EP0486691B1 - Centrifugal fan - Google Patents

Centrifugal fan Download PDF

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Publication number
EP0486691B1
EP0486691B1 EP91903340A EP91903340A EP0486691B1 EP 0486691 B1 EP0486691 B1 EP 0486691B1 EP 91903340 A EP91903340 A EP 91903340A EP 91903340 A EP91903340 A EP 91903340A EP 0486691 B1 EP0486691 B1 EP 0486691B1
Authority
EP
European Patent Office
Prior art keywords
blades
blade
fan
centrifugal fan
fan wheel
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.)
Expired - Lifetime
Application number
EP91903340A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0486691A4 (en
EP0486691A1 (en
Inventor
Alexei Fedorovich Andreichenko
Vitaly Alexandrovich Vasiliev
Mikhail Yakovlevich Gembarzhevsky
Tatyana Stepanovna Solomakhova
Igor Rostislavovich Schekin
Nikolai Illarionovich Vasilenko
Gennady Sergeevich Kulikov
Vladimir Ivanovich Malov
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.)
Gosudarstvenny Nauchno-Issledovatelsky Tsentr Tsen
Nauchno-Issledovatelsky I Proektno-Konstruktorsky
Original Assignee
GNITSTS AEROGIDRODINAMICHESKOG
Gosudarstvenny Nauchno-Issledovatelsky Tsentr Tsentralnogo Aerogidrodinamicheskogo Instituta Imeni Professora Ne Zhukovskogo
NAUCHNO-ISSLEDOVATELSKY I PROEKTNO-KONSTRUKTORSKY INSTITUT PO OBORUDOVANIJU DYLA KONDITSIONIROVANIA VOZDUKHA I VENTILYATSII
NI I PK I OBORU DYLA KONDITSIO
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 GNITSTS AEROGIDRODINAMICHESKOG, Gosudarstvenny Nauchno-Issledovatelsky Tsentr Tsentralnogo Aerogidrodinamicheskogo Instituta Imeni Professora Ne Zhukovskogo, NAUCHNO-ISSLEDOVATELSKY I PROEKTNO-KONSTRUKTORSKY INSTITUT PO OBORUDOVANIJU DYLA KONDITSIONIROVANIA VOZDUKHA I VENTILYATSII, NI I PK I OBORU DYLA KONDITSIO filed Critical GNITSTS AEROGIDRODINAMICHESKOG
Publication of EP0486691A1 publication Critical patent/EP0486691A1/en
Publication of EP0486691A4 publication Critical patent/EP0486691A4/en
Application granted granted Critical
Publication of EP0486691B1 publication Critical patent/EP0486691B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04D29/26—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
    • F04D29/26—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
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis

