur Erzeugung der erforderlichen Verbrennungsluft entweder ein sehr großvolumiges Radialgebläse eingesetzt werden oder die Drehzahl muss deutlich erhöht werden oder man muss einen entsprechend kleineren Brenner verwenden, der weniger Verbrennungsluft benötigt.One from the EP 0248282 B1 Known high-pressure cleaning device has such a pump-blower unit with a drive shaft. In such a device must to generate the required Combustion air either a very large volume radial fan can be used or the speed must be increased significantly or you must use a correspondingly smaller burner, which requires less combustion air.

Pumpen-Gebläse-Einheiten mit einer Antriebswelle sind auch aus der DE 3001571 A1 und der DE 3115698 C1 bekannt.Pump-blower units with a drive shaft are also made of DE 3001571 A1 and the DE 3115698 C1 known.

Eine Aufgabe der Erfindung besteht darin, ein Radialgebläse in HG-Technik hinsichtlich des erzeugten Volumenstroms und Drucks, insbesondere zur Verwendung bei einem Hochdruck-Reinigungsgerät, so zu verbessern, dass eine kleinvolumigere Bauweise erreicht wird und/oder ein Betrieb bei niedrigerer Drehzahl ermöglicht wird.An object of the invention is to improve a radial fan in HG-technology with regard to the volume flow and pressure generated, in particular for use in a high-pressure cleaner, so that a smaller-volume design is achieved and / or operation at a lower speed is made possible.

Diese Aufgabe wird erfindungsgemäß durch ein Radialgebläse mit den Merkmalen des Anspruchs 1 gelöst.This object is achieved by a radial fan with the features of claim 1.

Der Vorteil des erfindungsgemäßen Radialgebläses besteht insbesondere darin, dass durch den S-förmigen Umfangswandbereich die Rückströmung zum zweiten Saugraum nach Art eines Strömungsleitelements geführt und verbessert wird, was insgesamt zu einer Leistungserhöhung des Gebläses führt. Hinzu kommt der sich nach Art eines Diffusors im Querschnitt erweiternde Auslassbereich, der ebenfalls zur Erhöhung der Gebläseleistung beiträgt. Dabei ist dieser Auslassbereich im oder am Radialgebläse integriert. Die verbesserten erreichten Leistungsdaten machen das Radialgebläse insbesondere für Hochdruck-Reinigungsgeräte geeignet, wo es auf kleinvolumige Bauweise bei relativ geringer Drehzahl ankommt. Die geringe Drehzahl ist nicht nur durch den gemeinsamen Betrieb mit einer Hochdruckpumpe erforderlich, sondern sie trägt auch zu einer Verringerung der Geräuschemission bei. Gleichzeitig erhöht sich die Lebensdauer des Radialgebläses und einer eventuell auf einer gleichen Antriebswelle angeordneten Hochdruckpumpe.The advantage of the radial blower according to the invention is, in particular, that the return flow to the second suction chamber is guided and improved in the manner of a flow guide element by the S-shaped peripheral wall region, which leads to an overall increase in the power of the blower. In addition comes in the manner of a diffuser in cross-section widening outlet area, which also contributes to increase the fan performance. In this case, this outlet is integrated in or on the radial fan. The improved achieved performance data make the radial fan particularly suitable for high-pressure cleaning devices, where it comes down to small-volume design at relatively low speed. The low speed is not only required by the common operation with a high-pressure pump, but it also contributes to a reduction in the noise emission. At the same time increases the life of the radial fan and possibly one arranged on a same drive shaft high-pressure pump.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Anspruch 1 angegebenen Radialgebläses möglich.The measures listed in the dependent claims advantageous refinements and improvements of claim 1 radial fan are possible.

Erfindungsgemäß bilden die vom Laufrad entfernten Endbereiche des zweiten und des dritten Umfangswandbereichs gegenüberliegende Wandbereiche des Auslassbereichs, sodass dieser vollständig integriert und übergangslos angeformt ist. Dies führt ebenfalls zu einer Verbesserung der Strömungsverhältnisse.According to the invention, the end regions of the second and the third peripheral wall regions remote from the impeller form opposite wall regions of the outlet region, so that the latter is completely integrated and seamlessly formed. This also leads to an improvement in the flow conditions.

