EP1703139B1 - Centrifugal ventilator - Google Patents

Centrifugal ventilator Download PDF

Info

Publication number
EP1703139B1
EP1703139B1 EP06004223A EP06004223A EP1703139B1 EP 1703139 B1 EP1703139 B1 EP 1703139B1 EP 06004223 A EP06004223 A EP 06004223A EP 06004223 A EP06004223 A EP 06004223A EP 1703139 B1 EP1703139 B1 EP 1703139B1
Authority
EP
European Patent Office
Prior art keywords
radial fan
fan according
casing
side part
radial
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.)
Active
Application number
EP06004223A
Other languages
German (de)
French (fr)
Other versions
EP1703139A1 (en
Inventor
Rudolf Tungl
Roland Keber
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.)
Ebm Papst Landshut GmbH
Original Assignee
Ebm Papst Landshut 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
Application filed by Ebm Papst Landshut GmbH filed Critical Ebm Papst Landshut GmbH
Publication of EP1703139A1 publication Critical patent/EP1703139A1/en
Application granted granted Critical
Publication of EP1703139B1 publication Critical patent/EP1703139B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • 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
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers 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 with a side part and a pot-like housing part having housing and a fan arranged in the housing, with radially extending blades.
  • Such devices for conveying gaseous media are generally used in devices which have a large flow resistance.
  • These can be ceramic surface burners, which are used in the latest development in gas boilers.
  • Such gas boilers have a flow resistance of the order of 200 pascals and more. To overcome the large flow resistance, efforts are being made to produce the steepest possible pressure volume flow characteristics in a radial fan.
  • Radial blower of the type mentioned are known in the art. So is in the EP 0 410 271 A2 a device for conveying a gaseous medium known in which the housing part has a holder for the electric motor and the side part is provided with an inlet opening for the influx of the blower air.
  • the invention has for its object to provide a radial fan, which is particularly space-saving, inexpensive and easy to manufacture with the same performance.
  • the shape in the housing part is greater than in the side part.
  • the ratio height / diameter of the housing between 1: 7 and 1: 9 is selected. It is particularly advantageous if the ratio height / diameter of the housing is 1: 8.
  • a favorable embodiment can provide that the blow-out channel is formed on the housing part.
  • the housing has a protruding into the pressure chamber in tongue. It is favorable that the tongue is formed on the housing part in the form of a ramp which rises on the side wall of the housing part in the flow direction. By attaching a tongue, the pressure chamber is shielded in the blower against the fan, so that pressure losses can be reduced.
  • the tongue may be formed on the side part in the form of a ramp and to rise in the direction of flow toward the housing part.
  • the tongue By forming the tongue as a ramp, the gap between the fan and the side wall of the housing part can be reduced, without causing an increase in the noise level.
  • blower in a further embodiment of the blower can be provided to use a fan with a hub and a front cover plate, in which case the blades of the fan are held only on the hub and the cover plate.
  • a rear carrier disc can be omitted. This results in a cost-effective production of the fan and thus the radial fan as a whole.
  • a radial fan is shown in side view, which has a housing 4 in which a fan 5 is received.
  • the housing 4 consists of a side part 2 and a pot-like housing part 3.
  • an electric motor 7 is vibration-damped, which drives the fan 5 via its motor shaft.
  • the housing has a, in conjunction with Fig. 3 closer described pressure chamber 8.
  • the fan 5 forms together with the pressure chamber 8, as also in Fig. 3 an idealized Venturi nozzle, wherein the narrowest cross-section of this Venturi nozzle in the transition between the fan and the housing is located.
  • the formation 19 is larger in the illustrated embodiment in the housing part 3 as in the side part. 2
  • Fig. 2 is a Forderansicht the radial fan shown.
  • it is in the illustrated embodiment is a fan with backward curved blades.
  • a connection 12 in the form of a flange 12 is provided at the free end of the Ausblashimnals 13 .
  • the plane 11 of the terminal 12 forms in the illustrated embodiment with the theoretical blow-out direction - arrow A - an angle ⁇ ⁇ 90 °.
  • the angle ⁇ 86.4 °.
  • Fig. 3 is schematically illustrated the blower housing 4, in which the fan 5 is used.
  • the spiral pressure chamber is shielded in the region of the blow-out channel 13 by the tongue 14 against the fan 5.
  • ⁇ 3.6 °
  • the ratio H (largest blade height) to D (diameter of the spiral) in the illustrated embodiment is 0.12. It has been found during test series that deviations from this ratio still provide useful results, however, the value of 0.12 for a spiral diameter of 145.3 mm and a required volumetric flow rate of 11 I / s is the optimum measure. This power is achieved at a speed of 5250 rpm and a shaft power of 21 W.
  • Fig. 4 is schematically reproduced the venturi nozzle principle, wherein the area 9 as a fan wheel space in addition to the speed of the fan through the structural design, a further acceleration of the air flow causes, whereas the pressure chamber 8 causes the pressure increase and calm the air flow.
  • the fan 5 is provided with a hub 17, wherein the blades 6 are held on the hub 17 and on a cover plate 18. It is understood that according to desired performance requirements, other fan wheels can be used.

Abstract

The casing (4) has a side portion (2), pot-shaped casing portion (3) to form a casing scroll and a pressure chamber. The chamber has an impeller wheel (5) with radially extending blades. The ratio of the greatest blade height (H) to the greatest diameter (D) of the scroll is between 0.08-0.3.