Definitions

  • the present invention relates to the design of a centrifugal fan.
  • it relates to centrifugal fans with medium and high specific rotational speed used in ventilation and air-conditioning systems.
  • Centrifugal fans having a spiral casing which houses a fan wheel, comprising carrying and overlying discs between which are secured blades whose lateral surfaces are curved, have been known for many years.
  • a fan is disclosed in US 1 341 882, in which the blades have surfaces defined by two truncated cones and a flat surface lying in a plane which is tangent to the surfaces o the cones, so that each blade has a forwardly curved heel and a backwardly curved tip.
  • the basic requirements for modern fans are high aerodynamic parameters, a wide range of economical operation, ease of manufacture, and strength and reliability of construction.
  • the aerodynamic parameters are the volumetric flow rate of gas passing through the fan, total pressure provided by the fan, and the efficiency of the fan.
  • the "range of economical operation” should be understood as the range of its operating modes at a high efficiency.
  • each blade the angle formed by a segment of the curved produced in the section of the blade side surface by a plane perpendicular to the axis, and by a circle whose centre lies on the axis and which passes through the point of the said curve segment nearest to the wheel axis, is constant throughout the width of the fan wheel.
  • This angle will be referred to hereinafter as the "blade entrance angle”.
  • the angle of these blades formed by the segment of the curve produced in the section of the side surface of each blade by the plane which is perpendicular to the wheel axis and by the circle whose centre lies on the wheel axis and which passes through the point of this segment of the curve farthest from the wheel axis is also constant throughout the width of the fan wheel. This angle will be referred to below as the "blade exit angle”.
  • each side surface of the blade is of a curvilinear shape and, being intersected by any plane perpendicular to the wheel axis, forms a segment of a curve which, jointly with the circle whose centre lies on the wheel axis and which passes through the point of this segment of the curve nearest to the wheel axis, forms a blade entrance angle which grows throughout the wheel width in the direction from the carrying disc to the overlying one.
  • the entrance angle of each blade grows across the width of the fan wheel from the carrying to the overlying disc. This provides for the uniform loading of blades, reduces the intensity of secondary flows in the channels between blades and narrows the zone of separation in the gas flow which improves the aerodynamic characteristics of the centrifugal fan and broadens the range of its economical performance.
  • the blade is twisted around its longitudinal axis in the course of manufacture.
  • the practice of using the centrifugal fans with such blades has demonstrated that their performance is particularly efficient when the blade entrance angle at the overlying disc is at least one and a half times larger than the blade entrance angle at the carrying disc.
  • Such twisting of the blade is possible only in case of a large axial extension of the blade at which the relative twisting angle is small. If, however, the axial extension of the blade is small, the relative twisting angle is large. At a large relative twisting angle the material traditionally used for the manufacture of blades fails in the course of manufacture.
  • the blades of such centrifugal fans are very long axially.
  • the diameter of the inlet hole of the fan wheel is large, the radial length of each blade is small and the exit angles of blades bent against rotation of the wheel are small. It is a known fact that at a small radial length and small exit angles of blades the total pressure provided by the centrifugal fan is small.
  • twisting of blades causes residual stresses in their material which reduce the strength parameters of blades so that at high peripheral velocities of the fan wheel, characterized by strong centrifugal forces, the blades loss stability and become deformed. This tells adversely on the strength and reliability of the centrifugal fan.
  • the invention is essentially aimed at providing a centrifugal fan, wherein due to configuration of the lateral surface of the blades, there is provided an increase in the full pressure produced by the fan, a better strength of its structure and reliability in operation.
  • a centrifugal fan whose spiral casing accommodates a fan wheel comprises of a carrying disc and an overlying disc with blades secured therebetween, at least one curvilinear surface of each blade in the section by a plane perpendicular to the fan wheel axis defines a segment of the curve forming, together with the circle whose centre lies on the fan wheel axis which passes through the point of the segment of the curve, nearest to said centre, a blade entrance angle growing across the width of the fan wheel in the direction from the carrying disc to the overlying disc; said curvilinear side surface of the blade has the shape of a ruled developable surface with the generating lines inclined towards the plane perpendicular to the fan wheel axis at an angle varying from 45° to 85° and the projection of at least one of said generating lines on the plane perpendicular to the fan wheel axis is a tangent to the segment of the curve in said plane.
  • the requirement for increasing the blade entrance angle across the width of the fan wheel from the carrying disc to the overlying disc in the disclosed fan is ensured by the above-stated shape of the side surface of the blade. And this shape can be manufactured without subjecting the blade material to twisting or any other substantial plastic deformations; it is enough to bend it in order to produce the required shape of the side surface and blade profile. This procedure does not involve residual stresses which limit the axial dimensions of the blade. Consequently, the disclosed centrifugal fan can be made with blades having a variable entrance angle across the width of the fan wheel and having any, even small, axial length.
  • the fans with a small axial length of their blades are characterized by an increased radial length which, all other conditions being equal, brings about an increase in the exit angles of each blade and, accordingly, a higher total pressure provided by the fan.
  • a smaller axial length of the blades and elimination of considerable residual stresses in the material of the blades improves the strength paramaters of blades and the fan wheel as a whole. This permits either to increase the peripheral velocity of the fan wheel thereby improving the aerodynamic characteristics of the fan, or, by retaining the same peripheral velocity of the fan wheel, to enhance the mechanical strength and reliability of the centrifugal fan.
  • the blades made from sheet materials are used at peripheral velocities of the fan wheel which do not exceed about 70 m/s. At peripheral velocities exceeding 70 m/s the blades are of a profiled shape. This shape males it possible to design the blades both with one and two side surfaces in the form of a ruled developable surface.
  • the ruled developable surface should be cylindrical.
  • the ruled developable surface should be conical.
