US20120003097A1 - Axial flow fan - Google Patents

Axial flow fan Download PDF

Info

Publication number
US20120003097A1
US20120003097A1 US12/162,895 US16289507A US2012003097A1 US 20120003097 A1 US20120003097 A1 US 20120003097A1 US 16289507 A US16289507 A US 16289507A US 2012003097 A1 US2012003097 A1 US 2012003097A1
Authority
US
United States
Prior art keywords
blade
angle
hub
tip
axial flow
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.)
Abandoned
Application number
US12/162,895
Other languages
English (en)
Inventor
Kyung Seok Cho
Se Young Park
Woo June Kim
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.)
Hanon Systems Corp
Original Assignee
Halla Climate Control 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 Halla Climate Control Corp filed Critical Halla Climate Control Corp
Assigned to HALLA CLIMATE CONTROL CORP. reassignment HALLA CLIMATE CONTROL CORP. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CHO, KYUNG SEOK, KIM, WOO JUNE, PARK, SE YOUNG
Publication of US20120003097A1 publication Critical patent/US20120003097A1/en
Assigned to HALLA VISTEON CLIMATE CONTROL CORPORATION reassignment HALLA VISTEON CLIMATE CONTROL CORPORATION CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: HALLA CLIMATE CONTROL CORPORATION
Assigned to HANON SYSTEMS reassignment HANON SYSTEMS CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: HALLA VISTEON CLIMATE CONTROL CORPORATION
Abandoned legal-status Critical Current

Links

Images

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
    • F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
    • F04D29/328—Rotors specially for elastic fluids for axial flow pumps for axial flow fans with unequal distribution of blades around the hub
    • 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
    • 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
    • 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
    • F04D29/386—Skewed blades
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial 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
    • 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
    • F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes

