EP3085966B1 - Axialstromventilator - Google Patents

Axialstromventilator Download PDF

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Publication number
EP3085966B1
EP3085966B1 EP13899760.6A EP13899760A EP3085966B1 EP 3085966 B1 EP3085966 B1 EP 3085966B1 EP 13899760 A EP13899760 A EP 13899760A EP 3085966 B1 EP3085966 B1 EP 3085966B1
Authority
EP
European Patent Office
Prior art keywords
protruding portion
axial flow
blades
edge side
trailing edge
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.)
Active
Application number
EP13899760.6A
Other languages
English (en)
French (fr)
Other versions
EP3085966A4 (de
EP3085966A1 (de
Inventor
Yasuaki Kato
Takahide Tadokoro
Atsushi Kono
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.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of EP3085966A1 publication Critical patent/EP3085966A1/de
Publication of EP3085966A4 publication Critical patent/EP3085966A4/de
Application granted granted Critical
Publication of EP3085966B1 publication Critical patent/EP3085966B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D19/00—Axial-flow pumps
    • F04D19/002—Axial flow fans
    • 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
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
    • 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
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/304—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the trailing edge of a rotor blade

Definitions

  • the present invention relates to an axial flow blower.
  • an axial flow blower achieving reduction in noise through improvement of a blade structure
  • an axial flow blower disclosed in Patent Literature 1 is exemplified.
  • a radial center portion of a trailing edge of each blade is formed into a protruding shape curved so as to swell to a suction side, thereby equalizing a blowing-out velocity of the air in a radial direction of the blade.
  • JP 4501575 B2 (mainly FIG. 3 and FIG. 8)
  • JP2006037800A provides a blower capable of reducing noise and improving efficiency by improving a blade structure.
  • JP2002257088A provides an axial flow fan capable of reducing blade area without complicating a shape of a blade trailing edge part, improving a forming property and reducing cost, and saving energy by maintaining a load on a driving motor low when rotation speed is increased to increase the quantity of air flow.
  • JP2011179330A discloses an impeller includes a hub provided in a rotation center and a plurality of blades provided around the hub.
  • each blade is formed into a recessed curve on the peripheral side with respect to a suction side, and formed into a projecting curve on a hub side with respect to the suction side.
  • the projecting curve on the hub side is formed into a substantially arcuate shape, and the value of the curvature radius of the projecting curve formed into the substantially arcuate shape is reduced from the leading edge side of each blade toward the trailing edge side thereof.
  • the present invention has been made in view of the above, and has an obj ect to provide an axial flow blower capable of preventing increase in noise.
  • an axial flow blower including: a propeller fan; and a driving unit configured to rotate the propeller fan, the propeller fan including: the hub; and a plurality of blades supported by the hub, in which a pressure surface of each of the blades includes a protruding portion curved so as to swell to a suction side, in which a height of the protruding portion of the each of the blades on a trailing edge side is larger than a height of the protruding portion on a leading edge side, and in which a radial position of an apex of the protruding portion on the trailing edge side is located on a radially inner side with respect to a radial position of the apex of the protruding portion on the leading edge side.
  • an outer peripheral edge of the each of the blades may be curved so as to bend to the suction side.
  • a position of an inner end of the protruding portion on the trailing edge side is located on the radially inner side with respect to a position of the inner end of the protruding portion on the leading edge side.
  • a width dimension of the protruding portion on the trailing edge side may be larger than a width dimension of the protruding portion on the leading edge side.
  • the increase in noise can be prevented.
  • FIG. 1 is a sectional view of an axial flow blower according to a first embodiment of the present invention
  • FIG. 2 is a perspective view of a propeller fan of the axial flow blower according to the first embodiment.
  • An axial flow blower 100 includes a propeller fan 1, a motor 4 being a driving unit, and a bellmouth 5.
  • the propeller fan 1 includes a hub 2 and a plurality of blades 3.
  • the plurality of blades 3 are supported by the hub 2, and are arranged in a radiate manner on an outer peripheral surface of the hub 2 having substantially a columnar shape (including a truncated conical shape). Note that, in the illustrated example, the propeller fan including three blades is illustrated.
  • a center portion of the hub 2 is connected to the motor 4, and the propeller fan 1 is rotated by a driving force of the motor 4.
  • the bellmouth 5 is arranged on a radially outer side of the propeller fan 1. That is, under a state in which a proper gap is defined between an outer peripheral portion of the propeller fan 1 and an inner peripheral portion of the bellmouth 5, the propeller fan 1 is surrounded by the bellmouth 5.
  • an upper space on the drawing sheet of FIG. 1 corresponds to a suction side 6, and a lower space on the drawing sheet of FIG. 1 corresponds to a blowing-out side 7.
  • Each of the blades 3 is a forward blade having a leading edge extending to a forward side in a rotating direction RD.
