EP2035712A1 - Roue centrifuge - Google Patents

Roue centrifuge

Info

Publication number
EP2035712A1
EP2035712A1 EP07732575A EP07732575A EP2035712A1 EP 2035712 A1 EP2035712 A1 EP 2035712A1 EP 07732575 A EP07732575 A EP 07732575A EP 07732575 A EP07732575 A EP 07732575A EP 2035712 A1 EP2035712 A1 EP 2035712A1
Authority
EP
European Patent Office
Prior art keywords
impeller
channels
inlet
channel
noise
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Withdrawn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
EP07732575A
Other languages
German (de)
English (en)
Inventor
James Watt Taylor
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.)
Qinetiq Ltd
Original Assignee
Qinetiq Ltd
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 Qinetiq Ltd filed Critical Qinetiq Ltd
Publication of EP2035712A1 publication Critical patent/EP2035712A1/fr
Withdrawn legal-status Critical Current

Links

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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing 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
    • 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
    • F04D17/167—Operating by means of fibrous or porous elements, e.g. with sponge rotors
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/70—Shape

Definitions

  • the present invention relates to rotary impellers used in fluid-dynamic machines for moving and/or compressing gases or liquids or other fluent materials, such as fans, blowers, propellers, pumps and compressors, and more particularly is concerned with the production of low noise levels by such devices.
  • Most machines of this kind fall within one of two main classes, namely axial flow machines where the overall direction of flow of fluid through the impeller is generally parallel to its axis of rotation, and centrifugal machines where the overall direction of flow of fluid through the impeller is generally radial to its axis of rotation. It is to the latter class that the present invention is directed.
  • the impeller is a significant source of noise in such machines, the noise from the impeller being caused by the repeated exit of fluid from the individual blades (tonal noise) and the turbulent passage of the fluid over the blades (broadband noise).
  • Impellers according to the invention may find application in all of these markets, or more generally in centrifugal machines where there is a desire for lower noise operation.
  • each individual blade compresses a volume of fluid which contributes to the total flow through the machine.
  • the frequency of noise created in this way is known as the blade passing frequency and is dependent on the number of blades in the impeller and the number of significant static features at the exit from the impeller.
  • the present invention is predicated upon replacing the traditional bladed impeller with a multi-cellular form of construction with the impeller comprising a multiplicity of individual radial flow channels disposed in a circumferential and longitudinal array with respect to the axis of rotation of the impeller. This dramatically increases the equivalent number of "blades” passing the static features and correspondingly raises the frequency of the tonal noise generated. For a given flow output, higher frequencies have lower energy and hence the total amplitude of the noise generated should be reduced.
  • a centrifugal impeller having a construction as described above (hereinafter referred to as "an impeller of the kind stated") is disclosed and illustrated in a schematic manner in US2004/0184914.
  • the present invention seeks, however, to provide an impeller of the kind stated with an enhanced fluid dynamic performance.
  • the efficient transfer of momentum to the fluid in the rotating impeller requires an increase in the available flow area along the length of the flow channels.
  • some increase in the available flow area of each channel will inherently be achieved by virtue of the circumferential widths of the channels increasing with increasing radial distance from the axis of rotation.
  • a further increase in the available flow area can be achieved by configuring flow channels so as to provide an increase in a dimension orthogonal to the circumferential direction.
  • the invention accordingly resides in an impeller of the kind stated wherein at least a plurality of said channels are configured to extend from a respective channel inlet to a respective channel outlet which is offset from the respective inlet in the longitudinal direction of the impeller, and involve an increase in the internal dimension of the respective channel in the direction parallel to the axis of rotation of the impeller.
  • the flow channels may also be so configured that their inlets collectively define an inlet array of dished form surrounding the axis of rotation, the radius of which array decreases with increasing distance in the longitudinal direction of the impeller from a main inlet to the impeller at one end thereof.
  • the array of flow channels in an impeller according to the invention is preferably in the form of a succession of circumferential rows of such channels arranged along the impeller, with the channels in each such row being offset in the circumferential direction from the channels in the adjoining such row(s).
  • This circumferential offset reduces the number of channels passing the same static feature at any instant and further breaks up the fluid flow which reduces the generation of discrete tones and distributes the noise over a wider range of frequencies.