Description

Die Erfindung betrifft ein Radialgebläse mit einem ein Seitenteil und ein topfartiges Gehäuseteil aufweisenden Gehäuse und einem in dem Gehäuse angeordneten Lüfterrad, mit sich radial erstreckenden Schaufeln.The invention relates to a radial fan with a side part and a pot-like housing part having housing and a fan arranged in the housing, with radially extending blades.

Derartige Vorrichtungen zum Fördern von gasförmigen Medien werden in der Regel eingesetzt in Vorrichtungen, die einen großen Strömungswiderstand besitzen. Es kann sich dabei um keramische Flächenbrenner handeln, die in der neuesten Entwicklung in Gaskesseln verwendet werden. Derartige Gasheizkessel weisen einen Strömungswiderstand in der Größenordnung von 200 Paskal und mehr auf. Zur Überwindung des großen Strömungswiderstands ist man bestrebt, möglichst steile Druckvolumen-Stromkennlinien bei einem Radialgebläse zu erzeugen.Such devices for conveying gaseous media are generally used in devices which have a large flow resistance. These can be ceramic surface burners, which are used in the latest development in gas boilers. Such gas boilers have a flow resistance of the order of 200 pascals and more. To overcome the large flow resistance, efforts are being made to produce the steepest possible pressure volume flow characteristics in a radial fan.

Radialgebläse der genannten Gattung sind im Stand der Technik bekannt. So ist in der EP 0 410 271 A2 eine Vorrichtung zum Fördern eines gasförmigen Mediums bekannt, bei dem das Gehäuseteil eine Halterung für den Elektromotor aufweist und das Seitenteil mit einer Einlassöffnung für den Zustrom der Gebläseluft versehen ist.Radial blower of the type mentioned are known in the art. So is in the EP 0 410 271 A2 a device for conveying a gaseous medium known in which the housing part has a holder for the electric motor and the side part is provided with an inlet opening for the influx of the blower air.

Die Druckschrift US 2004/0062646 A1 , die als nächstliegenden Stand der Technik angesehen wird, offenbart die Merkmale des Oberbegriffs des Anspruchs 1.The publication US 2004/0062646 A1 , which is considered to represent the closest prior art, discloses the features of the preamble of claim 1.

Der Erfindung liegt die Aufgabe zugrunde, ein Radialgebläse anzugeben, das bei möglichst gleicher Leistung besonders raumsparend, kostengünstig und einfach herzustellen ist.The invention has for its object to provide a radial fan, which is particularly space-saving, inexpensive and easy to manufacture with the same performance.

Die Aufgabe wird bei einem Gebläse der genannten Gattung durch die im Anspruch 1 angegebenen Merkmale gelöst.The object is achieved in a fan of the type mentioned by the features specified in claim 1.

Die erfindungsgemäße Lösung sieht daher vor, ein Radialgebläse mit einem ein Seitenteil und ein topfartiges Gehäuseteil aufweisendes Gehäuse zu schaffen, mit einem darin angeordneten Lüfterrad, einem am Seitenteil angeordneten Elektromotor und mit einem von Gehäuseteil und Seitenteil gebildeten Druckraum, der mit dem Lüfterrad-Raum zwischen den Schaufeln im Querschnitt eine Düse nach Art einer Venturi-Düse bildet, wobei das Verhältnis größte Schaufelhöhe (H) / größter Durchmesser (D) der Spirale im Wesentlichen zwischen H/D = 0,08 und H/D = 0,3 beträgt. Durch die besondere Gestaltung der Druckraumgeometrie und der Auslegung der Schaufeln des Lüfterrads im Verhältnis zum Durchmesser der Spirale des Druckraums, werden die gewünschten Leistungen in hervorragender Weise erreicht. Vorzugsweise beträgt das Verhältnis H/D = 0,1, besonders bevorzugt beträgt jedoch das Verhältnis H/D = 0,12. Dies entspricht bei einer konstruktiven Ausgestaltung einem größten Durchmesser von ca. 145,3 mm bei einer Schaufelhöhe von 18 mm.The solution according to the invention therefore provides for providing a radial fan with a housing having a side part and a cup-shaped housing part, with a fan wheel arranged therein, an electric motor arranged on the side part and with a pressure chamber formed by the housing part and side part which is connected to the fan wheel space between the blade forms in cross-section a nozzle in the manner of a Venturi nozzle, wherein the ratio of the largest blade height (H) / largest diameter (D) of the spiral is substantially between H / D = 0.08 and H / D = 0.3. Due to the special design of the pressure chamber geometry and the design of the blades of the fan in relation to the diameter of the spiral of the pressure chamber, the desired performance can be achieved in an excellent manner. Preferably, the ratio H / D = 0.1, more preferably, however, the ratio H / D = 0.12. This corresponds to a design of a largest diameter of about 145.3 mm with a blade height of 18 mm.

Besonders vorteilhaft ist es, wenn im Gehäuseteil und/oder im Seitenteil Ausformungen ausgebildet sind, durch die sich der spiralenförmige Druckraum kontinuierlich dreidimensional erweitert.It is particularly advantageous if formations are formed in the housing part and / or in the side part through which the spiral-shaped pressure chamber widens continuously in three dimensions.