Der Auslassbereich besitzt an seinem gehäuseseitigen Anfang seine geringste Breite, die vorzugsweise geringer als der halbe Durchmesser des Laufrads ist. Diese Dimensionierung hat sich als besonders geeignet zur Erzielung eines hohen Drucks und eines hohen Volumenstroms erwiesen. Dies wird zweckmäßigerweise dadurch erreicht, dass der dritte Umfangswandbereich am gehäuseseitigen Anfang des Auslassbereichs eine zungenartig ins Gehäuseinnere gerichtete Gestalt besitzt, sodass diese Verengung am Beginn des Auslassbereichs durch die Umfangswandbereiche erzielt wird und keine zusätzlichen Elemente erforderlich sind.The outlet region has at its housing-side beginning its smallest width, which is preferably less than half the diameter of the impeller. This dimensioning has proven to be particularly suitable for achieving a high pressure and a high volume flow. This is expediently achieved in that the third peripheral wall region on the housing-side beginning of the outlet region has a tongue-like design into the housing interior, so that this narrowing is achieved at the beginning of the outlet region by the peripheral wall regions and no additional elements are required.

Das Gehäuse besteht vorzugsweise aus Kunststoff zur Erzielung einer einfachen und kostengünstigen Fertigung, wobei prinzipiell auch eine Ausführung aus Metall möglich ist.The housing is preferably made of plastic to achieve a simple and cost-effective production, in principle, a metal version is possible.

Der zweite Umfangswandbereich besitzt in einer bevorzugten Ausführung eine logarithmische Spiralform, die sich hinsichtlich der angestrebten Ziele als besonders vorteilhaft erwiesen hat.In a preferred embodiment, the second peripheral wall region has a logarithmic spiral shape, which has proved to be particularly advantageous with regard to the desired objectives.

Zur Verbesserung der angestrebten Eigenschaften trägt auch ein zwischen dem Laufrad oder dessen Schaufelkranz und den beiden Seitenwandungen gebildetes Labyrinth-Dichtsystem bei.To improve the desired properties also contributes between the impeller or its blade ring and the two side walls formed labyrinth sealing system.

Das erfindungsgemäße Radialgebläse eignet sich im Hinblick auf die beschriebenen Eigenschaften und Vorteile ganz besonders für den Einsatz in einem Hochdruck-Reinigungsgerät, bei dem das Laufrad des Radialgebläses und eine Hochdruckpumpe an derselben Antriebswelle eines Antriebsmotors fixiert sind und eine Pumpen-Gebläse-Einheit bilden. Bevorzugt ist dabei die Anordnung des Radialgebläses auf der einen und die der Hochdruckpumpe an der anderen Seite des Antriebsmotors.The radial fan according to the invention is particularly suitable for use in a high-pressure cleaning device in which the impeller of the radial fan and a high-pressure pump are fixed to the same drive shaft of a drive motor and form a pump-fan unit in view of the described properties and advantages. Preferred is the arrangement of the radial fan on one side and that of the high-pressure pump on the other side of the drive motor.

In einer vorteilhaften konstruktiven Ausgestaltung ist die Pumpen-Gebläse-Einheit auf einem insbesondere fahrbaren Chassis zusammen mit einem Heizkessel angeordnet, wobei das Radialgebläse zur Zuführung der Verbrennungsluft für einen Brenner mit dem Heizkessel verbunden ist und eine Flüssigkeitsleitung von der Hochdruckpumpe aus zur Aufheizung der Flüssigkeit im Heizkessel verläuft.In an advantageous structural embodiment, the pump-blower unit is arranged on a particular mobile chassis together with a boiler, wherein the radial fan for supplying the combustion air for a burner is connected to the boiler and a liquid line from the high pressure pump for heating the liquid in the Boiler is running.

