EP1857683A2 - Radialgebläse, insbesondere für Abzugshauben und Dunstabsauger - Google Patents

Radialgebläse, insbesondere für Abzugshauben und Dunstabsauger Download PDF

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Publication number
EP1857683A2
EP1857683A2 EP07107751A EP07107751A EP1857683A2 EP 1857683 A2 EP1857683 A2 EP 1857683A2 EP 07107751 A EP07107751 A EP 07107751A EP 07107751 A EP07107751 A EP 07107751A EP 1857683 A2 EP1857683 A2 EP 1857683A2
Authority
EP
European Patent Office
Prior art keywords
curvature
casing
axis
plane
fan
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.)
Withdrawn
Application number
EP07107751A
Other languages
English (en)
French (fr)
Other versions
EP1857683A3 (de
Inventor
Antonio Ranalli
Francesco Tanoni
Gabriele Teobaldelli
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.)
LN 2 - Srl
Original Assignee
LN 2 - Srl
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 LN 2 - Srl filed Critical LN 2 - Srl
Publication of EP1857683A2 publication Critical patent/EP1857683A2/de
Publication of EP1857683A3 publication Critical patent/EP1857683A3/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—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
    • F04D29/4226—Fan casings
    • 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 present invention relates to a centrifugal fan having the characteristics mentioned in the preamble of main claim 1.
  • the invention is placed particularly, but not exclusively, in the technical field of centrifugal fans designed for applications in extractor hoods or fume extraction devices.
  • fans of the aforesaid type are used as suction devices for vapours, combustion fumes, exhaust gases, or in all those applications in which provision is made for the extraction and conveying, in general, of gaseous mixtures.
  • Typical embodiments provide for the use of centrifugal fans with helical casing having a cylindrical drum type fan wheel and axially extending blades.
  • the casings of these fans are further provided with a lateral suction aperture and a tangential delivery aperture, between which extends a pressure chamber following a helical course and the volume of which is defined between the casing and the fan wheel.
  • a flow separator typically comprising an appendage standing up in the casing at the zone having a lesser radial distance between the fan wheel and the helical profile of the casing, in which zone the emerging delivery flow (directed tangentially) runs close to the flow introduced by suction in the fan wheel (at the smaller cross-section of the helical chamber of the fan).
  • An example of a fan comprising a similar flow separator device is known from European Patent Application No. 1462658 .
  • separators although on the one hand they make it possible to improve the characteristics of separation and exchange of the gaseous fluids treated by the fan, on the other hand they give rise to noisy operation, in particular generated by the passage of the blades in the region of the separator.
  • the principal aim of the invention is that of providing a centrifugal fan equipped with a flow separator of the aforesaid type, which makes it possible to improve, with respect to known solutions, the overall output, guaranteeing an adequate capacity of separation of the fluids, and at the same time minimising the noise produced by the separator, for the purpose of improved overall efficiency.
  • the reference 1 designates a centrifugal fan, particularly designed for use in extractor hoods or fume extraction devices, and produced according to the present invention.
  • the fan 1 comprises a casing 2 with helical external profile, and which is defined by two casing half-shells 2a, 2b capable of being removably coupled to each other, at a plane of junction, indicated diagrammatically by P in the drawings.
  • the two casing half-shells are configured with substantial mirror-image symmetry with respect to the junction plane P, as shown in the assembled state in Figure 3, except for the lateral suction aperture provided on only one of the two casing half-shells.
  • a cylindrical drum type fan wheel 3 provided with axially extending blades 4, the fan wheel being capable of being driven in rotation about an axis X.
  • the reference 7 indicates a pressure chamber defined within the casing, along the helical course of same, and the volume of which is formed between the drum of the fan wheel 3 and the inner surface profile 3b of the casing itself.
  • the fan also comprises a flow separator device, indicated as a whole by 8, which is arranged at the zone having the smallest radial distance between the fan wheel 3 and the inner surface profile 3b of the casing. This zone is indicated by M in the drawings.
  • the flow separator 8 is defined conjointly by a pair of appendages 9, each formed in the respective casing half-shell 2a, 2b, and being also preferably produced with mirror-image symmetry with respect to the median plane P of junction of the half-shells, as shown in Figure 3.
  • the appendages 9 defining the flow separator that relating to the casing half-shell 2a, will be described in detail hereinafter, it being understood that the other appendage, where not otherwise specified, is structurally identical and also symmetrical in mirror image to the plane P.
  • the projection of the appendage 9 in the plane Q of Figure 4 extends substantially along an arc B of circumference, extending in prolongation of the inner helical profile 3b of the casing and also protruding into the pressure chamber behind the delivery aperture 5.