Vorzugsweise ist die Ausformung im Gehäuseteil größer als im Seitenteil. Durch die Wahl der Gehäusegestalt und die Anordnung der größeren Ausformung im Gehäuseteil ergibt sich die Möglichkeit, auf der dem Motor abgewandten Seite des GebläseGehäuses in gewünschter Weise Ausformungen anzubringen, ohne dass eine räumliche Einschränkung gegeben wäre.Preferably, the shape in the housing part is greater than in the side part. By choosing the housing shape and the arrangement of the larger shape in the housing part, there is the possibility to attach on the side facing away from the engine of the blower housing in the desired manner, without a spatial restriction would be given.

Günstigerweise wird das Verhältnis Höhe/Durchmesser des Gehäuses zwischen 1:7 und 1:9 gewählt. Besonders vorteilhaft ist es, wenn das Verhältnis Höhe/Durchmesser des Gehäuses 1:8 beträgt.Conveniently, the ratio height / diameter of the housing between 1: 7 and 1: 9 is selected. It is particularly advantageous if the ratio height / diameter of the housing is 1: 8.

Besonders vorteilhaft ist es, wenn bei einer Drehzahl von n = 5250 ein Luftvolumenstrom von 11 L/s geliefert wird. Dabei ergibt sich eine Luftleistungskennzahl von pa = 1050 (Druck), der bei einer Drehzahl von 5250 und dem genannten Luftvolumenstrom von 11 L/s eine Wellenleistung von ca. 21 W erfordert. Dies ist im Vergleich zum Stand der Technik ein sehr niedriger Wert.It is particularly advantageous if, at a speed of n = 5250, an air volume flow of 11 L / s is supplied. This results in an air flow rate of pa = 1050 (pressure), which requires a shaft power of about 21 W at a speed of 5250 and the said air volume flow of 11 L / s. This is a very low value compared to the prior art.

Eine weitere vorteilhafte Ausgestaltung ist darin zu sehen, dass die Ebene des Anschlusses am Ausblaskanal des Gehäuses in einem Winkel α≤90° zur Ausblasrichtung (Pfeil A) steht. Besonders vorteilhaft ist es, wenn der Winkel zwischen 90° und 83° liegt, wobei besonders bevorzugt α = 86,4° beträgt.A further advantageous embodiment can be seen in the fact that the plane of the connection at the outlet channel of the housing is at an angle α≤90 ° to the discharge direction (arrow A). It is particularly advantageous if the angle lies between 90 ° and 83 °, with α = 86.4 ° being particularly preferred.

Eine günstige Ausführungsform kann vorsehen, dass der Ausblaskanal am Gehäuseteil ausgebildet ist.A favorable embodiment can provide that the blow-out channel is formed on the housing part.

Von besonderem Vorteil ist, dass das Gehäuse eine in den Druckraum hinein ragende Zunge aufweist. Dabei ist es günstig, dass die Zunge am Gehäuseteil in Form einer Rampe ausgebildet ist, die auf der Seitenwand des Gehäuseteils in Strömungsrichtung ansteigt. Durch die Anbringung einer Zunge wird der Druckraum im Ausblasbereich gegen das Lüfterrad abgeschirmt, so dass Druckverluste reduziert werden können.It is particularly advantageous that the housing has a protruding into the pressure chamber in tongue. It is favorable that the tongue is formed on the housing part in the form of a ramp which rises on the side wall of the housing part in the flow direction. By attaching a tongue, the pressure chamber is shielded in the blower against the fan, so that pressure losses can be reduced.

Bei einer anderen Ausführungsform kann es vorteilhaft sein, dass die Zunge am Seitenteil in Form einer Rampe ausgebildet ist und in Strömungsrichtung zum Gehäuseteil hin ansteigt. Durch die Ausbildung der Zunge als Rampe kann der Spalt zwischen Lüfterrad und Seitenwand des Gehäuseteils verringert werden, ohne dass es zu einem Ansteigen des Geräuschpegels kommt.In another embodiment, it may be advantageous for the tongue to be formed on the side part in the form of a ramp and to rise in the direction of flow toward the housing part. By forming the tongue as a ramp, the gap between the fan and the side wall of the housing part can be reduced, without causing an increase in the noise level.

Bei einer weiteren Ausführungsform des Gebläses kann vorgesehen sein, ein Lüfterrad mit einer Nabe und einer vorderen Deckscheibe zu verwenden, wobei dann die Schaufeln des Lüfterrads lediglich an der Nabe und der Deckscheibe gehalten sind. Eine rückwärtige Trägerscheibe kann entfallen. Hierdurch ergibt sich eine kostengünstige Herstellung des Lüfterrads und somit des Radialgebläses insgesamt.In a further embodiment of the blower can be provided to use a fan with a hub and a front cover plate, in which case the blades of the fan are held only on the hub and the cover plate. A rear carrier disc can be omitted. This results in a cost-effective production of the fan and thus the radial fan as a whole.

Im Folgenden wird die Erfindung anhand in der Zeichnung dargestellter Ausführungsbeispiele näher erläutert. Es zeigen:

Fig. 1
eine Seitenansicht eines Radialgebläses,
Fig. 2
eine Forderansicht auf das Radialgebläse mit Motor und Anschlussflansch,
Fig. 3
eine schematische Darstellung mit Druckraum, und
Fig. 4
eine schematische Darstellung der Zuordung Lüfterrad-Raum - Druckraum im Schnitt.
In the following the invention will be explained in more detail with reference to embodiments shown in the drawing. Show it:
Fig. 1
a side view of a radial fan,
Fig. 2
a Forderansicht on the radial fan with motor and flange,
Fig. 3
a schematic representation with pressure chamber, and
Fig. 4
a schematic representation of the assignment fan wheel space - pressure chamber in section.