  • edges 8 of each of the blades 3 an edge facing the forward side in the rotating direction RD is referred to as a leading edge 8a, and an edge facing a backward side in the rotating direction RD is referred to as a trailing edge 8c.
  • a portion connecting a radially outer portion of the leading edge 8a and a radially outer portion of the trailing edge 8c to each other is referred to as an outer peripheral edge 8b.
  • a portion connecting each of the blades 3 and the hub 2 to each other is referred to as a connection edge 8d.
  • suction surface 9a One surface of each blade 3 surrounded by the leading edge 8a, the outer peripheral edge 8b, the trailing edge 8c, and the connection edge 8d as described above is referred to as a suction surface 9a, and the other surface thereof is referred to as a pressure surface 9b.
  • the suction surface 9a is a surface on the suction side 6, and the pressure surface 9b is a surface on the blowing-out side 7.
  • a rotation center line of the propeller fan 1 is referred to as a rotation axis 10 .
  • the rotating direction RD of the propeller fan is schematically indicated by the outline arrows of the drawings, and flows of the air are schematically indicated by the dashed arrows .
  • FIG. 3 is a plan view for illustrating one of the blades as an representative example
  • FIG. 4 is a view for illustrating the propeller fan according to the first embodiment when circumferential changes of the pressure surface are projected on a radial plane including the rotation axis
  • FIG. 5 is a view for particularly illustrating only the pressure surface in one radial cross-section in the same manner as that of FIG. 4 .
  • the dot-and-dash lines A1 to A6 of FIG. 3 correspond to lines along which radial cross-sections of the hub and the blade are taken.
  • the dot-and-dash lines A1 to A6 include the rotation axis, and extend continuously from the connection edge to the outer peripheral edge.
  • the lines B1 to B6 of FIG. 4 respectively correspond to the cross-sections of the pressure surface taken along the dot-and-dash lines A1 to A6.
  • FIG. 5 is an illustration of only the pressure surface taken along the line B3 of FIG. 4 .
  • the pressure surface 9b includes a protruding portion 11 curved so as to swell to the suction side 6. Assuming that a straight line BL (chain double-dashed line of FIG. 5 ) is brought into abutment on the pressure surface 9b from the blowing-out side 7, a portion swelling from the straight line BL to the suction side 6 corresponds to the protruding portion 11.
  • An end portion of the protruding portion 11 on the outer peripheral edge side of each blade 3 is referred to as an outer end 11a of the protruding portion, and an end portion of the protruding portion 11 on the connection edge side thereof is referred to as an inner end 11b.
  • a most distant point of the protruding portion 11 from the straight line BL (chain double-dashed line) is referred to as an apex 11c of the protruding portion.
  • a distance between the apex 11c of the protruding portion 11 and the straight line BL (chain double-dashed line) is referred to as a height H of the protruding portion 11.
  • a radial distance (denoted by W in FIG.
  • a width dimension W of the protruding portion 11 is referred to as a width dimension W of the protruding portion 11.
  • a line connecting points of the outer end 11a of the protruding portion 11, a line connecting points of the inner end 11b thereof, and a line connecting points of the apex 11c thereof are indicated by the curved lines La, Lb, and Lc, respectively.
  • the pressure surface 9b includes the protruding portion 11 curved so as to swell to the suction side 6.
  • the outer end 11a of the protruding portion 11 is positioned on a radially inner side with respect to the outer peripheral edge 8b of each of the blades 3. Further, the height H of the protruding portion 11 on the trailing edge side is larger than the height H of the protruding portion 11 on the leading edge side.
  • the height H of the protruding portion 11 becomes larger as approaching to the trailing edge.
  • a radius position (radial position) of the apex 11c of the protruding portion 11 on the trailing edge side is located on the radially inner side with respect to a radius position (radial position) of the apex 11c of the protruding portion 11 on the leading edge side.
  • the radial position of the protruding portion 11 is shifted radially inward as approaching to the trailing edge.
  • aposition of the inner end 11b of the protruding portion 11 on the trailing edge side is located on the radially inner side with respect to a position of the inner end 11b of the protruding portion 11 on the leading edge side.
  • the position of the inner end 11b of the protruding portion 11 is shifted radially inward as approaching to the trailing edge.
  • a point on the curved line Lb which is obtained by connecting the points of the inner end 11b of the protruding portion 11, is shifted radially inward as approaching to the trailing edge.
  • the width dimension W of the protruding portion 11 on the trailing edge side is larger than the width dimension W of the protruding portion 11 on the leading edge side.
  • the width dimension W of the protruding portion 11 becomes larger as approaching to the trailing edge.
  • each of the blades 3 is curved so as to bend to the suction side 6.
  • the flow velocity increases from the radially inner side toward the radially outer side, and becomes maximum in a region positioned slightly radially outward of a radial center.
  • the flow velocity decreases from the region toward the outer peripheral edge being a position of a maximum radius.