  • the appendage is preferably produced integrally with the corresponding casing half-shell and has a free edge 10, at its free end opposed to the casing wall, the profile of which is also clearly illustrated in the lateral projection of the plane W of Figure 5.
  • the profile of the free edge 10 of the appendage 9 comprises at least a first and a second curved section 10a, 10b, in prolongation of each other, having respective radii of curvature R1, R2 of opposite sign and also defining a point of flexion F in the connection zone.
  • the section 10a that closest to the median plane P of coupling of the casing half-shells, has a convex curvature, the radius of curvature R1 of which is centred in the part of the plane of projection W of Figure 5 containing the axis Y.
  • the point of flexion has coordinates (x, y) such that the ratio (x/D) between the abscissa and the outside diameter of the fan wheel, this diameter being indicated by D, is selected to have a value ranging between 0.04 and 0.185, and the ratio (y/D) between the ordinate and the fan wheel outside diameter D is between 0.04 and 1.11.
  • the radius of curvature R1 of the first section 10a is selected to have a value such that the ratio between the radius R1 and the fan wheel outside diameter D is between 1.11 and 0.04, and also preferably equal to around 0.085.
  • the radius of curvature R2 of the second section 10b is selected to have a value such that the ratio between the radius R2 and the fan wheel outside diameter D is between 0.04 and 1.11, and also preferably equal to around 0.16.
  • the sections 10a, 10b may conveniently be extended, in the plane of projection W, so as to terminate respectively on the median plane P and on the semicircular bottom of the delivery aperture.
  • those sections may be in turn connected, on the opposite side from the flexion zone, with further sections of the free edge 10, as illustrated in Figure 5.
  • the curved section 10a prefferably be extended, on the opposite side from the flexion F, in a third section 10c, substantially rectilinear and also extending as far as the median plane P, and for the curved section 10b to be extended in a corresponding manner in a fourth, curved section 10d.
  • the rectilinear section 10c is moreover inclined, in the plane of projection W, with respect to the perpendicular to the median plane P, with definition of an angle of inclination A having a value conveniently between 0° and 45°.
  • the fourth section 10d has a radius of curvature, indicated by R4, of the same direction as the radius of curvature R2 of the section 10b.
  • the radius of curvature R4 is moreover conveniently selected to have a value such that the ratio (R4/D) between the radius of curvature itself and the outside diameter of the fan wheel is between 0.04 and 1.11.
  • the point S in which is centred the radius of curvature R' of the arc of circumference which identifies the curved course of the appendage 9 in the plane of projection Q has coordinates ( x',y' ) such that the ratio (x'/D) between its abscissa and the outside diameter D of the fan wheel is selected to have a value of between 0 and 0.5., and the ratio (y'/D) between the ordinate and the outside diameter D of the fan wheel has a value of between 0 and 0.5.
  • the radius of curvature R' of the arc B is moreover conveniently selected to have a value such that the ratio (R'/D) between same and the diameter D of the fan wheel is between 0.15 and 0.6, and also preferably equal to around 0.3.
  • the angle E subtended by that arc is selected to have a value of between 15° and 90°, preferably equal to 35°.
  • the point of flexion F' is further located, with respect to the system of coordinates x',y' , defined above, with respective coordinates such that the ratio ( x" /D) between its abscissa and the diameter D of the fan wheel is between 0 and 0.95, and the ratio ( y" /D) between its ordinate and the diameter D is between 0.4 and 1.4.
  • the radius of curvature R5 of the fifth section 12a is conveniently selected moreover to have a value such that the ratio R5/D between said radius and the diameter of the fan wheel is between 0 and 9.5.
  • the radius of curvature R6 of the sixth section 12b is conveniently selected moreover to have a value such that the ratio R6/D between said radius and the diameter of the fan wheel is between 0 and 5.
  • the reference 15 indicates diagrammatically a pressure intake, for example produced in the form of an aperture or through-hole provided in the body of one of the appendages 9 defining the flow separator 8.
  • the aperture 15, advantageously provided integrally with the separator 8, is provided behind the delivery aperture 5 of the fan and may conveniently be used for housing a pressure sensor, for example intended for determining the rate of flow delivered by the fan or to give the signal to a pressure switch, without interfering noticeably with the flow and therefore without altering the performance of the appliance.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Separating Particles In Gases By Inertia (AREA)
EP07107751A 2006-05-16 2007-05-08 Radialgebläse, insbesondere für Abzugshauben und Dunstabsauger Withdrawn EP1857683A3 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ITPD20060193 ITPD20060193A1 (it) 2006-05-16 2006-05-16 Ventilatore centrifugo, particolarmente per cappe aspiranti ed estrattori di fumi