In Fig. 1 ist ein Radialgebläse in Seitenansicht dargestellt, das ein Gehäuse 4 aufweist, in dem ein Lüfterrad 5 aufgenommen ist. Das Gehäuse 4 besteht aus einem Seitenteil 2 und einem topfartigen Gehäuseteil 3. An dem Seitenteil 2 ist ein Elektromotor 7 schwingungsgedämpft gehalten, der über seine Motorwelle das Lüfterrad 5 antreibt. Das Gehäuse weist einen, in Verbindung mit Fig. 3 näher beschriebenen Druckraum 8 auf. Das Lüfterrad 5 bildet zusammen mit dem Druckraum 8, wie ebenfalls in Fig. 3 näher erläutert, eine idealisierte Venturi-Düse, wobei der engste Querschnitt dieser Venturi-Düse im Übergang zwischen Lüfterrad und Gehäuse liegt.In Fig. 1 a radial fan is shown in side view, which has a housing 4 in which a fan 5 is received. The housing 4 consists of a side part 2 and a pot-like housing part 3. On the side part 2, an electric motor 7 is vibration-damped, which drives the fan 5 via its motor shaft. The housing has a, in conjunction with Fig. 3 closer described pressure chamber 8. The fan 5 forms together with the pressure chamber 8, as also in Fig. 3 an idealized Venturi nozzle, wherein the narrowest cross-section of this Venturi nozzle in the transition between the fan and the housing is located.

Im Gehäuseteil 3 und/oder im Seitenteil 2 sind Ausformungen 19 ausgebildet, durch die sich der spiralenförmige Druckraum 8 kontinuierlich dreidimensional erweitert.In the housing part 3 and / or in the side part 2 formations 19 are formed through which the spiral-shaped pressure chamber 8 extends continuously in three dimensions.

Die Ausformung 19 ist im dargestellten Ausführungsbeispiel im Gehäuseteil 3 größer als im Seitenteil 2.The formation 19 is larger in the illustrated embodiment in the housing part 3 as in the side part. 2

In Fig. 2 ist eine Forderansicht des Radialgebläses dargestellt. Das Gebläse einen Ausblaskanal 13 und eine Ansaugöffnung 20 auf. Wie in der Ansaugöffnung zu erkennen ist, handelt es sich bei dem dargestellten Ausführungsbeispiel um ein Lüfterrad mit rückwärts gekrümmten Schaufeln. Am freien Ende des Ausblaskänals 13 ist ein Anschluss 12 in Form eines Flansches 12 vorgesehen. Die Ebene 11 des Anschlusses 12 bildet im dargestellten Ausführungsbeispiel mit der theoretischen Ausblasrichtung - Pfeil A - einen Winkel α ≤ 90°. In einer besonders bevorzugten Ausführungsform beträgt der Winkel α = 86,4°. Durch diese Anordnung wird der austretende Luftstrom noch weiter druckvermindernd geführt, da durch die winkelmäßige Anordnung zwischen Kanalfortsetzung und Ausblaskanal die Spiralkontur des Gebläses fortgesetzt wird. Hiermit geht gleichzeitig eine Druckerhöhung einher. In der zeichnerischen Darstellung laufen die theoretische Ausblasrichtung - Pfeil A - und die Seitenwand 16 des Kanals - durch zwei Parallelstriche gekennzeichnet - parallel zueinander. Ebenso - verlaufen die senkrechte Mittelachse des Gebläses und die Ebene 11 parallel zueinander.In Fig. 2 is a Forderansicht the radial fan shown. The blower on a blow-out 13 and a suction port 20. As can be seen in the intake, it is in the illustrated embodiment is a fan with backward curved blades. At the free end of the Ausblaskänals 13 a connection 12 in the form of a flange 12 is provided. The plane 11 of the terminal 12 forms in the illustrated embodiment with the theoretical blow-out direction - arrow A - an angle α ≤ 90 °. In a particularly preferred embodiment, the angle α = 86.4 °. By this arrangement, the exiting air flow is performed even further pressure reducing, since the spiral contour of the fan is continued by the angular arrangement between the channel continuation and blow-out. This is accompanied by an increase in pressure at the same time. In the diagram, the theoretical discharge direction - arrow A - and the side wall 16 of the channel - indicated by two parallel lines - run parallel to one another. As well - the vertical center axis of the fan and the plane 11 are parallel to each other.

In Fig. 3 ist schematisch das Gebläse-Gehäuse 4 dargestellt, in dem das Lüfterrad 5 eingesetzt ist. Der spiralförmige Druckraum wird im Bereich des Ausblaskanals 13 durch die Zunge 14 gegen das Lüfterrad 5 abgeschirmt. In dieser Darstellung ist mit β = 3,6° der Komplementärwinkel zu dem Winkel α eingezeichnet.In Fig. 3 is schematically illustrated the blower housing 4, in which the fan 5 is used. The spiral pressure chamber is shielded in the region of the blow-out channel 13 by the tongue 14 against the fan 5. In this illustration, with β = 3.6 °, the complementary angle to the angle α is drawn.

