EP0259061A2 - Ventilateur axial et aube en faisant partie - Google Patents

Ventilateur axial et aube en faisant partie Download PDF

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Publication number
EP0259061A2
EP0259061A2 EP87307335A EP87307335A EP0259061A2 EP 0259061 A2 EP0259061 A2 EP 0259061A2 EP 87307335 A EP87307335 A EP 87307335A EP 87307335 A EP87307335 A EP 87307335A EP 0259061 A2 EP0259061 A2 EP 0259061A2
Authority
EP
European Patent Office
Prior art keywords
fan
axial flow
fan blade
angle
installation
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Withdrawn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
EP87307335A
Other languages
German (de)
English (en)
Other versions
EP0259061A3 (fr
Inventor
Kenichi Nanbu
Takashi Ishida
Hideo Hirama
Takuzo Kanno
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.)
Seiko Electronic Components Ltd
Original Assignee
Seiko Electronic Components 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 Seiko Electronic Components Ltd filed Critical Seiko Electronic Components Ltd
Publication of EP0259061A2 publication Critical patent/EP0259061A2/fr
Publication of EP0259061A3 publication Critical patent/EP0259061A3/fr
Withdrawn legal-status Critical Current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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F04D29/384—Blades characterised by form

Definitions

  • This invention concerns an axial flow fan and a fan blade therefor.
  • An axial flow fan having a hub provided with a plurality of fan blades each of whose angle of installation varies radially thereof, the angle of installation being constituted by the angle between a straight line connecting the leading and trailing edges of the respective fan blade on a predetermined cross section of the latter concentric to the axis of the fan, on the one hand, and a plane perpendicular to the said axis on the other hand.
  • the angle of installation of each blade increases gradually in a radially inward direction but this makes it difficult to achieve an air flow which is equally spread over each fan blade.
  • a fan blade for an axial flow fan the angle of installation of the fan blade varying radially thereof, the angle of installation being constituted by the angle between a straight line connecting the leading and trailing edges of a fan blade on a predetermined cross section of the latter concentric to the axis of a fan adapted to be provided with the fan blade, on the one hand, and a plane perpendicular to the said axis, on the other hand, characterised in that the angle of installation is at its maximum in relation to a said cross section which is between the radially inner and outer ends of the fan blade.
  • the distance between the said leading and trailing edges of the fan blade is at its greatest between the radially inner and outer ends of the fan blade.
  • the width of the blade at its radially inner end is greater than at its radially outer end.
  • the invention also comprises an axial flow fan having a hub provided with a plurality of fan blades each of whose angle of installation varies radially thereof, the angle of installation being constituted by the angle between a straight line connecting the leading and trailing edges of the respective fan blade on a predetermined cross section of the latter concentric to the axis of the fan, on the one hand, and a plane perpendicular to the said axis, on the other hand, characterised in that the angle of installation of each fan blade is at its maximum in relation to a cross section which is between the radially inner and outer ends of the respective fan blade.
  • the fan blades may be mounted within a fan casing.
  • the fan casing may comprise a block having a centrally disposed cylindrical aperture extending therethrough, the fan blades being disposed in the cylindrical aperture. There may also be a motor which is secured to and externally of the said block.
  • the fan casing comprises a duct.
  • the duct is preferably venturi-shaped, the fan blades being disposed at the throat of the venturi-shaped duct.
  • a known axial flow fan comprises, as shown in Figures 1 and 2, a motor 3 which rotates, with respect to the axis of a rotor shaft 5, a rotor portion of the fan consisting of a hub 2 having a plurality of fan blades 1.
  • the fan comprises a fan casing 4 which holds the motor 3 and accommodates the rotor portion.
  • Figure 3 there is shown a first embodiment of an axial flow fan which is generally similar to that of Figures 1 and 2 but which has fan blades 1 whose angles of installation differ from those of Figures 1 and 2.
  • angle of installation is explained with reference to Figures 4 and 5, Figure 4 being a plan view of the rotor portion of the axial flow fan of Figure 3, and Figure 5 being a development of a cylindrical cross section of a fan blade thereof with respect to the rotor shaft 5.
  • a straight line 12 represents a plane which passes through a point 6 on the leading edge 14 of a fan blade 1, the plane being perpendicular to the axis of the rotor shaft 5.
  • the point 6 is on a cylindrical cross section 16 which is concentric to the axis of the rotor shaft 5.
  • a straight line 13 connects the point 6 with a point 9 on the trailing edge 15 of the fan blade 1, the point 9 being on the cross section 16.
  • the angle formed by the two straight lines 12, 13 is represented by X which is designated as the "angle of installation".
  • an angle of installation Y is defined by the relationship between a leading edge point 7 and a trailing edge point 10 on a cross section 17
  • an angle of installation Z is defined by the relationship between a leading edge point 8 and a trailing edge point 11 on a cross section 18.
  • each fan blade 1 in order to allow the air flow to be efficiently produced by the fan blades 1, the angle of installation of each fan blade 1 is made to increase gradually from the outer circumference of the fan blade 1 toward the inner circumference thereof.