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

Figur 1
eine Seitenansicht des Radialgebläses als Ausführungsbeispiel der Erfindung, bei dem die mit der Trennwand versehene Seitenwandung abgenommen, jedoch die Trennwand dargestellt ist,
Figur 2
eine zum Teil im Schnitt dargestellte Seitenansicht eines Hochdruck-Reinigungsgeräts, bei dem ein Heizkessel im Schnitt und das mit dem Heizkessel verbundene Radialgebläse entsprechend Figur 1 dargestellt ist, und
Figur 3
eine Draufsicht auf das Hochdruck-Reinigungsgerät mit schematisch dargestelltem Antriebsmotor und schematisch dargestellter Hochdruckpumpe.
An embodiment of the invention is illustrated in the drawing and explained in more detail in the following description. Show it:
FIG. 1
a side view of the radial fan as an embodiment of the invention, in which the side wall provided with the partition removed, but the partition wall is shown,
FIG. 2
a partially sectioned side view of a high pressure cleaning device in which a boiler in section and connected to the boiler Radial fan accordingly FIG. 1 is shown, and
FIG. 3
a plan view of the high pressure cleaning device with schematically illustrated drive motor and schematically illustrated high-pressure pump.

Bei dem in Figur 1 dargestellten Ausführungsbeispiel eines Radialgebläses 9 ist ein topfartiges Laufrad 10 drehbar in einem schneckenartigen Gehäuse 11 gelagert. Das Laufrad 10 besteht aus einem kreisscheibenartigen Boden 12, der mittig eine Nabe 13 zur Verbindung mit der Antriebswelle 16 eines nur in Figur 3 dargestellten Antriebsmotors 17 besitzt. Am radial äußeren Umfangsbereich des Bodens 12 erhebt sich senkrecht zu seiner Ebene eine Vielzahl von Schaufeln 14, die einen Schaufelkranz 15 bilden.At the in FIG. 1 illustrated embodiment of a radial fan 9 is a cup-shaped impeller 10 rotatably mounted in a helical housing 11. The impeller 10 consists of a circular disk-like bottom 12, the center of a hub 13 for connection to the drive shaft 16 of a only in FIG. 3 has shown drive motor 17. At the radially outer peripheral region of the bottom 12 rises perpendicular to its plane a plurality of blades 14 which form a blade ring 15.

Das Gehäuse 11 besteht aus einer schneckenartig geformten Umfangswandung 18, wobei sich ein teilkreisartig gekrümmter erster Umfangswandbereich 19 direkt mit einem sehr kleinen Spalt entlang des Schaufelkranzes 15 erstreckt, im Ausführungsbeispiel über einen Winkel von ca. 120°. Dieser Winkel kann jedoch variieren, wobei zwischen dem Schaufelkranz 15 und dem ersten Umfangswandbereich 19 eine Abdichtung nach Art einer Labyrinthdichtung vorgesehen sein kann.The housing 11 consists of a helically shaped peripheral wall 18, wherein a part-circular curved first peripheral wall portion 19 extends directly with a very small gap along the blade ring 15, in the embodiment over an angle of about 120 °. However, this angle may vary, wherein between the blade ring 15 and the first peripheral wall portion 19, a seal may be provided in the manner of a labyrinth seal.

Ab dem bezüglich der Drehrichtung A des Laufrads 10 hinteren Ende des ersten Umfangswändbereichs 19 schließt sich ein zweiter Umfangswandbereich 20 an, der sich spiralartig mit immer größer werdendem radialen Abstand zum Laufrad 10 bis zu einem Auslassbereich 21 erstreckt, der den Gebläseauslass bildet. Der zweite Umfangswandbereich 20 besitzt eine logarithmische Spiralform.From the rear end of the first circumferential wall area 19 with respect to the direction of rotation A of the impeller 10, a second circumferential wall area 20 connects, which extends in a spiral manner with increasing radial distance from the impeller 10 as far as an outlet area 21 which forms the fan outlet. The second peripheral wall portion 20 has a logarithmic spiral shape.