  • the conical surface intensifies the changes of the blade entrance angle across the width of the fan wheel in the direction from the carrying disc to the overlying one.
  • segment of the curve formed when the side surface of the blade is intersected by the plane of the carrying disc should form an arc of the circle wherein the relation of the square of chord length to the difference of squares of the diameters of the circles passing, respectively, through the exit and entrance edges of blades should be within 0.2 to 0.25.
  • segment of a curve which is formed when the side surface of the blade is intersected by the plane of the carrying disc should form on the side of the blade entrance edge an arc of the circle conjugate with the segment of a straight line from the side of the blade exit edge and that the relation of the square of the distance between the ends of said segment of the curve to the difference of squares of the diameters of the circles passing, respectively, through the exit and entrance edges of blades should vary from 0.15 to 0.22.
  • the relation of the diameter of the circle passing through the exit edges of the blades to the diameter of the carrying disc should vary from 0.9 to 1.1.
  • the blades used in the disclosed fan wheel have, each, a profile with a longer or shorter segment of a straight line. This permits producing a selection of discrete aerodynamic characteristics of the centrifugal fan, thereby broadening the zone of effective operation of the fan, i.e. the zone of high efficiency performance.
  • centrifugal fan used, for example, in air conditioning and ventilating systems of industrial or civic buildings.
  • a centrifugal fan comprises a spiral casing 1 (Fig. 1) having an inlet pipe 2 and an outlet pipe 3 (Fig. 2).
  • the chamber 4 of the spiral casing 1 houses a fan wheel 5 formed by a carrying disc 6 (Fig. 1) and an overlying disc 7 installed between which over the periphery are blades 8 forming a chamber 9 (Fig. 2) inside the fan wheel 5 and channels between blades 8a.
  • the carrying disc 6 is secured by a hub 10 (Fig. 1) on a drive shaft 11 (not shown in the drawings).
  • the relative width of the fan wheel i.e. the relation of the width b2 of the fan wheel 5 at the exit edges of the blades 8 to the diameter D2 of the circle passing through the exit edges of the blades 8 is equal to 0.25 in this embodiment of the invention.
  • the entrance angle ⁇ 1 of the blade 8 grows along the width b1 of the fan wheel 5 in the direction from the carrying disc 6 to the overlying disc 7.
  • the entrance angle ⁇ '1 (Fig. 5) of the blade 8 at the carrying disc 6 amounts approximately to 15° while the entrance angle ⁇ '' 1 of the blade 8 at the overlying disc 7 is about 21°.
  • the exit angles ⁇ 2 (Fig. 4) of the blade 8 are determined in a similar way.
  • the exit angle ⁇ 2 of each blade 8 also grows along the width b2 of the fan wheel 5 in the direction from the carrying disc 6 to the overlying disc 7.
  • the blade exit angle ⁇ ' 2 (Fig. 5) at the carrying disc 6 is about 32° while the blade exit angle ⁇ '' 2 at the overlying disc 7 is about 35°.
  • Each curvilinear side surface 12 (Fig. 5) is about 32° while the blade exit angle ⁇ '' 2 at the overlying disc 7 is about 35°.
  • the blade 8 is a ruled developable surface, cylindrical in this version of realization.
  • the generating lines 16 of this surface 12 are inclined to the plane perpendicular to the axis O1-O1 of the fan wheel 5 at an angle ⁇ varying from 45° to 85°.
  • the angle ⁇ is 78° and the plane perpendicular to the axis O1-O1 of the fan wheel 5 is the plane of the carrying disc 6.
  • the projection 17 of at least one of the generating lines 16 (just one in this version) on the plane of the carrying disc 6 is a tangent to the segment 13 of the curve in this plane.
  • the segment 13 of the curve formed by intersection of the side surface 12 of the blade 8 with the plane of the carrying disc 6 is an arc 18 (Fig. 6) of the circle 19.
  • the shape of this arc 18 of the circle 19 in such that the relation of the square of the length l1 of the chord 20 of said arc 18 to the difference of squares of diameters D2, D1 of the circles 21, 22 passing, respectively, through the exit edges 23 and entrance edges 24 of the blades 8 lies within the limits from 0.2 to 0.25; in the given embodiment of the centrifugal fan this relation is 0.21.
  • blades 8 are also possible.
  • the blades 8 should be of a profiled type. Such a blade 8 is shown in Fig. 7.
  • the aerodynamic parameters of the fan can be raised by using the blades 8 with at least one side surface 12 being conical.
  • the design of the fan remains the same as that of a fan with cylindrical blades. This version of the blade 8 appears in Fig. 8.
  • each of their blades 8 should be so constructed that when its side surface 12 is intersected by the plane of the carrying disc 6 this forms a segment 13 of the curve which at the side of the entrance edge 24 of the blade 8 is the arc 25 of the circle 26 conjugate with the segment 27 of the straight line 28 at the side of the exit edge 23 of this blade 8.
  • the shape of this segment 13 of the curve is such that the relation of the square of distance l2 between its ends to the difference of squares D2, D1 of the circles 21, 22 passing, respectively, through the exit edges 23 and entrance edges 24 of the blades 8 lies within the limits from 0.15 to 0.22. In the given embodiment of the centrifugal fan this relation is 0.19. It should be emphasized that this version of the blades 8 is possible both with the cylindrical and conical shapes of the side surface 12.
  • the profile of the blades 8 (Fig. 10) is made in the form of an arc 25 of the circle 26 conjugate with the segment 27 of the straight line 28 in which the relation of the diameter D2 of the circle 21 passing through the exit edges 23 of the blades 8 to the diameter D3 of the carrying disc 6 lies within the limits from 0.9 to 1.1.
  • Shown in Fig. 10 is a version of the centrifugal fan wherein said relation is equal to 1.05.
  • the centrifugal fan functions as follows. As the drive shaft 11 (not shown in the drawings) rotates, its rotation is transmitted via the carrying disc 6 secured on the shaft 11 by means of the hub 10 to the fan wheel 5 installed in the chamber 4 of the spiral casing 1. When the fan wheel 5 rotates along arrow A (Fig. 2), the gas moves in the axial direction shown by arrows B (Fig. 1) through the inlet pipe 2 into the chamber 9 inside the fan wheel 5 where it is acted upon by the vacuum near the entrance edges 24 of the blades 8, changes its direction from axial to radial and moves onto the blades 8 of the fan wheel 5. Turning of the gas flow through 90° causes nonuniformity of its velocities along the entrance edges 24 of the blades 8.
  • This nonuniformity is such that the gas flowing around the blades 8 at the overlying disc 7 has a higher speed than at the carrying disc 6.
  • the present invention can most advantageously be used in centrifugal medium and high-speed fans employed in ventilation and air conditioning systems.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Nitrogen And Oxygen Or Sulfur-Condensed Heterocyclic Ring Systems (AREA)
EP91903340A 1990-06-08 1990-06-08 Centrifugal fan Expired - Lifetime EP0486691B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/SU1990/000147 WO1991019104A1 (en) 1990-06-08 1990-06-08 Centrifugal fan