Erfindungsgemäß beträgt das Verhältnis H (größte Schaufelhöhe) zu D (Durchmesser der Spirale) im dargestellten Ausführungsbeispiel 0,12. Es hat sich während Testserien herausgestellt, dass Abweichungen von diesem Verhältnis noch brauchbare Ergebnisse liefern, jedoch ist der Wert 0,12 bei einem Spiraldurchmesser von 145,3 mm und einer geforderten Volumenstromkennzahl von 11 I/s das optimale Maß. Diese Leistung wird erreicht bei einer Drehzahl von 5250 U/min und einer Wellenleistung von 21 W.According to the invention, the ratio H (largest blade height) to D (diameter of the spiral) in the illustrated embodiment is 0.12. It has been found during test series that deviations from this ratio still provide useful results, however, the value of 0.12 for a spiral diameter of 145.3 mm and a required volumetric flow rate of 11 I / s is the optimum measure. This power is achieved at a speed of 5250 rpm and a shaft power of 21 W.

In Fig. 4 ist schematisch das Venturi-Düsen-Prinzip wiedergegeben, wobei der Bereich 9 als Lüfterrad-Raum zusätzlich zur Drehzahl des Lüfterrads durch die konstruktive Gestaltung, eine weitere Beschleunigung des Luftstroms bewirkt, wohingegen der Druckraum 8 die Druckerhöhung und Beruhigung des Luftstroms herbeiführt.In Fig. 4 is schematically reproduced the venturi nozzle principle, wherein the area 9 as a fan wheel space in addition to the speed of the fan through the structural design, a further acceleration of the air flow causes, whereas the pressure chamber 8 causes the pressure increase and calm the air flow.

Bei der in den Figuren dargestellten Ausführungsform ist, wie schematisch in Fig. 4 wiedergegeben, das Lüfterrad 5 mit einer Nabe 17 versehen, wobei die Schaufeln 6 an der Nabe 17 und an einer Deckscheibe 18 gehalten sind. Es versteht sich, dass entsprechend gewünschter Leistungsanforderungen auch andere Lüfterräder Verwendung finden können.In the embodiment shown in the figures, as shown schematically in FIG Fig. 4 reproduced, the fan 5 is provided with a hub 17, wherein the blades 6 are held on the hub 17 and on a cover plate 18. It is understood that according to desired performance requirements, other fan wheels can be used.

Bezugszeichenliste:LIST OF REFERENCE NUMBERS

11
Radialgebläsecentrifugal blower
22
Seitenteilside panel
33
topfartiges Gehäuseteilcup-shaped housing part
44
Gehäusecasing
55
Lüfterradfan
66
Schaufelnshovel
77
Elektromotorelectric motor
88th
Druckraumpressure chamber
99
Lüfterrad-RaumFan room
1010
Düsejet
1111
Ebene des Anschlusses 12Level of connection 12
1212
Anschlussconnection
1313
Ausblaskanalblow-out
Pfeil AArrow A.
AusblasrichtungDischarge
1414
Zungetongue
1515
Ramperamp
1616
Seitenwand des Gehäuseteils 3Side wall of the housing part 3
1717
Nabehub
1818
Deckscheibecover disc

Claims (16)

  1. A radial fan (1) comprising a casing (4) having a side part (2) and a pot-shaped casing part (3), a fan wheel (5) arranged inside the casing and having radially extending blades (6), an electric motor (7) arranged at the side part, and a compression space (8) formed by the casing part and the side part, characterized in that the compression space together with the fan wheel space between the blades (6) in its cross-section forms a nozzle (8') of a Venturi nozzle type, and that the relation largest blade height (H)/largest diameter (D) of the spiral substantially is in the range between H/D = 0.08 and H/D = 0.3.
  2. The radial fan according to claim 1, characterized in that the relation largest blade height (H)/largest diameter (D) of the spiral preferably is substantially H/D = 0.1, particularly preferred H/D = 0.12.
  3. The radial fan according to claim 1 or 2, characterized in that recesses (19) are formed in the casing part (3) and/or the side part (2) by means of which the spiral-shaped compression space (8) is continuously enlarged in a three-dimensional manner.
  4. The radial fan according to claim 3, characterized in that the recess (19) in the casing part (3) is larger than in the side part (2).
  5. The radial fan according to one of the preceding claims, characterized in that the relation height/diameter of the casing (4) is between 1:7 and 1:9.
  6. The radial fan according to claim 5, characterized in that the relation height/diameter of the casing (4) is substantially 1:8.
  7. The radial fan according to one of the preceding claims, characterized in that an air volume flow of about 11 l/s is delivered at a speed of about n = 5250.
  8. The radial fan according to one of the preceding claims, characterized in that the performance characteristics l/s = 11 (volume flow) and Pa = 1050 (pressure) are obtained at a speed of n = 5250 and a shaft output of about 21 W.
  9. The radial fan according to one of the preceding claims, characterized in that the plane (11) of the connecting portion (12) at the exhaust passage (13) of the casing (4) is arranged at an angle α ≤ 90° to the exhaust direction (arrow A).
  10. The radial fan according to claim 9, characterized in that the plane of the connecting portion (12) at the exhaust passage (13) of the casing (4) is arranged at an angle of 90° > α ≥ 83°, preferably α = 86.4° to the exhaust direction (arrow A).
  11. The radial fan according to one of the preceding claims, characterized in that the exhaust passage (13) is formed in the casing part (3).
  12. The radial fan according to one of the preceding claims, characterized in that the casing (4) comprises a tab (14) projecting into the compression space (8).
  13. The radial fan according to claim 12, characterized in that the tab (14) on the casing part (3) is in the form of a ramp (15) rising in the direction of flow on the side wall (16) of the casing part (3).
  14. The radial fan according to claim 12, characterized in that the tab (14) is formed on the side part (2) in the form of a ramp (15) which rises in the direction of flow towards the casing part (3).
  15. The radial fan according to at least one of the preceding claims, characterized in that the fan wheel (5) comprises a hub (17) and at least one cover disc (18).
  16. The radial fan according to claim 15, characterized in that only one cover disc (18) is provided at the fan wheel (5) and that the blades (8) are supported only on the hub (17) and the single cover disc (8).
EP06004223A 2005-03-14 2006-03-02 Centrifugal ventilator Active EP1703139B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE202005004180U DE202005004180U1 (en) 2005-03-14 2005-03-14 centrifugal blower