In der Gegenrichtung schließt sich an den ersten Umfangswandbereich 19 ein dritter Umfangswandbereich 22 an, der sich ebenfalls bis zum Auslassbereich 21 hin erstreckt. Dieser dritte Umfangswandbereich 22 ist S-förmig bis zu einer zungenartigen Einbuchtung 23 gekrümmt, wobei diese Einbuchtung 23 den Anfang des Auslassbereichs 21 bildet, der an diesem Anfang bezüglich der Auslassströmungsrichtung seine geringste Breite besitzt und sich dann in Auslassströmungsrichtung nach Art eines Diffusors in seiner Breite beziehungsweise seinem Querschnitt erweitert. Die beiden vom ersten Umfangswandbereich 19 entfernten Endbereiche des zweiten Umfangswandbereichs 20 und des dritten Umfangswandbereichs 22 bilden dabei gegenüberliegende Wandungen des Auslassbereichs 21, sodass dieser bezüglich der Umfangswandung 18 einstückig angeformt ist. Er kann in einer alternativen Ausführung auch angesetzt sein.In the opposite direction, adjoining the first peripheral wall region 19 is a third circumferential wall region 22 which likewise extends as far as the outlet region 21. This third peripheral wall region 22 is curved in an S shape as far as a tongue-like indentation 23, this indentation 23 forming the beginning of the outlet region 21, which has its smallest width at this beginning with respect to the outlet flow direction, and then in width in the outlet flow direction in the manner of a diffuser or expanded its cross section. The two end regions of the second peripheral wall region 20 and of the third peripheral wall region 22 remote from the first peripheral wall region 19 form opposite walls of the outlet region 21, so that this is integrally formed with respect to the circumferential wall 18. He may also be recognized in an alternative embodiment.

Die S-förmige Krümmung des dritten Auslasswandbereichs 22 besitzt ausgehend vom ersten Umfangswandbereich 19 zuerst eine gegensinnige und dann wieder eine gleichsinnige Krümmung. Der gleichsinnige Krümmungsbereich 24 (bezüglich des ersten Umfangswandbereichs 19) bildet ein Strömungsleitelement für den zum Laufrad 10 rückgeführten Teilstrom. Die Einbuchtung 23 fördert die Teilung der Strömung in diesen rückgeführten Teilstrom und den zum Auslassbereich 21 hin gelangenden Teilstrom.The S-shaped curvature of the third outlet wall region 22, starting from the first peripheral wall region 19, has first an opposing curvature and then again an equidirectional curvature. The same direction of curvature region 24 (with respect to the first peripheral wall portion 19) forms a flow guide for the return to the impeller 10 partial flow. The indentation 23 promotes the division of the flow into this recirculated partial flow and the partial flow reaching the outlet region 21.

Die Umfangswandung 18 bildet zusammen mit zwei die offenen Seiten der Umfangswandung 18 abdeckenden Seitenwandungen 25, 26 das Gehäuse 11. Gemäß Figur 3 sind diese Seitenwandungen 25, 26 jeweils einstückig mit einem axialen Teilbereich der Umfangswandung 18 verbunden, sodass ein zweiteiliges Gehäuse 11 gebildet wird. Die beiden Teile sind an einer Verbindungslinie 27 miteinander verschraubt oder auf eine andere Weise miteinander fixiert.The peripheral wall 18 forms together with two the open sides of the peripheral wall 18 covering side walls 25, 26, the housing 11. According to FIG. 3 These side walls 25, 26 are each integrally connected to an axial portion of the peripheral wall 18, so that a two-part housing 11 is formed. The two parts are at a connecting line 27 screwed together or fixed together in some other way.

Alternativ hierzu kann selbstverständlich die Umfangswandung 18 auch vollständig an einer der beiden Seitenwandungen 25, 26 einstückig angeformt werden, oder es liegt ein dreistückiges Gehäuse vor, bestehend aus Umfangswandung 18 und den beiden Seitenwandungen 25, 26.Alternatively, of course, the peripheral wall 18 may be integrally formed integrally on one of the two side walls 25, 26, or there is a three-piece housing, consisting of peripheral wall 18 and the two side walls 25, 26th

Das Laufrad 10 ist zu den beiden Seitenwandungen 25, 26 hin labyrinthdichtungsartig abgedichtet, wie dies in der EP 1022469 B1 oder in der EP 1022470 B1 näher beschrieben ist.The impeller 10 is sealed to the two side walls 25, 26 towards labyrinth seal, as shown in the EP 1022469 B1 or in the EP 1022470 B1 is described in more detail.