  • a flow is directed radially outward due to a centrifugal force, thereby reducing a flow rate on the hub side. Accordingly, insufficient flow rate causes the flow to be separated from a blade surface. Due to turbulence generated by the separation, noise may be increased, and efficiency may be reduced due to the separation.
  • the pressure surface 9b of each of the blades 3 includes the protruding portion 11, thereby suppressing appearance of the distribution of the flow rate in the radial direction, which causes the above-mentioned problems.
  • the pressure surface 9b acts so as to push out the air in a direction of the blowing-out side 7.
  • the protruding portion 11 functions as an escape route for the pushed air, and the flow directed toward the protruding portion 11 is generated on the pressure surface 9b.
  • the radial position of the apex 11c of the protruding portion 11 on the trailing edge side is located on the radially inner side with respect to the radial position of the apex 11c of the protruding portion 11 on the leading edge side.
  • the air on the radially outer side of the pressure surface 9b is moved to the radially inner side.
  • the height H of the protruding portion 11 on the trailing edge side is larger than the height H of the protruding portion 11 on the leading edge side. Accordingly, the effect of moving the air to the radially inner side can be further enhanced, and imbalanced concentration of the flow rate on the radially outer side can be further suppressed.
  • the distribution of the flow rate in the radial direction can be almost equalized.
  • the protruding portion 11 is formed over the entire angle range where the radial cross-sections extend continuously from the connection edge 8d to the outer peripheral edge 8b (entire angle range where the pressure surface extends continuously in the radial direction from the connection edge 8d to the outer peripheral edge 8b). Accordingly, without abruptly changing the flow of the air, the distribution of the flow rate in the radial direction can be controlled. Thus, turbulence of the air can be suppressed, and increase in noise and reduction in efficiency caused by the turbulence of the air can be prevented.
  • the propeller fan at a vicinity of the outer peripheral edge, a swirling flow is generated from the pressure surface to the suction surface through the outer side of the outer peripheral edge due to a pressure difference between the pressure surface and the suction surface.
  • the radially outer side of the protruding portion is inclined so as to push the air to the inner peripheral side, thereby increasing the pressure and intensifying the swirling flow from the pressure surface to the suction surface.
  • the outer end of the protruding portion is arranged on the inner peripheral side with respect to the outer peripheral edge, thereby preventing intensification of the swirling flow generated on the outer side of the outer peripheral edge.
  • the outer peripheral edge of each of the blades is curved so as to bend to the suction side. That is, the outer peripheral edge 8b is positioned on the suction side 6 with respect to the straight line BL (chain double-dashed line) of FIG. 5 . Accordingly, even in the above-mentioned case where the swirling flow from the pressure surface to the suction surface may be generated, because the outer peripheral edge is curved to bend to the suction side, a pressure change is started before the air is caused to flow out from the pressure surface to the outer side of the outer peripheral edge. Consequently, the abrupt pressure change can be prevented from occurring afterward, and turbulence caused by the swirling can be reduced. Further, even if the swirling flow is generated, a position of the swirling flow can be shifted from the suction surface to the suction side. Thus, an influence of the swirling flow can be lessened.
  • the position of the inner end 11b of the protruding portion 11 on the trailing edge side is located on the radially inner side with respect to the position of the inner end 11b of the protruding portion 11 on the leading edge side. Accordingly, as compared to a mode of merely forming the protruding portion, it is possible to intensify an effect of increasing the radially-inner-side flow rate of the air passing through the propeller fan.
  • the width dimension W of the protruding portion 11 on the trailing edge side is larger than the width dimension W of the protruding portion 11 on the leading edge side. Accordingly, with a view to equalizing the radial distribution of the flow velocity on the blowing-out side by forming the protruding portion, it is possible to enlarge a controllable range of the radial distribution of the flow velocity on the blowing-out side.
  • the distribution of the axial flow velocity on the blowing-out side can be almost equalized. Accordingly, increase in noise and reduction in efficiency, which are caused by the extensive distribution of the flow velocity, can be prevented, thereby being capable of obtaining the propeller fan capable of achieving reduction in noise and high efficiency. In addition, it is possible to suppress turbulence of the flow, which may be generated in order to almost equalize the flow velocity. Thus, effects of reducing noise and increasing efficiency can be enhanced.
  • an outdoor unit of an air-conditioning apparatus is given.
  • the axial flow blower according to the present invention is applied to a blower of the outdoor unit of the air-conditioning apparatus, it is possible to reduce aerodynamic noise caused when generating a desired quantity of air, and to reduce necessary power. In other words, it is possible to obtain the air-conditioning apparatus capable of reducing noise and excellent in energy saving performance .