Publications (3)

Publication Number Publication Date
EP0486691A1 EP0486691A1 (en) 1992-05-27
EP0486691A4 EP0486691A4 (en) 1992-09-02
EP0486691B1 true EP0486691B1 (en) 1995-03-15

Family

ID=21617690

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91903340A Expired - Lifetime EP0486691B1 (en) 1990-06-08 1990-06-08 Centrifugal fan

Country Status (5)

Country Link
EP (1) EP0486691B1 (ja)
JP (1) JPH05505438A (ja)
DE (1) DE69017911T2 (ja)
FI (1) FI102309B (ja)
WO (1) WO1991019104A1 (ja)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FI122540B (fi) * 2007-04-20 2012-03-15 Flaekt Woods Ab Radiaalisiipipyörä
JP2009127541A (ja) * 2007-11-26 2009-06-11 Daikin Ind Ltd 遠心ファン
JP4994421B2 (ja) * 2009-05-08 2012-08-08 三菱電機株式会社 遠心ファン及び空気調和機
EP2921711B1 (de) * 2014-03-21 2020-10-21 punker GmbH Radialventilatorrad und Gebläseanordnung
CN104564806A (zh) * 2014-12-18 2015-04-29 徐工集团工程机械股份有限公司 一种叶片、离心式风机叶轮及离心式风机
DE102015118557A1 (de) 2015-10-30 2017-05-04 Ebm-Papst Mulfingen Gmbh & Co. Kg Aufdachklimaanlage

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191023096A (en) * 1910-10-06 1911-02-16 James Keith Improvements in Centrifugal Fans.
US1341882A (en) * 1915-09-07 1920-06-01 Buffalo Forge Co Centrifugal fan
GB464449A (en) * 1935-11-22 1937-04-19 James Keith & Blackman Company Improvements in centrifugal fans
DE952547C (de) * 1951-10-30 1956-11-15 Bruno Eck Dr Ing Ventilatorlaufrad radialer Bauart
FR2378962A1 (fr) * 1977-01-28 1978-08-25 Kawasaki Heavy Ind Ltd Rotor de ventilateur a flux diagonal pour la propulsion d'un gaz
SU1337555A1 (ru) * 1985-11-10 1987-09-15 Ленинградский Политехнический Институт Им.М.И.Калинина Рабочее колесо центробежного вентил тора

Also Published As

Publication number Publication date
FI102309B1 (fi) 1998-11-13
FI920519A0 (fi) 1992-02-07
EP0486691A4 (en) 1992-09-02
JPH05505438A (ja) 1993-08-12
DE69017911D1 (de) 1995-04-20
FI102309B (fi) 1998-11-13
EP0486691A1 (en) 1992-05-27
WO1991019104A1 (en) 1991-12-12
DE69017911T2 (de) 1995-10-12

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