Publications (2)

Publication Number Publication Date
EP1703139A1 EP1703139A1 (en) 2006-09-20
EP1703139B1 true EP1703139B1 (en) 2011-01-26

Family

ID=36678521

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06004223A Active EP1703139B1 (en) 2005-03-14 2006-03-02 Centrifugal ventilator

Country Status (5)

Country Link
US (1) US8257034B2 (en)
EP (1) EP1703139B1 (en)
AT (1) ATE497109T1 (en)
DE (2) DE202005004180U1 (en)
ES (1) ES2360580T3 (en)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8839815B2 (en) 2011-12-15 2014-09-23 Honeywell International Inc. Gas valve with electronic cycle counter
US8899264B2 (en) 2011-12-15 2014-12-02 Honeywell International Inc. Gas valve with electronic proof of closure system
US8905063B2 (en) 2011-12-15 2014-12-09 Honeywell International Inc. Gas valve with fuel rate monitor
US8947242B2 (en) 2011-12-15 2015-02-03 Honeywell International Inc. Gas valve with valve leakage test
US9074770B2 (en) 2011-12-15 2015-07-07 Honeywell International Inc. Gas valve with electronic valve proving system
US9234661B2 (en) 2012-09-15 2016-01-12 Honeywell International Inc. Burner control system
US9557059B2 (en) 2011-12-15 2017-01-31 Honeywell International Inc Gas valve with communication link
US9995486B2 (en) 2011-12-15 2018-06-12 Honeywell International Inc. Gas valve with high/low gas pressure detection
US10024439B2 (en) 2013-12-16 2018-07-17 Honeywell International Inc. Valve over-travel mechanism
US10203049B2 (en) 2014-09-17 2019-02-12 Honeywell International Inc. Gas valve with electronic health monitoring
US10215291B2 (en) 2013-10-29 2019-02-26 Honeywell International Inc. Regulating device
US10564062B2 (en) 2016-10-19 2020-02-18 Honeywell International Inc. Human-machine interface for gas valve
US10697815B2 (en) 2018-06-09 2020-06-30 Honeywell International Inc. System and methods for mitigating condensation in a sensor module
US10851993B2 (en) 2011-12-15 2020-12-01 Honeywell International Inc. Gas valve with overpressure diagnostics
US11073281B2 (en) 2017-12-29 2021-07-27 Honeywell International Inc. Closed-loop programming and control of a combustion appliance

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5739981B2 (en) 2010-04-06 2015-06-24 スリーエム イノベイティブ プロパティズ カンパニー Radiant blower with shaped scroll profile
US9846440B2 (en) 2011-12-15 2017-12-19 Honeywell International Inc. Valve controller configured to estimate fuel comsumption
US9835265B2 (en) 2011-12-15 2017-12-05 Honeywell International Inc. Valve with actuator diagnostics
US10422531B2 (en) 2012-09-15 2019-09-24 Honeywell International Inc. System and approach for controlling a combustion chamber
US9841122B2 (en) 2014-09-09 2017-12-12 Honeywell International Inc. Gas valve with electronic valve proving system
ES2907289T3 (en) * 2015-09-07 2022-04-22 Emc Fime S R L electric centrifugal blower
US10503181B2 (en) 2016-01-13 2019-12-10 Honeywell International Inc. Pressure regulator