Von der Seitenwandung 26 aus (in Figur 1 nicht dargestellt) erstreckt sich eine Trennwand 28 ins Innere des topfartigen Laufrads 10 und unterteilt dessen Innenraum in einen ersten Saugraum V1 und einen zweiten Saugraum V2, der dem Umfangswandbereich 19 zugewandt ist. Diese Trennwand 28 erstreckt sich von der Seitenwandung 26 aus schräg bis zum Boden 12 des Laufrads 10 hin, wobei prinzipiell auch ein paralleler Verlauf zur Drehachse des Laufrads 10 möglich ist. Zur Abdichtung des Spalts zwischen dem Boden 12 des Laufrads 10 und dem diesem Boden 12 zugewandten Rand der Trennwand 28 kann dieser Rand mit Dichtelementen versehen sein, wie dies im angegebenen Stand der Technik näher beschrieben ist. Die Seitenwandung 26 ist mit einer Luftansaugöffnung 29 versehen, die im ersten Saugraum V1 mündet.From the side wall 26 (in FIG. 1 not shown), a partition wall 28 extends into the interior of the cup-shaped impeller 10 and divides the interior thereof into a first suction chamber V1 and a second suction chamber V2, which faces the peripheral wall region 19. This partition wall 28 extends from the side wall 26 obliquely out to the bottom 12 of the impeller 10, wherein in principle a parallel course to the axis of rotation of the impeller 10 is possible. To seal the gap between the bottom 12 of the impeller 10 and the bottom 12 of this facing edge of the partition wall 28, this edge may be provided with sealing elements, as described in more detail in the cited prior art. The side wall 26 is provided with an air intake opening 29, which opens in the first suction chamber V1.

Die Luftansaugöffnung 29 kann in verschiedener Gestalt und Ausgestaltung vorliegen. Verschiedene Varianten und Ausgestaltungen sind im eingangs angegebenen Stand der Technik näher beschrieben und können bei der vorliegenden Erfindung entsprechend eingesetzt werden.The air intake 29 may be in various shapes and configurations. Various variants and embodiments are described in detail in the prior art mentioned above and can be used accordingly in the present invention.

Die prinzipielle Wirkungsweise ist im angegebenen Stand der Technik gemäß der EP 1022469 B1 oder der EP 1022470 B1 ausführlich beschrieben, sodass sie im Folgenden vereinfacht und verkürzt dargestellt wird. Es handelt sich dabei um gezielt vereinigte Funktionen der Radial- und Querstromgebläsetechnik sowie der Seitenkanal-Verdichtertechnik, wobei diese Gebläsetechnik als HG-Technik bezeichnet wird. Je nach Auslegung und Ausführung dominiert die eine oder andere Technik.The principal mode of action is in the cited prior art according to the EP 1022469 B1 or the EP 1022470 B1 described in detail so that it is simplified and shortened in the following. These are specifically combined functions of the radial and cross-flow fan technology as well as the side channel compressor technology, whereby this fan technology is referred to as HG technology. Depending on the design and execution, one or the other technique dominates.

Bei rotierendem Laufrad 10 in der Drehrichtung A wirkt das Laufrad 10 im Bereich des ersten Saugraums V1 als Radialebläse. Außenluft wird durch die Luftansaugöffnung 28 in den ersten Saugraum V1 gesaugt und über den Umfangsbereich des ersten Saugraums V1 durch den Schaufelkranz 15 radial nach außen beschleunigt. Dieser beschleunigte Luftstrom teilt sich außen in einen Arbeitsstrom A1 und einen Arbeitsstrom A2 auf. Der Arbeitsstrom A1 gelangt wieder in den ersten Saugraum V1 zurück und wird durch die Radialgebläsewirkung erneut nach außen hin beschleunigt, wobei ein wesentlicher Teil dieses Arbeitsstroms am entgegengesetzten Ende des ersten Saugraums V1 in den Spiralerweiterungsbereich gelangt.With a rotating impeller 10 in the direction of rotation A, the impeller 10 acts in the region of the first suction chamber V1 as a radial fan. Outside air is sucked through the air intake opening 28 into the first suction chamber V1 and accelerated radially outward over the peripheral region of the first suction chamber V1 through the blade ring 15. This accelerated air flow is divided outside into a working flow A1 and a working flow A2. The working flow A1 returns to the first suction chamber V1 and is accelerated outwards again by the radial fan action, whereby a substantial part of this working flow reaches the spiral extension area at the opposite end of the first suction chamber V1.

