WO2010018607A1 - Ventilateur centrifuge - Google Patents

Ventilateur centrifuge Download PDF

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Publication number
WO2010018607A1
WO2010018607A1 PCT/IT2009/000367 IT2009000367W WO2010018607A1 WO 2010018607 A1 WO2010018607 A1 WO 2010018607A1 IT 2009000367 W IT2009000367 W IT 2009000367W WO 2010018607 A1 WO2010018607 A1 WO 2010018607A1
Authority
WO
WIPO (PCT)
Prior art keywords
disc
counter
impeller
hole
axis
Prior art date
Application number
PCT/IT2009/000367
Other languages
English (en)
Inventor
Antonio Ranalli
Francesco Tanoni
Original Assignee
Ln 2 S.R.L. A Socio Unico
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 S.R.L. A Socio Unico filed Critical Ln 2 S.R.L. A Socio Unico
Priority to EP09787832.6A priority Critical patent/EP2324249B1/fr
Publication of WO2010018607A1 publication Critical patent/WO2010018607A1/fr

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
    • F04D29/26—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
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/009—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids by bleeding, by passing or recycling fluid
    • 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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel

Definitions

  • the present invention relates to a centrifugal fan having the features set out in the preamble of main claim 1. Technological Background
  • Centrifugal fans of the above-mentioned type are well known for being used in pre-mixing air/gas mixtures for burners of heating devices. They are typically provided with a bladed impeller which is housed in a manifold which is, for example, helical, and inside which the impeller is rotatably supported so as to be driven about an axis of rotation.
  • the intake cross-section is formed laterally in the manifold , and is constructed in the form of an opening which is coaxial with the axis of the impeller.
  • the outlet cross-section of the impeller is connected to the helical volute of the manifold so as to impart to the radial flow which is generated by the impeller a main tangential component as far as the outlet cross- section of the manifold.
  • a typical structural form of a centrifugal fan makes provision for the set of blades to extend, in the axial direction, between a base disc, which carries a hub for connection to the shaft of the impeller, and a counter-disc which extends between the intake cross-section and outlet cross-section of the impeller.
  • Those discs define, together with the blades of the impeller, bladed conduits with cross-sections of the conduits having profiles of closed contour, those conduits extending between the axially opposing walls of the manifold for receiving the impeller.
  • the region between the counter-disc and the wall of the manifold facing it is normally the location for recirculation of fluid which flows from the outlet cross-section into the intake region, with consequent reductions in terms of performance and effectiveness of the fan.
  • the above-mentioned region is provided so as to bring about, aibeit minimai, spacing between the fan and the manifold, which are in relative movement during the operation of the fan. Any interposition of sliding type sealing means between the impeller and the counter-disc would not be an acceptable solution because of the reduction in effectiveness which it would involve owing to the occurrences of friction in addition to the wear which would occur between the parts in contact.
  • a main object of the invention is to provide a fan which is structurally and operationally configured to overcome the limits set out with reference to the prior art mentioned.
  • Figure 1 is a perspective view of a fan constructed in accordance with the invention
  • Figure 2 is an axially sectioned view of part of the fan of Figure 1
  • Figure 3 is a view corresponding to that of Figure 2 of a fan constructed in accordance with the prior art
  • Figure 4 is an axially sectioned view of a detail of part of the fan of the preceding Figures
  • - - Figure 5 is a view corresponding to that of Figure 4, in a construction variant of the invention.
  • a centrifugal fan is generally designated 1 and comprises an impeller 2 which has a set of blades having a plurality of blades 3 which extend substantially radially and a manifold 4 for receiving the impeller.
  • the impeller 2 can be rotated about an axis of rotation X, for example, by means of a motor which is not illustrated, to the driving shaft of which (also not illustrated) there is provision for the impeller 2 to be securely attached.
  • the intake cross-section 5 is advantageously constructed in the form of a circular opening 5a of the manifold, which is coaxial with the axis X, as illustrated in Figure 1, and the outlet cross-section 6 is constructed as an opening 6a which extends circumferentially at the outer diameter of the impeller 2.
  • the measurement of the outer radius of the impeller is designated R 9 ( Figure 4).
  • the set of blades formed by the blades 3 extends parallel with the axial direction from a first disc 7 until it terminates at a second opposing counter-disc 8.