  • the flow channels are tessellated together with cross-sectional shapes based on hexagons (or truncated hexagons in the case of the rows of channels at each end of the impeller).
  • This provides an inherently strong structural form with a high area efficiency for fluid flow, allows a natural offset for the channels in adjoining rows, provides "flat" radial faces for working the fluid, and is more efficient than, say, circular or elliptical channels in terms of structural weight and flow area.
  • This is not an essential feature of the invention, however, and other cross-sectional forms may be adopted if desired. For example a channel form based on quadrilaterals would provide a slightly higher area efficiency at the expense of some structural strength for a given wall thickness, and could therefore be more suited to lower load applications.
  • the number of flow channels in each circumferential row is preferably the same, and is preferably a prime number to reduce the formation of harmonics of the blade passing frequency in the noise spectrum.
  • Figure 1 is a pictorial view of a preferred embodiment of a centrifugal fan impeller according to the invention
  • Figure 2 is an axial section through the impeller of Figure 1 ;
  • Figure 3 is a simplified schematic diagram illustrating the increase in "axial thickness" of flow channels in the impeller of Figures 1 and 2;
  • Figure 4 illustrates comparative noise spectra measured for a conventional vacuum cleaner when equipped with its original impeller and with an impeller according to the invention.
  • the impeller there illustrated is for a centrifugal air fan or blower such as may be incorporated in a vacuum cleaner, hairdryer or the like appliance. It comprises a generally annular structure bounded at one longitudinal end by a disc 1 with a central aperture 2 constituting the main air inlet to the device, and closed at the other end by a disc 3 which extends inwardly in the form of a streamlined body 4 adapted to be fitted onto the spindle of an associated motor (not shown) for rotating the impeller in use.
  • a multiplicity of radial air flow channels 5 extend through the impeller and when it is rotated induce a flow of air to pass in through the aperture 2 and along the channels 5 into an associated conventional volute casing (not shown) whence it is directed as required.
  • each channel 5 there are a total of 44 channels 5 disposed in an array of four circumferential rows, each comprising 11 channels, arranged along the impeller.
  • the individual channels are of generally hexagonal cross-section, truncated to five sides for the end rows bounded by the discs 2 and 3, and tessellated as shown so that the centres of the channels in each row are offset in the circumferential direction from those in the adjoining row or rows by a half channel width.
  • centrelines of the channels 5 do not each lie in a single radial plane but as shown particularly in Figure 2 the channels are swept in the longitudinal direction of the impeller away from the inlet end so that the centres of their individual outlets are offset in that direction from the centres of their respective inlets.
  • the inlet ends of the channels 5 are swept towards the main inlet 2, with the radius of the ring of channel inlets in each circumferential row decreasing for successive rows away from the main inlet 2, so that the channel inlets collectively define an array of dished form surrounding the body 4.
  • this geometry assists in smoothing the transition of the airflow from the axial direction as it enters the inlet 2 to the radial direction as it passes through the channels 5, while maintaining the desired flow area ratios.
  • each channel could be swept so far that their individual inlets lie in the plane of the aperture 2, resulting in a hybrid form of device which acts as an axial flow impeller at the inlet ends of the channels and transitions to a centrifugal impeller further along the channels.
  • the channels 5 also have a component of curvature in the circumferential direction to improve compression of the air.
  • Figure 4 is a graph which illustrates by the solid line the noise spectrum obtained from a conventional vacuum cleaner when fitted with its original centrifugal impeller (being of conventional design with seven blades and 90mm in diameter), and by the broken line the noise spectrum obtained from the same appliance when the impeller was replaced with one of the same diameter substantially in accordance with the design shown in Figures 1 and 2.
  • measurements were taken with the vacuum cleaner running and placed on the floor, by a sound level meter located 1m above and 1m in front of the appliance.
  • a centrifugal impeller comprising a multiplicity of individual radial flow channels disposed in a circumferential and longitudinal array with respect to the axis of rotation of the impeller, wherein at least a plurality of said channels are configured to extend from a respective channel inlet to a respective channel outlet which is offset from the respective inlet in the longitudinal direction of the impeller, and involve an increase in the internal dimension of the respective channel in the direction parallel to the axis of rotation of the impeller.
  • An impeller according to claim 2 further comprising a profiled body located around the axis of rotation within said dished inlet array, the radius of which body increases with increasing distance in the longitudinal direction of the impeller from said main inlet.