Publications (2)

Publication Number Publication Date
EP1857683A2 true EP1857683A2 (de) 2007-11-21
EP1857683A3 EP1857683A3 (de) 2010-02-24

Family

ID=38269004

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07107751A Withdrawn EP1857683A3 (de) 2006-05-16 2007-05-08 Radialgebläse, insbesondere für Abzugshauben und Dunstabsauger

Country Status (3)

Country Link
EP (1) EP1857683A3 (de)
IT (1) ITPD20060193A1 (de)
RU (1) RU2426013C2 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101457946B (zh) * 2007-12-11 2010-11-24 宁波方太厨具有限公司 用于抽油烟系统的仿生微孔降噪结构
EP2177769A3 (de) * 2008-10-15 2015-05-27 MAHLE Behr GmbH & Co. KG Radialgebläsegehäuse
CN106855062A (zh) * 2016-12-15 2017-06-16 东华大学 一种变深度降噪蜗舌及多翼离心风机

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012218286A1 (de) * 2012-10-08 2014-04-10 GEA Küba GmbH Ventilatorvorrichtung

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29920373U1 (de) 1999-11-19 2000-01-13 Motoren Ventilatoren Gmbh Gehäuse für einen Lüfter, insbesondere einen Radiallüfter
US20060051204A1 (en) 2004-09-03 2006-03-09 Lyons Leslie A Lobed joint draft inducer blower

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19950245C1 (de) * 1999-10-19 2001-05-10 Ebm Werke Gmbh & Co Kg Radialgebläse
JP4026366B2 (ja) * 2001-03-16 2007-12-26 株式会社デンソー 遠心式送風機
KR100420518B1 (ko) * 2001-08-28 2004-03-02 엘지전자 주식회사 팬하우징
TWI228216B (en) * 2004-03-25 2005-02-21 Quanta Comp Inc Centrifugal fan
FR2875560B1 (fr) * 2004-09-23 2006-12-01 Renault Sas Ventilateur centrifuge a bruit reduit pour systeme de ventilation d'un vehicule automobile

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29920373U1 (de) 1999-11-19 2000-01-13 Motoren Ventilatoren Gmbh Gehäuse für einen Lüfter, insbesondere einen Radiallüfter
US20060051204A1 (en) 2004-09-03 2006-03-09 Lyons Leslie A Lobed joint draft inducer blower

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101457946B (zh) * 2007-12-11 2010-11-24 宁波方太厨具有限公司 用于抽油烟系统的仿生微孔降噪结构
EP2177769A3 (de) * 2008-10-15 2015-05-27 MAHLE Behr GmbH & Co. KG Radialgebläsegehäuse
CN106855062A (zh) * 2016-12-15 2017-06-16 东华大学 一种变深度降噪蜗舌及多翼离心风机

Also Published As

Publication number Publication date
RU2007118153A (ru) 2008-11-20
EP1857683A3 (de) 2010-02-24
RU2426013C2 (ru) 2011-08-10
ITPD20060193A1 (it) 2007-11-17

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