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

Claims (4)

  1. Axialströmungsgebläse (100), umfassend:
    einen Propellerlüfter (1); und
    eine Antriebseinheit, die eingerichtet ist, den Propellerlüfter (1) zu drehen,
    wobei der Propellerlüfter (1) umfasst:
    eine Nabe (2); und
    eine Vielzahl von Schaufeln (3), die durch die Nabe (2) gestützt werden,
    wobei eine Druckoberfläche (9b) jeder der Schaufeln (3) einen vorstehenden Abschnitt (11) umfasst, der gekrümmt ist, um zu einer Saugseite hin anzuschwellen,
    wobei eine Höhe (H) des vorstehenden Abschnitts jeder der Schaufeln (3) auf einer Hinterkantenseite größer ist als eine Höhe des vorstehenden Abschnitts auf einer Vorderkantenseite, und
    wobei das Axialströmungsgebläse dadurch gekennzeichnet ist, dass:
    eine radiale Position eines Scheitels (11c) des vorstehenden Abschnitts auf der Hinterkantenseite in Bezug auf eine radiale Position des Scheitels des vorstehenden Abschnitts auf der Vorderkantenseite auf einer radial inneren Seite angeordnet ist, und
    eine Position eines inneren Endes (11b) des vorstehenden Abschnitts auf der Hinterkantenseite in Bezug auf eine Position des inneren Endes des vorstehenden Abschnitts auf der Vorderkantenseite auf der radial inneren Seite angeordnet ist.
  2. Axialströmungsgebläse nach Anspruch 1, wobei eine äußere Umfangskante (8b) jeder der Schaufeln (3) gekrümmt ist, um sich zur Saugseite zu biegen.
  3. Axialströmungsgebläse nach Anspruch 1 oder 2, wobei ein Breitenmaß (W) des vorstehenden Abschnitts auf der Hinterkantenseite größer ist als ein Breitenmaß des vorstehenden Abschnitts auf der Vorderkantenseite.
  4. Außeneinheit einer Klimaanlage, die das Axialströmungsgebläse (100) nach einem der Ansprüche 1 bis 3 verwendet.
EP13899760.6A 2013-12-20 2013-12-20 Axialstromventilator Active EP3085966B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2013/084322 WO2015092924A1 (ja) 2013-12-20 2013-12-20 軸流送風機