  • Each pair of adjacent blades 3 defines, together with the disc 7 and the counter-disc 8, a bladed conduit 9 which extends between the intake cross-section 5 and outlet cross-section 6 and in which the fluid processed by the fan is conveyed in the direction of the outlet cross- section.
  • the disc 7 radially extends, with respect to the axis X, with spacing from a first wall 10 of the manifold 4.
  • the counter-disc 8 also extends substantially parallel with and spaced-apart from a second wall 11 of the manifold, as clearly shown in Figure 2.
  • the counter-disc 8 and the wall 11 facing it have a surface profile of conical extent having a main axis X, as illustrated in the axial section of Figure 2.
  • the counter-disc 8 is provided with a slot-like hole which has a circumferential profile concentric with the axis X and which is designated 15.
  • the hole 15 extends through the thickness of the counter-disc 8 so as to define a passage for fluid communication between each bladed conduit 9 and the spatial region 13 which is external with respect to the conduit and which is delimited by the wall 11.
  • the counter-disc 8 is divided by the hole 15, which extends without any gap, into two separate portions designated 8a, 8b.
  • the slot-like hole 15 is of annular construction and is delimited by a pair of concentric annular edges 16a, 16b which belong to the first and the second portion 8a, 8b of the counter-disc, respectively, in a mutual spaced-apart relationship.
  • the recirculation of fluid which is brought about owing to the provision of the slot-like hole 15 is indicated with the arrows A, which recirculation limits the "by-pass" which is normally found in impellers having a closed counter-disc (which is continuous), an example of which is shown in Figure 3, in which the flow is indicated with the arrows B..
  • the arrows B' indicate a residual by-pass flow which occurs in the impellers according to the invention, wherein there is produced, owing to the slot-like hole 15, a type of aerodynamic sealing which is produced in the alternative to contact type sealing.
  • t the distance measured in an axial direction between the edges of the profiles of the portions 8a, 8b of the counter-disc 8 defining the hole 15
  • R t the radial distance of the edge 16b which defines the radial positioning of the hole 15 with respect to the counter-disc 8
  • the dimensional relationships t/R g and Rt/Rg are selected in the following preferred value intervals:
  • FIG. 5 illustrates a construction variant of the invention, in which details similar to those of the preceding example are referred to with the same reference numerals.
  • That variant differs principally in that there is provision, in the spatial region 13, in a position facing the hole 15, for a body having an annular profile which is designated 20 and which is fixedly joined to the stationary wall 11 of the manifold 4. That profile is formed so as to have a quadrilateral cross-section and is positioned with predetermined spacing from the passage which is defined by the slot-like hole 15 in the counter- disc 8, as clearly shown in the corresponding Figure.
  • the symbol s designates the distance, measured perpendicularly relative to the generating line of the conical profile of the counter-disc 8, between the counter-disc itself and the profile 20.
  • the dimension of the cross-section of the profile 20 measured radially with respect to the axis X is designated t 2 .
  • the measurement of the radial dimension of the opening 20a formed between the edge 16b and the facing edge of the profile 20 is designated ti.
  • the measurement of the radial dimension of the opening 20b which is formed between the edge 16a and the corresponding facing edge of the profile 20 is designated t 3 .
  • the radial distance from the axis X of the edge 16b of the hole 15 is designated R tl , which distance identifies the radial positioning of the slot-like hole in the counter-disc 8.
  • the invention thereby achieves the object set out and provides a number of advantages over known solutions.
  • slot-like hole provided in the cqunter-disc is also advantageous during balancing because it acts as a means for engaging any balancing masses which may have to be positioned on the impeller during such a step.
  • a main advantage consists in that, with the fan according to the invention, it is possible to obtain aerodynamic type sealing in contrast to the recirculation of fluids which occurs between the intake cross-section and outlet cross-section in fans of conventional type.
  • Such sealing advantageously limits the by-pass effect which is typically found in impeller structures with manifolds having counter-discs of a closed type in the radial direction, that is to say, which extend continuously between the intake cross-section and outlet cross-section of the fan.
  • the invention achieves an overall increase in the performance and effectiveness with respect to solutions of the conventional type.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Centrifugal Separators (AREA)