  • the known axial flow blades X ⁇ Y ⁇ Z in accordance with the air velocity produced by rotation of the fan on the assumption that air flows equally between the inner and outer circumference of each fan blade 1.
  • the fan blades 1 are generally capable of expelling an amount of air which is large relative to an increment in the angle of installation, but the above-mentioned generation of vortices or disturbance in the air flow leads to a deterioration in the air flow efficiency, which in turn leads to an increase in the load on the fan. Furthermore, the air flow is inverted through the gap between the fan casing 4 and fan blades 1 as a result of the differences in pressure, so that it is difficult to achieve the desired air flow which is equally spread over the whole of each fan blade from its radially inner end to its radially outer end. This is because the load increases to a greater extent than any increase in the air flow rate, that is, the efficiency of the axial flow fan deteriorates.
  • the angle of installation is at its maximum Y in relation to the cross section 17 which is between the radially inner and outer ends of the fan blade. That is, the angle of installation is larger at a central portion of the blade than that at the inner end and the outer end thereof.
  • Such an arrangement produces a desired air flow that varies at different portions of the fan blades in a suitable manner, as well as producing improved efficiency and a reduction in the noise level.
  • the relationship between the angles of installation X, Y and Z of the inner portion, central portion and outer portion of each fan blade 1 of the axial flow fan is X ⁇ Y, Z ⁇ Y.
  • the axial flow fan shown in Figure 3 has fan blades 1 such that the rotational load is reduced by virtue of a reduction in the angle of installation at the inner portion and the outer portion of each fan blade for the purpose of decreasing the projected area of the fan blade 1 in the direction of rotation of the motor 3. Furthermore, the angle of installation can be arranged to be such as to prevent the generation of vortices.
  • each fan blade 1 can be arranged to be relatively large because the air flow is smoother here than at the inner and outer ends thereof. This allows a relatively large quantity of air to be caused to flow at this central portion, so compensating for the air flow at the inner and outer end portions. The generation of vortices is reduced in spite of the large angle of installation.
  • the rotor portion of the fan consists of four fan blades 1 carried by the hub 2, the fan casing 4 both providing a mounting for the motor 3 and accommodating the rotor portion.
  • the fan casing 4 is bored with a circular hole which surrounds the rotating fan blades 1.
  • the angle of installation of each fan blade 1 is larger at a central portion thereof than at the outer end portion and inner end portion thereof.
  • Figures 6 and 7 are perspective views of rotor portions of second and third embodiments respectively of an axial flow fan of the present invention.
  • Figure 6 illustrates an embodiment in which the length of a blade, i.e. the distance from the front end of a fan blade 1 to the rear end thereof, is arranged to be long at the central portion thereof without any thickness restriction in the vertical direction in contrast to the embodiment shown in Figure 3, whereby to produce a larger air flow rate. That is to say, the distance 20 between the leading and trailing edges 14, 15 of each fan blade 1 is at its greatest between the radially inner and outer ends of the fan blade 1.
  • Figure 7 illustrates an embodiment in which eight fan blades 1 are provided although more fan blades can be provided, if desired. Furthermore, in the construction of Figure 7, the diameter of the hub portion 2 is small and this assists in producing a large air flow and a relatively thin fan.
  • FIG 8 is a perspective view of a fourth embodiment of the present invention, wherein the fan casing 4 is formed as a block 21 having the shape of a rectangular parallelopiped.
  • the block 21 has a centrally disposed cylindrical aperture 22 extending therethrough, the fan blades 1 being disposed in the cylindrical aperture 22.
  • FIG 9 illustrates a fifth embodiment in which, the fan casing 4, shown in Figure 8, is reduced in size for the purpose of cost reduction, although the fan casing 4 can be completely cut out if desired.
  • Figure 10 illustrates a sixth embodiment in which the fan casing is constituted by a block or "ring" 23 which is arranged around the fan blades 1 and to which the motor 3 (not shown in Figure 10) can be secured externally.
  • Figure 11 illustrates a seventh embodiment in which the fan casing 4 is substantially omitted, i.e. reduced to a minimum, and in which the length of each fan blade 1 becomes shorter in the direction of movement from the inside to the outside, for the purpose of improvement in the efficiency at the outer portion, the improved efficiency being similar to that achieved by the reduction of the angle of installation. That is to say, the width 24 of each fan blade 1 at its radially inner end or root is greater than at its radially outer end.
  • FIG 12 illustrates an eighth embodiment in which the fan casing 4 comprises a Venturi-shaped duct 25, for the purpose of making the air flow smooth, as a result of which there is an improvement in efficiency.
  • the fan blades 1 are disposed at the throat of the venturi-shaped duct 25.
  • the efficiency of an axial flow fan is improved, and the noise level thereof is reduced by reducing the generation of vortices by arranging that the angle of installation of each fan blade 1 is greater at the central portion thereof than at the radially inner and outer portions thereof.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP87307335A 1986-09-01 1987-08-19 Ventilateur axial et aube en faisant partie Withdrawn EP0259061A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP205691/86 1986-09-01
JP20569186A JPS6361800A (ja) 1986-09-01 1986-09-01 軸流送風機