Im Bereich des zweiten Saugraums V2 ist das Laufrad an seinen beiden axialen Stirnseiten durch die Seitenwandungen 25, 26 nicht abgeschlossen. Zum Innenraum hin bildet die Trennwand 28 einen dichten Abschluss, und an dem der Trennwand gegenüberliegenden ersten Umfangswandbereich 19 bildet diese die Abdichtung. Das Laufrad 10 arbeitet daher im Bereich des zweiten Saugraums V2 ausschließlich als Querstromgebläse, welches den Arbeitsstrom A2 ansaugt und dabei durch die S-förmige Krümmung des dritten Umfangswandbereichs 22 und durch die Einbuchtung 23 unterstützt wird. Dieser Arbeitsstrom A2 wird dann verdichtet und an der gegenüberliegenden Seite des Laufrads 10 wieder ausgeblasen. Das Gebläse arbeitet somit zum Teil als zweistufiges Gebläse mit einer durch den ersten Saugraum V1 gebildeten, als Radialgebläse arbeitenden ersten Stufe und einer durch den zweiten Saugraum V2 gebildeten, als Querstromgebläse arbeitenden zweiten Stufe.In the region of the second suction chamber V2, the impeller is not closed at its two axial end faces by the side walls 25, 26. Towards the interior, the partition wall 28 forms a tight seal, and at the partition wall opposite the first peripheral wall portion 19, this forms the seal. The impeller 10 therefore operates in the region of the second suction chamber V2 exclusively as a cross-flow fan, which sucks the working stream A2 and is supported by the S-shaped curvature of the third peripheral wall portion 22 and the indentation 23. This working stream A2 is then compressed and blown out again on the opposite side of the impeller 10. The fan works thus partly as a two-stage blower with a first stage formed by the first suction chamber V1, working as a radial fan and a second stage formed by the second suction chamber V2, acting as a cross-flow fan.

Der aus der zweiten Stufe, also aus dem Saugraum V2 austretende Arbeitsstrom A3 gelangt dann entlang des spiralförmig gekrümmten zweiten Umfangswandbereichs 20 zum Auslassbereich 21.The working stream A3 emerging from the second stage, that is to say from the suction chamber V2, then reaches the outlet region 21 along the spirally curved second peripheral wall region 20.

Die Ausbildung des Auslassbereichs 21 als Ausblasdiffusor infolge der beschriebenen Erweiterung in der Breite oder im Querschnitt bewirkt eine Erhöhung des statischen Gebläsedrucks.The formation of the outlet portion 21 as a discharge diffuser due to the described enlargement in width or in cross-section causes an increase in the static fan pressure.

Das in den Figuren 2 und 3 dargestellte Hochdruck-Reinigungsgerät weist einen ähnlichen Aufbau wie das aus der EP 0248282 B1 bekannte Hochdruck-Reinigungsgerät. Beim bekannten Gerät besitzt der Antriebsmotor eine vertikale Antriebswelle, während die Antriebswelle 16 des Antriebsmotors 17 gemäß den Figuren 2 und 3 horizontal angeordnet ist. Es ist selbstverständlich möglich, auch das im Zusammenhang mit der Erfindung beschriebene Hochdruck-Reinigungsgerät mit einer vertikalen Antriebswelle 16 auszubilden.That in the Figures 2 and 3 shown high pressure cleaning device has a similar structure as that of the EP 0248282 B1 known high pressure cleaning device. In the known device, the drive motor has a vertical drive shaft, while the drive shaft 16 of the drive motor 17 is arranged horizontally according to Figures 2 and 3. It is of course possible to form the high-pressure cleaning device described in connection with the invention with a vertical drive shaft 16.