Family Cites Families (45)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3093299A (en) * 1961-05-15 1963-06-11 Trane Co Centrifugal fan
US3824028A (en) * 1968-11-07 1974-07-16 Punker Gmbh Radial blower, especially for oil burners
ES461142A1 (en) * 1976-09-04 1978-06-01 Mtu Friedrichshafen Gmbh Exhaust gas turbocharger
IN152940B (en) * 1978-10-20 1984-05-05 Cummins Engine Co Inc
GB2057567A (en) * 1979-08-24 1981-04-01 Borg Warner Expanding scroll diffuser for radial flow impeller
DE3005094C2 (en) * 1980-02-12 1983-02-24 Klein, Schanzlin & Becker Ag, 6710 Frankenthal Centrifugal pump with double volute casing
DE3001868C2 (en) * 1980-01-19 1984-01-19 Klein, Schanzlin & Becker Ag, 6710 Frankenthal Centrifugal pump with double volute casing
JPS60145497A (en) * 1983-12-29 1985-07-31 Matsushita Electric Ind Co Ltd Centrifugal blower
US4785515A (en) * 1986-07-09 1988-11-22 Willette Russell J Method of making a centrifugal pump
EP0406418B1 (en) * 1988-02-29 1995-02-15 Ebara Corporation Piping connection part of pump
DE4001383A1 (en) * 1989-01-19 1990-07-26 Ebara Corp Method of forming casing of centrifugal pump - is formed in one piece from steel plate by deep drawing, female dies and press forming
WO1990009524A1 (en) * 1989-02-14 1990-08-23 Airflow Research & Manufacturing Corporation Centrifugal fan and diffuser with accumulating volute
CA1331872C (en) * 1989-05-23 1994-09-06 Richard Sixsmith Centrifugal radially aligned outlet type fan with baffle
DE3924281A1 (en) * 1989-07-22 1991-01-31 Standard Elektrik Lorenz Ag DEVICE FOR CONVEYING A GASEOUS MEDIUM
DE4009869A1 (en) * 1990-03-28 1991-10-02 Mulfingen Elektrobau Ebm RADIAL BLOWER WITH INTERNAL SPIRAL
US5156524A (en) * 1990-10-26 1992-10-20 Airflow Research And Manufacturing Corporation Centrifugal fan with accumulating volute
US5281092A (en) * 1991-01-18 1994-01-25 Sullivan John T Volute housing for a centrifugal fan, blower or the like
US5141397A (en) * 1991-01-18 1992-08-25 Sullivan John T Volute housing for a centrifugal fan, blower or the like
AU3965893A (en) * 1992-01-13 1993-08-03 Fasco Industries, Inc. Noise cancellation device for centrifugal blower
US5324167A (en) * 1993-08-20 1994-06-28 Tlt-Babcock, Inc. Centrifugal fan
US5551836A (en) * 1995-01-27 1996-09-03 Revcor, Inc. High pressure combustion blower assembly
JPH09242696A (en) * 1996-03-11 1997-09-16 Denso Corp Centrifugal blower
TW381150B (en) * 1996-03-29 2000-02-01 Sanyo Electric Co Electric fan
CA2229127C (en) * 1997-03-03 2001-06-12 William J. Roy Method of venting a furnace
DE19740590A1 (en) * 1997-09-15 1999-03-18 Klein Schanzlin & Becker Ag Volute casing pump
US6299409B1 (en) * 1998-04-10 2001-10-09 Denso Corporation Centrifugal type blower unit
DE69922083T2 (en) * 1998-05-26 2005-03-31 Carrier Corp. Spiral for blowers
US6146092A (en) * 1998-07-13 2000-11-14 Ford Motor Company Centrifugal blower assembly with a diffuser
US6056506A (en) * 1998-09-23 2000-05-02 Emerson Electric Co. Pump assembly for jetted tub
US6224335B1 (en) * 1999-08-27 2001-05-01 Delphi Technologies, Inc. Automotive air conditioning fan assembly
JP4185654B2 (en) * 2000-08-04 2008-11-26 カルソニックカンセイ株式会社 Centrifugal multi-blade blower
US6314894B1 (en) * 2000-08-30 2001-11-13 Jakel Incorporated Furnace blower housing with integrally formed exhaust transition
US6575696B1 (en) * 2000-09-21 2003-06-10 Fasco Industries, Inc. Method of sound attenuation in centrifugal blowers
DE60134420D1 (en) * 2000-12-04 2008-07-24 Robert Bosch Llc One-piece high-performance centrifugal blower
US6468034B1 (en) * 2000-12-04 2002-10-22 Fasco Industries, Inc. Flush mount round exhaust fabricated inducer housing
US20020119044A1 (en) * 2001-02-26 2002-08-29 O'connor, John F. Centrifugal blower with partitioned scroll diffuser
US20030012649A1 (en) * 2001-07-16 2003-01-16 Masaharu Sakai Centrifugal blower
US6709235B2 (en) * 2001-09-14 2004-03-23 Honeywell International Inc. Turbine housing for high exhaust temperature
US6742989B2 (en) * 2001-10-19 2004-06-01 Mitsubishi Heavy Industries, Ltd. Structures of turbine scroll and blades
JP3721346B2 (en) * 2002-06-26 2005-11-30 株式会社ケーヒン Centrifugal blower
KR100485329B1 (en) * 2002-10-09 2005-04-25 학교법인 선문학원 centrifugal blower with blade preventing eddy
AT413872B (en) * 2002-10-17 2006-06-15 Bitter Engineering & Systemtec WHEEL FOR A PUMP
US6953321B2 (en) * 2002-12-31 2005-10-11 Weir Slurry Group, Inc. Centrifugal pump with configured volute
DE10313054B4 (en) * 2003-03-24 2012-10-04 Motoren Ventilatoren Landshut Gmbh centrifugal blower
US7108482B2 (en) * 2004-01-23 2006-09-19 Robert Bosch Gmbh Centrifugal blower