Abstract

La présente invention concerne un ventilateur centrifuge comprenant un impulseur radial (2) et un collecteur (4) destiné à recevoir l'impulseur, doté d'au moins une section transversale d'admission (5) et d'au moins une section transversale de refoulement (6) pour le flux qui est produit par l'impulseur, l'impulseur (2) étant prévu de façon à être mis en rotation autour d'un axe de rotation (X), la section transversale d'admission (5) et la section transversale de refoulement (6) étant prévues respectivement à proximité de l'axe de rotation et dans une position éloignée de cet axe. L'impulseur (2) comprend une pluralité de lames sensiblement radiales (3) qui s'étendent dans une direction axiale entre un disque (7) et un contre-disque (8) qui sont solidement fixés aux lames et qui définissent, avec les lames, des conduits correspondants (9) qui s'étendent entre les sections transversales d'admission et de refoulement, le contre-disque (8) s'étendant entre ces sections transversales (5, 6) avec un espacement à partir d'une paroi (11) du collecteur (4) en face de celui-ci. Le contre-disque (8) est pourvu d'au moins un trou débouchant (15) à travers le contre-disque de façon à placer chaque conduit (9) de l'impulseur (2) en communication fluidique avec la région d'espacement (13) définie entre le contre-disque (8) et la paroi (11) du collecteur en face de celui-ci.
PCT/IT2009/000367 2008-08-12 2009-08-05 Ventilateur centrifuge WO2010018607A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP09787832.6A EP2324249B1 (fr) 2008-08-12 2009-08-05 Ventilateur centrifuge

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITPD2008A000250A IT1391671B1 (it) 2008-08-12 2008-08-12 Ventilatore centrifugo
ITPD2008A000250 2008-08-12

Publications (1)

Publication Number Publication Date
WO2010018607A1 true WO2010018607A1 (fr) 2010-02-18

Family

ID=40793200

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IT2009/000367 WO2010018607A1 (fr) 2008-08-12 2009-08-05 Ventilateur centrifuge

Country Status (3)

Country Link
EP (1) EP2324249B1 (fr)
IT (1) IT1391671B1 (fr)
WO (1) WO2010018607A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3359821B1 (fr) * 2015-10-06 2021-01-27 Nordic Heater AB Ensemble ventilateur comportant une roue de ventilateur ayant une entrée et une sortie de surfaces de section transversale égales

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1528797A (fr) * 1967-04-17 1968-06-14 Lyonnaise Ventilation Perfectionnements aux ventilateurs centrifuges
DE2357305A1 (de) * 1973-11-16 1975-05-22 Klein Schanzlin & Becker Ag Laufrad fuer kreiselpumpen
DE2550481A1 (de) * 1975-11-11 1977-05-18 Motoren Turbinen Union Kuehlvorrichtung
US5628616A (en) * 1994-12-19 1997-05-13 Camco International Inc. Downhole pumping system for recovering liquids and gas

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1528797A (fr) * 1967-04-17 1968-06-14 Lyonnaise Ventilation Perfectionnements aux ventilateurs centrifuges
DE2357305A1 (de) * 1973-11-16 1975-05-22 Klein Schanzlin & Becker Ag Laufrad fuer kreiselpumpen
DE2550481A1 (de) * 1975-11-11 1977-05-18 Motoren Turbinen Union Kuehlvorrichtung
US5628616A (en) * 1994-12-19 1997-05-13 Camco International Inc. Downhole pumping system for recovering liquids and gas

Also Published As

Publication number Publication date
IT1391671B1 (it) 2012-01-17
EP2324249A1 (fr) 2011-05-25
EP2324249B1 (fr) 2016-03-30
ITPD20080250A1 (it) 2010-02-13

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