Auf einem Chassis 40, das als mit Rädern versehenes fahrbares Chassis ausgebildet sein kann, ist eine Pumpen-Gebläse-Einheit 30 montiert, die aus dem Antriebsmotor 17 besteht, dessen Antriebswelle 16 auf der einen Seite das Laufrad 10 des Radialgebläses 9 und auf der gegenüberliegenden Seite eine Hochdruckpumpe 31 antreibt. Das Radialgebläse 9 beziehungsweise dessen Auslassbereich 21 ist an einen zylindrischen Heizkessel 32 angeschlossen, dessen Deckel 33 einen Gebläsebrenner 34 trägt, der mit Gas oder flüssigem Brennstoff betrieben wird. Die Hochdruckpumpe 31 ist über eine Verbindungsleitung 35 mit einem Rohrsystem 36 im Innern des Heizkessels 32 verbunden, wobei sich das Rohrsystem 36 in einer Vielzahl von Windungen entlang der zylindrischen Außenwand 37 des Heizkessels 32 erstreckt. Diese Windungen sind im dargestellten Ausführungsbeispiel zweilagig ausgebildet, wobei selbstverständlich auch eine andere Anzahl von Lagen möglich ist.On a chassis 40, which may be formed as a wheeled mobile chassis, a pump-blower unit 30 is mounted, which consists of the drive motor 17, the drive shaft 16 on one side of the impeller 10 of the radial fan 9 and on the opposite Side a high-pressure pump 31 drives. The radial fan 9 or its outlet region 21 is connected to a cylindrical heating boiler 32, the cover 33 of which carries a fan burner 34 which is equipped with gas or liquid fuel is operated. The high-pressure pump 31 is connected via a connecting line 35 to a pipe system 36 in the interior of the boiler 32, wherein the pipe system 36 extends in a plurality of turns along the cylindrical outer wall 37 of the boiler 32. These turns are formed in two layers in the illustrated embodiment, of course, a different number of layers is possible.

Die vom Radialgebläse 9 erzeugte Luftströmung strömt im Heizkessel 32 entlang der Außenwand 37 nach oben und führt dem Gebläsebrenner 34 die erforderliche Verbrennungsluft zu. Die Brennerflamme erstreckt sich vom Gebläsebrenner 34 aus vertikal nach unten und heizt das Rohrsystem 36 beziehungsweise die sich darin befindliche Flüssigkeit auf. Die aufgeheizte Flüssigkeit wird dann im Durchlaufverfahren durch die Hochdruckpumpe 31 zu einer nicht dargestellten Auslass-Pumpendüse geleitet, die üblicherweise an einem Hochdruckschlauch angebracht ist.The air flow generated by the radial fan 9 flows upward in the boiler 32 along the outer wall 37 and supplies the required combustion air to the fan burner 34. The burner flame extends vertically downward from the blower burner 34 and heats the pipe system 36 or the liquid therein. The heated liquid is then passed in a continuous process through the high-pressure pump 31 to an outlet pump nozzle, not shown, which is usually mounted on a high-pressure hose.

Seitlich am Radialgebläse 9 ist noch eine Kraftstoffpumpe 38 zur Kraftstoffzuführung zum Gebläsebrenner 34 an der Antriebswelle 16 beziehungsweise an der Nabe 13 des Laufrads 10 angeschlossen und wird simultan angetrieben.Laterally on the radial fan 9, a fuel pump 38 is still connected to the fuel supply to the fan burner 34 on the drive shaft 16 and the hub 13 of the impeller 10 and is driven simultaneously.

Am Ausgang des Radialgebläses 9 beziehungsweise am Ausgang des Auslassbereichs 21 ist ein Regulierelement 39 angeordnet, durch das der erzeugte Luftstrom je nach Erfordernis reguliert werden kann.At the outlet of the radial blower 9 or at the outlet of the outlet region 21, a regulating element 39 is arranged, by means of which the air flow generated can be regulated as required.

Als Antriebsmotor 17 wird üblicherweise ein 4-poliger Asynchronmotor eingesetzt, der bei einem 50 Hz-Wechselstrom eine Drehzahl von weniger als 1.500 U/min bewirkt. Prinzipiell können auch elektronisch gesteuerte Motoren eingesetzt werden, die eine größere Variabilität der Drehzahl ermöglichen.As a drive motor 17, a 4-pole asynchronous motor is usually used, which causes a speed of less than 1,500 U / min in a 50 Hz alternating current. in principle Also electronically controlled motors can be used, which allow a greater variability of the speed.

Das Gehäuse 11 des Radialgebläses 9 besteht zweckmäßigerweise aus Kunststoff, um einerseits eine kostengünstige Herstellung und andererseits ein geringes Gewicht zu erreichen. Prinzipiell ist jedoch auch eine Metallausführung möglich.The housing 11 of the radial fan 9 is suitably made of plastic, on the one hand to achieve a cost-effective production and on the other hand a low weight. In principle, however, a metal version is possible.