Landscapes

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

Abstract

Une roue de ventilateur centrifuge silencieuse présente une forme de construction multicellulaire comprenant de multiples canaux de flux radial (5) individuels placés dans un réseau périphérique et radial par rapport à l'axe de rotation. Ceci augmente la ' fréquence de passage de pale' si on compare cette roue à une hélice classique et comme les fréquences plus élevées possèdent une énergie moindre pour une sortie de flux donné, l'amplitude totale du bruit généré peut être réduite. Chaque canal (5) s'étend d'une entrée de canal respective à une sortie de canal respective qui est décalée de l'entrée respective dans le sens longitudinal de la roue, et ceci implique un accroissement de la dimension interne du canal respectif dans le sens parallèle à l'axe de rotation, favorisant ainsi la décélération et la compression de l'air ou d'un autre milieu transporté lorsque celui-ci s'écoule à travers ces canaux.
EP07732575A 2006-06-30 2007-04-26 Roue centrifuge Withdrawn EP2035712A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GBGB0612993.6A GB0612993D0 (en) 2006-06-30 2006-06-30 Centrifugal impeller
PCT/GB2007/001538 WO2008001033A1 (fr) 2006-06-30 2007-04-26 Roue centrifuge

Publications (1)

Publication Number Publication Date
EP2035712A1 true EP2035712A1 (fr) 2009-03-18

Family

ID=36888371

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07732575A Withdrawn EP2035712A1 (fr) 2006-06-30 2007-04-26 Roue centrifuge

Country Status (6)

Country Link
US (1) US20090185906A1 (fr)
EP (1) EP2035712A1 (fr)
JP (1) JP2009541661A (fr)
CN (1) CN101484707A (fr)
GB (1) GB0612993D0 (fr)
WO (1) WO2008001033A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114483604A (zh) * 2021-12-06 2022-05-13 鑫磊压缩机股份有限公司 一种能轴向和径向均导流的双向分流叶轮

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010028763B4 (de) * 2010-05-07 2015-04-02 Man Diesel & Turbo Se Schalldämpfer für einen Turboverdichter und Verfahren zum Auslegen eines Schalldämpfers
CN103867486B (zh) * 2014-04-03 2016-08-17 干平 叶轮
EP3901469A1 (fr) * 2020-04-20 2021-10-27 Hamilton Sundstrand Corporation Hélice
FR3111676B1 (fr) * 2020-06-19 2022-12-16 Seb Sa Hélice pour appareil soufflant comprenant des canaux radiaux de passage d’air
US11441572B2 (en) * 2020-08-24 2022-09-13 Hamilton Sundstrand Corporation Impeller design and manufacturing method with pentagonal channel geometry
CN114857053B (zh) * 2022-05-30 2024-02-27 杭州老板电器股份有限公司 一种蜗壳、多翼离心风机以及油烟机

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE414359A (fr) *
GB191012768A (en) * 1909-04-07 1911-05-25 Bernhard Bomborn Improvements in Centrifugal Blowers or Pumps.
GB305800A (en) * 1928-01-25 1929-02-14 Horace Stanley Pochin Improvements in or relating to centrifugal fans
DE548474C (de) * 1930-08-30 1932-04-13 Siemens Schuckertwerke Akt Ges Geblaeserad
GB655830A (en) * 1947-12-13 1951-08-01 Packard Motor Car Co Centrifugal impeller structure
GB1046272A (en) * 1962-04-27 1966-10-19 Zenkner Kurt Radial flow blower
FR2647511B1 (fr) * 1989-05-25 1993-11-26 Velecta Ventilation Elect Appliq Ventilateur centrifuge ayant un niveau de bruit reduit
DE10302773B3 (de) * 2003-01-17 2004-03-11 Institut für Luft- und Kältetechnik gemeinnützige Gesellschaft mbH Lauf- und Leiträder für Strömungsmaschinen, insbesondere für Verdichter und Ventilatoren
US20070177349A1 (en) * 2005-11-23 2007-08-02 Himanshu Pokharna High efficiency fluid mover

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2008001033A1 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114483604A (zh) * 2021-12-06 2022-05-13 鑫磊压缩机股份有限公司 一种能轴向和径向均导流的双向分流叶轮
CN114483604B (zh) * 2021-12-06 2023-10-27 鑫磊压缩机股份有限公司 一种能轴向和径向均导流的双向分流叶轮

Also Published As

Publication number Publication date
US20090185906A1 (en) 2009-07-23
JP2009541661A (ja) 2009-11-26
WO2008001033A1 (fr) 2008-01-03
GB0612993D0 (en) 2006-08-09
CN101484707A (zh) 2009-07-15

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