Publications (3)

Publication Number Publication Date
EP3085966A1 EP3085966A1 (de) 2016-10-26
EP3085966A4 EP3085966A4 (de) 2017-08-16
EP3085966B1 true EP3085966B1 (de) 2020-05-20

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EP13899760.6A Active EP3085966B1 (de) 2013-12-20 2013-12-20 Axialstromventilator

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EP (1) EP3085966B1 (de)
JP (1) JPWO2015092924A1 (de)
WO (1) WO2015092924A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11965522B2 (en) 2015-12-11 2024-04-23 Delta Electronics, Inc. Impeller

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CN106870451A (zh) * 2015-12-11 2017-06-20 台达电子工业股份有限公司 叶轮及风扇
US11236760B2 (en) 2015-12-11 2022-02-01 Delta Electronics, Inc. Impeller and fan
JP6719641B2 (ja) * 2017-02-28 2020-07-08 三菱電機株式会社 プロペラファン、送風機及び空気調和機
JP6428833B2 (ja) 2017-04-14 2018-11-28 ダイキン工業株式会社 プロペラファン
CN110506164B (zh) * 2017-04-19 2021-07-13 三菱电机株式会社 螺旋桨式风扇及空调装置用室外机
CN111133201B (zh) * 2017-10-03 2021-10-08 三菱电机株式会社 螺旋桨式风扇以及轴流式鼓风机
CN108506247B (zh) * 2018-05-09 2024-08-23 约克广州空调冷冻设备有限公司 叶片及使用其的轴流叶轮
WO2019214632A1 (zh) 2018-05-09 2019-11-14 约克广州空调冷冻设备有限公司 叶片及使用其的轴流叶轮
JP7289235B2 (ja) * 2019-07-18 2023-06-09 株式会社コロナ エアコン装置の室外機用プロペラファン
JP7258225B2 (ja) * 2020-03-24 2023-04-14 三菱電機株式会社 軸流ファン、送風装置、及び、冷凍サイクル装置
BR112023017994A2 (pt) * 2021-03-12 2023-10-03 Daikin Ind Ltd Ventilador de hélice e aparelho de refrigeração
JP2024090454A (ja) * 2022-12-23 2024-07-04 パナソニックＩｐマネジメント株式会社 軸流ファンおよび美容装置

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JP3524410B2 (ja) * 1998-12-25 2004-05-10 シャープ株式会社 プロペラファン
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JP2002257088A (ja) * 2001-03-06 2002-09-11 Toshiba Kyaria Kk 軸流ファン
JP4501575B2 (ja) * 2004-07-26 2010-07-14 三菱電機株式会社 軸流送風機
JP5263198B2 (ja) * 2010-02-26 2013-08-14 パナソニック株式会社 羽根車と送風機及びそれを用いた空気調和機
JP6035508B2 (ja) * 2012-04-02 2016-11-30 パナソニックＩｐマネジメント株式会社 送風機とそれを用いた室外ユニット
JP2013249787A (ja) * 2012-06-01 2013-12-12 Daikin Industries Ltd プロペラファン

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11965522B2 (en) 2015-12-11 2024-04-23 Delta Electronics, Inc. Impeller

Also Published As

Publication number Publication date
EP3085966A4 (de) 2017-08-16
WO2015092924A1 (ja) 2015-06-25
EP3085966A1 (de) 2016-10-26
JPWO2015092924A1 (ja) 2017-03-16

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