Claims (9)

  1. Radial fan with a pot-like impeller (10), which is provided on its periphery with a blade rim (15), with a housing (11) accommodating the impeller (10) and with a peripheral wall (18) which, starting from an arc-like curved first peripheral wall section (19) running directly along the blade rim (15), has on one side in the direction of rotation of the impeller (10) a second peripheral section (20) with a spiral-like steadily enlarging radial distance from the impeller (10) as far as an outlet area (21), and on the other side, against the direction of rotation of the impeller (10), has a third peripheral wall section (22), similarly extending up to the outlet area (21), with two side walls (25, 26) covering the axial end faces of the impeller (10), wherein a partition (28) provided on one of the side walls (26) engages in the pot-like impeller (10) and divides its interior into a first (V1) and a second suction chamber (V2), and wherein the first suction chamber (V1) is assigned a suction intake (29) and the second suction chamber (V2) directly faces the first peripheral wall section (19) running along the blade rim (15), wherein the third peripheral wall section (22), starting from the first peripheral wall section (19), has an S-shaped curve up to the outlet area (21), and its subsection (24) curved in the same direction as the first peripheral wall section (19) forms a flow control element for an airflow (A2) fed back to the second suction chamber (V2), and wherein the outlet area (21) enlarges in cross-section in the outlet flow direction in the manner of a diffuser, characterised in that the end sections of the second and third peripheral wall sections (20, 22) furthest away from the impeller (10) form opposite wall sections of the outlet area (21), so that the outlet area is formed completely integrated and transition-free.
  2. Radial fan according to claim 1, characterised in that the outlet area (21) has its greatest width, which is preferably less than half the diameter of the impeller (10), at its housing-side starting point.
  3. Radial fan according to any of the preceding claims, characterised in that the third peripheral wall section (22) at the housing-side start of the outlet area (21) has a shape (23) directed tongue-like into the housing interior.
  4. Radial fan according to any of the preceding claims, characterised in that the housing is made of plastic or metal.
  5. Radial fan according to any of the preceding claims, characterised in that the second peripheral wall section (20) has a logarithmic spiral form.
  6. Radial fan according to any of the preceding claims, characterised in that a labyrinth seal system is formed between the impeller (10) or its blade rim (15) and the two side walls (25, 26).
  7. High-pressure cleaning machine with a radial fan (9) according to any of the preceding claims, characterised in that the impeller (10) of the radial fan (9) and a high-pressure pump (31) are fixed on the same drive shaft (16) of a drive motor (17) and form a pump-fan unit (30).
  8. High-pressure cleaning machine according to claim 7, characterised in that the radial fan (9) is mounted on one side and the high-pressure pump (31) on the other side of the drive motor (17).
  9. High-pressure cleaning machine according to claim 7 or 8, characterised in that the pump-fan unit (30) is mounted on a chassis (40), in particular mobile, together with a heating boiler (32), wherein the radial fan (9) is connected to the heating boiler (32) to supply combustion air for a burner (34), and a fluid line (35, 36) runs from the high-pressure pump (31) for heating the fluid in the heating boiler (32).
EP07819773.8A 2006-12-28 2007-11-13 Radial fan and a high-pressure cleaning device having a radial fan Not-in-force EP2104787B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006061756A DE102006061756A1 (en) 2006-12-28 2006-12-28 Radial blower i.e. HG-blower, for high-pressure cleaning device, has circumferential wall region curved from outlet wall region in S-shape, and outlet region extended in flow direction to diffuser in cross sections
PCT/EP2007/009787 WO2008083787A1 (en) 2006-12-28 2007-11-13 Radial fan and a high-pressure cleaning device having a radial fan

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EP2104787A1 EP2104787A1 (en) 2009-09-30
EP2104787B1 true EP2104787B1 (en) 2016-05-04

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EP07819773.8A Not-in-force EP2104787B1 (en) 2006-12-28 2007-11-13 Radial fan and a high-pressure cleaning device having a radial fan

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US (1) US8813689B2 (en)
EP (1) EP2104787B1 (en)
CN (1) CN101652572B (en)
DE (1) DE102006061756A1 (en)
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WO (1) WO2008083787A1 (en)

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Publication number Publication date
DK2104787T3 (en) 2016-08-22
DE102006061756A1 (en) 2008-07-03
CN101652572B (en) 2013-08-21
US8813689B2 (en) 2014-08-26
WO2008083787A1 (en) 2008-07-17
CN101652572A (en) 2010-02-17
EP2104787A1 (en) 2009-09-30
US20110044808A1 (en) 2011-02-24

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