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10697632B2 (en) 2011-12-15 2020-06-30 Honeywell International Inc. Gas valve with communication link
US9995486B2 (en) 2011-12-15 2018-06-12 Honeywell International Inc. Gas valve with high/low gas pressure detection
US8905063B2 (en) 2011-12-15 2014-12-09 Honeywell International Inc. Gas valve with fuel rate monitor
US8947242B2 (en) 2011-12-15 2015-02-03 Honeywell International Inc. Gas valve with valve leakage test
US10851993B2 (en) 2011-12-15 2020-12-01 Honeywell International Inc. Gas valve with overpressure diagnostics
US8899264B2 (en) 2011-12-15 2014-12-02 Honeywell International Inc. Gas valve with electronic proof of closure system
US9557059B2 (en) 2011-12-15 2017-01-31 Honeywell International Inc Gas valve with communication link
US9074770B2 (en) 2011-12-15 2015-07-07 Honeywell International Inc. Gas valve with electronic valve proving system
US8839815B2 (en) 2011-12-15 2014-09-23 Honeywell International Inc. Gas valve with electronic cycle counter
US9234661B2 (en) 2012-09-15 2016-01-12 Honeywell International Inc. Burner control system
US10215291B2 (en) 2013-10-29 2019-02-26 Honeywell International Inc. Regulating device
US10024439B2 (en) 2013-12-16 2018-07-17 Honeywell International Inc. Valve over-travel mechanism
US10203049B2 (en) 2014-09-17 2019-02-12 Honeywell International Inc. Gas valve with electronic health monitoring
US10564062B2 (en) 2016-10-19 2020-02-18 Honeywell International Inc. Human-machine interface for gas valve
US11073281B2 (en) 2017-12-29 2021-07-27 Honeywell International Inc. Closed-loop programming and control of a combustion appliance
US10697815B2 (en) 2018-06-09 2020-06-30 Honeywell International Inc. System and methods for mitigating condensation in a sensor module

Also Published As

Publication number Publication date
EP1703139A1 (en) 2006-09-20
DE502006008789D1 (en) 2011-03-10
DE202005004180U1 (en) 2006-07-27
US20060204382A1 (en) 2006-09-14
ATE497109T1 (en) 2011-02-15
ES2360580T3 (en) 2011-06-07
US8257034B2 (en) 2012-09-04

Similar Documents

Publication Publication Date Title
EP1703139B1 (en) Centrifugal ventilator
EP1462658B1 (en) Radial fan
DE69925071T2 (en) Centrifugal fan unit for a motor vehicle
DE102010046870B4 (en) Side channel blower, in particular secondary air blower for an internal combustion engine
EP0786597B1 (en) Radial blower
DE1428191A1 (en) Centrifugal blower
EP2886874A1 (en) Radial impeller for a drum type ventilator and fan assembly having such a radial impeller
EP2104787B1 (en) Radial fan and a high-pressure cleaning device having a radial fan
WO2007022648A1 (en) Centrifugal compressor
DE10017808B4 (en) Housing for a blower, especially a radial blower
EP0589300A1 (en) Radial blower
EP1165965B1 (en) Side channel compressor
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
DE3842697A1 (en) HIGH PRESSURE BLOWER
EP1998052A2 (en) Axial ventilator with subsequent guide vane apparatus
EP1022469B1 (en) Radial fan
EP1538340A2 (en) Compact diagonal fan
EP1022470B1 (en) Radial fan
EP0389565B1 (en) Radial fan
EP0450272B1 (en) Radial fan with an internal spiral
DE3029507A1 (en) Spiral flow type fan - has forward curved blades and stator passages profiled for quiet running and high pressure
DE4242474A1 (en) Device for conveying a gaseous medium
DE10249244B4 (en) Impeller for a side channel machine
DE2705260A1 (en) Radial blade high pressure blower - has inlet cone extending inside impeller to stabilise performance at low volumes
EP4180726A1 (en) Extractor hood

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): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

17P Request for examination filed

Effective date: 20070316

17Q First examination report despatched

Effective date: 20070418

AKX Designation fees paid

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REF Corresponds to:

Ref document number: 502006008789

Country of ref document: DE

Date of ref document: 20110310

Kind code of ref document: P

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502006008789

Country of ref document: DE

Effective date: 20110310

REG Reference to a national code

Ref country code: NL

Ref legal event code: T3

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2360580

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20110607

LTIE Lt: invalidation of european patent or patent extension

Effective date: 20110126

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

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20110126

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20110126

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20110526

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20110427

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20110126

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20110526

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

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

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20110126

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20110426

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20110126

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20110126

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20110126

BERE Be: lapsed

Owner name: EBM-PAPST LANDSHUT G.M.B.H.

Effective date: 20110331

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

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20110126

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20110126

Ref country code: MC

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

Effective date: 20110331

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20110126

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20110126

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20110126

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20110126

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

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

Ref country code: BE

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

Effective date: 20110331

26N No opposition filed

Effective date: 20111027

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

Ref country code: CH

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

Effective date: 20110331

Ref country code: LI

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

Effective date: 20110331

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502006008789

Country of ref document: DE

Effective date: 20111027

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 497109

Country of ref document: AT

Kind code of ref document: T

Effective date: 20110302

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

Ref country code: AT

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

Effective date: 20110302

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

Ref country code: LU

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

Effective date: 20110302

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

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20110126

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 11

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 12

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 13

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

Ref country code: FR

Payment date: 20230320

Year of fee payment: 18

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

Ref country code: TR

Payment date: 20230228

Year of fee payment: 18

Ref country code: GB

Payment date: 20230323

Year of fee payment: 18

Ref country code: DE

Payment date: 20230320

Year of fee payment: 18

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230521

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

Ref country code: NL

Payment date: 20230322

Year of fee payment: 18

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

Ref country code: IT

Payment date: 20230331

Year of fee payment: 18

Ref country code: ES

Payment date: 20230414

Year of fee payment: 18

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

Ref country code: NL

Payment date: 20240320

Year of fee payment: 19