Publications (2)

Publication Number Publication Date
EP0259061A2 true EP0259061A2 (fr) 1988-03-09
EP0259061A3 EP0259061A3 (fr) 1989-02-22

Family

ID=16511109

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87307335A Withdrawn EP0259061A3 (fr) 1986-09-01 1987-08-19 Ventilateur axial et aube en faisant partie

Country Status (2)

Country Link
EP (1) EP0259061A3 (fr)
JP (1) JPS6361800A (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2294092A (en) * 1994-10-12 1996-04-17 Christopher Martin Dunphy Destratification fan
US6238185B1 (en) * 1998-12-04 2001-05-29 Sunonwealth Electric Machine Industry Co., Ltd. Fan with low noise, high air flow and high wind pressure
DE102012004617A1 (de) * 2012-03-06 2013-09-12 Ziehl-Abegg Ag Axialventilator
ITMI20120451A1 (it) * 2012-03-22 2013-09-23 Elica Spa Girante per il convogliamento assiale di fluidi, in particolare per sistemi di refrigerazione
US10344764B2 (en) 2015-08-18 2019-07-09 Sanyo Denki Co., Ltd. Axial blower and series-type axial blower
RU195333U1 (ru) * 2019-11-19 2020-01-23 Общество с ограниченной ответственностью "АЭРДИН" Лопатка осевого рабочего колеса вентилятора
CN114832608A (zh) * 2021-02-01 2022-08-02 中国石油化工股份有限公司 一种用于危化品泄漏应急处置的综合应急站

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB376647A (en) * 1932-01-01 1932-07-14 William Alexander Improvements in the blades of screw rotors for operating with any fluid
US2097389A (en) * 1932-07-07 1937-10-26 Mey Rene De Fan blade or the like
GB848278A (en) * 1957-04-16 1960-09-14 Enso Gutzeit Oy Improvements in or relating to impellers
GB1171001A (en) * 1966-03-28 1969-11-19 Rotron Inc Axial Flow Propeller Fan.
FR1583878A (fr) * 1967-06-10 1969-12-05
US4411598A (en) * 1979-12-12 1983-10-25 Nissan Motor Company, Limited Fluid propeller fan

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5783696A (en) * 1980-11-14 1982-05-25 Nippon Denso Co Ltd Fan

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB376647A (en) * 1932-01-01 1932-07-14 William Alexander Improvements in the blades of screw rotors for operating with any fluid
US2097389A (en) * 1932-07-07 1937-10-26 Mey Rene De Fan blade or the like
GB848278A (en) * 1957-04-16 1960-09-14 Enso Gutzeit Oy Improvements in or relating to impellers
GB1171001A (en) * 1966-03-28 1969-11-19 Rotron Inc Axial Flow Propeller Fan.
FR1583878A (fr) * 1967-06-10 1969-12-05
US4411598A (en) * 1979-12-12 1983-10-25 Nissan Motor Company, Limited Fluid propeller fan

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2294092A (en) * 1994-10-12 1996-04-17 Christopher Martin Dunphy Destratification fan
GB2294092B (en) * 1994-10-12 1999-01-06 Christopher Martin Dunphy A destratification fan
US6238185B1 (en) * 1998-12-04 2001-05-29 Sunonwealth Electric Machine Industry Co., Ltd. Fan with low noise, high air flow and high wind pressure
DE102012004617A1 (de) * 2012-03-06 2013-09-12 Ziehl-Abegg Ag Axialventilator
WO2013131641A2 (fr) 2012-03-06 2013-09-12 Ziehl-Abegg Ag Ventilateur axial
US10781818B2 (en) 2012-03-06 2020-09-22 Ziehl-Abegg Se Axial fan
ITMI20120451A1 (it) * 2012-03-22 2013-09-23 Elica Spa Girante per il convogliamento assiale di fluidi, in particolare per sistemi di refrigerazione
EP2642130A1 (fr) * 2012-03-22 2013-09-25 Elica S.p.A. Roue pour transport axial des fluides, en particulier pour systèmes de réfrigération
US10344764B2 (en) 2015-08-18 2019-07-09 Sanyo Denki Co., Ltd. Axial blower and series-type axial blower
RU195333U1 (ru) * 2019-11-19 2020-01-23 Общество с ограниченной ответственностью "АЭРДИН" Лопатка осевого рабочего колеса вентилятора
CN114832608A (zh) * 2021-02-01 2022-08-02 中国石油化工股份有限公司 一种用于危化品泄漏应急处置的综合应急站
CN114832608B (zh) * 2021-02-01 2023-03-17 中国石油化工股份有限公司 一种用于危化品泄漏应急处置的综合应急站

Also Published As

Publication number Publication date
JPS6361800A (ja) 1988-03-17
EP0259061A3 (fr) 1989-02-22

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Inventor name: KANNO, TAKUZO

Inventor name: ISHIDA, TAKASHI

Inventor name: NANBU, KENICHI

Inventor name: HIRAMA, HIDEO