Definitions

  • the present invention relates to an axial flow fan, and more particularly, to an axial flow fan capable of promoting structural stability so as to decrease deformation and unbalance of a blade and accomplishing low noise level.
  • an axial flow fan 10 which is used for cooling heat exchange medium passing an inside of a heat exchanger such as a radiator, a condenser and so on of a vehicle, is provided with a hub 20 coupled to a shaft 52 of a driving source 50 such as a motor, a plurality of blades 30 arranged radially at an outer circumference of the hub 20 , and a fan band 40 for connecting tips of the blades 30 so as to prevent the blades from being deformed.
  • the axial flow fan 10 is therefore rotated by rotational force transferred from the driving source 50 to the hub 20 and blows air in an axial direction by the blades 30 .
  • a shroud 60 fixed to the heat exchanger is used to guide efficiently the air blown by the axial flow fan 10 .
  • the shroud 60 is formed so as to have a blowhole which is sized so that the axial flow fan 10 can be rotatably inserted therein, and support the motor 50 which is a driving source.
  • a leading edge LE which is an edge at a side of a rotational direction and a trailing edge TE which is an edge at an opposite side of the rotational direction have a backward sweeping angle inclined toward an opposite direction of the rotation as it goes from a root 32 of the blade connecting the blade 30 to the hub 20 to a center portion of the blade 30 and a forward sweeping angle inclined toward the rotational direction as it goes to a tip 34 of the blade connecting the blade to the fan band 40 .
  • Such change of the sweep angle is an important factor in performance of the axial flow fan, however it is known to be difficult to obtain satisfactory blowing efficiency and noise reduction effect.
  • improved axial flow fans have been proposed in Korean Patent Application Laid Open Nos. 2002-94183 and 2002-94184 by the present inventor.
  • the former axial flow fan 10 a has a waveform structured blade 30 a , in which the sweeping angles of the leading edge LE and the trailing edge TE change alternately from a backward to a forward and from the forward to the backward as it goes from a root 32 a of the blade toward a tip 34 a of the blade. Further, a chord length CL is gradually increased as it goes from the root 32 a of the blade toward the tip 34 a of the blade.
  • a reference symbol a denotes an angle of the blade 30 in relation to a horizontal line H.
  • Reference symbols 20 a and 40 a denote the hub and the fan bend respectively.
  • the latter axial flow fan 10 b has a waveform structured blade 30 b as same as the former, and a chord length CL (see FIG. 4 ) is also gradually increased as it goes from the root 32 b of the blade toward the tip 34 b of the blade 34 b . Further, the root 32 b of the blade has maximum backward sweeping angle and the tip 34 b of the blade has maximum forward sweeping angle.
  • Reference symbols 20 b and 40 b denote the hub and the fan band respectively.
  • an area between inflection points P 1 and P 2 located on a mid-chord line, which runs along middle points between the leading edge LE and the trailing edge TE, works as an area for dispersing air flow and thus prevent the air flow from being concentrated, thereby capable of increasing blowing efficiency and reducing noise compared to the axial flow fan shown in FIG. 1 and FIG. 2 .
  • an equiangular distribution angle is defined as a case that the distribution angle becomes 360/n.
  • the distribution angle A 1 of the blade can be moved by a predetermined angle in a rotational direction (+) or an opposite direction of the rotation ( ⁇ ) of the axial flow fan in the equiangular distribution angle, and at this time a range in which the angle can be increased or decreased is referred as a clearance angle B.
  • a clearance angle B a range in which the angle can be increased or decreased.
  • U.S. Pat. No. 5,000,660 discloses an axial flow fan with a blade of an uneven structure in which curvatures from a root of the blade to a tip of the blade are different at least between two blades, and the axial flow fan is suggested for the purpose of increasing rigidity of a portion of the root of the blade and reducing noise in a portion of the tip of the blade.
  • the clearance angle B is set to be excessively large.
  • An object of the present invention is to provide an axial flow fan capable of promoting structural stability so as to decrease deformation and unbalance of a blade and accomplishing low noise level by determining a distribution angle of the blade with an optimum clearance angle and thereby determining uneven rate of the blade.
  • the clearance angle is in the range of 6° to 7°
  • a hub-side distribution angle of the blade when assuming that an angle between two lines which pass through a center of the hub and middles of each root of the blade, respectively, where the adjacent two blades and the hub come into contact is, a hub-side distribution angle of the blade, and an angle between two lines which pass through a center of the hub and middles of each tip of the two blades, respectively is a tip-side distribution angle of the blade, the hub-side distribution angle of blade and the tip-side distribution angle of blade are same.
  • the blade has the sweeping angle which changes gradually as it goes from the tip of the blade having a forward angle to the root of the blade having a backward angle and connected to the hub and a plurality of flow dispersing areas between the forward angle area of a side of the tip of the blade and the backward angle area of a side of the root of the blade, in which a direction of the sweeping angle is alternately reversed.
  • the blade has a leading edge extending from the tip of the blade to the root of the blade, and a direction of a sweeping angle of the leading edge changes gradually from a maximum backward angle at the root of the blade to a maximum forward angle at the tip of the blade, wherein the direction of the sweeping angle is reversed from the backward angle at a side of the root of the blade to a forward angle, then reversed to a backward angle and reversed again to a forward angle so as to be connected to a forward angle at a side of the tip of the blade.
  • the blade has a trailing edge extending from the tip of the blade to the root of the blade, and a changing pattern of a sweeping angle of the trailing edge is as same as that of the leading edge.
  • FIG. 1 is an exploded perspective view illustrating an example of a conventional axial flow fan and shroud assembly.
  • FIG. 2 is a partial front view illustrating the conventional axial flow fan.
  • FIG. 3 is a front view illustrating another example of a conventional axial flow fan.
  • FIG. 4 is a sectional view of a blade for defining a chord.
  • FIG. 5 is a perspective view illustrating yet another example of a conventional axial flow fan.
  • FIG. 6 is a partial front view illustrating the axial flow fan shown in FIG. 5 .
  • FIG. 7 is a partial front view for explaining distribution angle of a blade in the axial flow fan shown in FIG. 5 .
  • FIG. 8 is a front view of a preferred embodiment of an axial flow fan according to the present invention.
  • FIG. 9 is a partial front view for explaining a structure of a blade in the axial flow fan shown in FIG. 8 .
  • FIG. 10 to FIG. 15 are graphs comparatively showing noise levels according to frequency in relation to the axial flow fan according to the fan of FIGS. 8 and 9 and the conventional axial flow fan.
  • FIG. 16 is a graph showing variation pattern in overall noise according to variation of a clearance angle.
  • FIG. 8 is an illustration of an axial flow fan according to a preferred embodiment of the present invention.
  • the axial flow fan 100 includes a hub 110 ; a plurality of blades 120 radially arranged at a circumference of the hub 110 and having a sweeping angle of which direction changes alternately in an area between a root 122 of the blade and a tip 124 of the blade; and a fan band 130 for connecting integrally the tips 124 of the each blade 120 .
  • the illustrated axial flow fan 100 has 9 blades 120 .
  • an angle between two lines L 1 and L 2 which pass through a center C of the hub 110 and middles C 1 and C 2 of each root 122 of the blade, respectively, where the adjacent two blades 120 and the hub 110 come into contact is a distribution angle A 1 of the blade
  • a range of an angle by which the distribution angle A 1 of the blade is movable in a rotational direction (+) or an opposite direction of rotation ( ⁇ ) of the axial flow fan 100 is a clearance angle
  • a number of the blade is n
  • an equiangular distribution, representing an interval by which the blades are arranged can be defined by 360/n.
  • the blades 120 can be exemplary arranged in interval of 40°, an actual angular distribution of the blade 120 can be moved in the rotational direction (+) or the opposite direction of rotation ( ⁇ ) of the axial flow fan 100 by a predetermined angle in the range of the clearance angle.
  • an angle A 1 r between two lines L 1 and L 2 which pass through center C of the hub 110 and the middle C 1 and C 2 of each root 122 of the blade, respectively, where the adjacent two blades 120 and the hub 110 come into contact is a hub-side distribution angle of the blade and an angle A 1 t between two lines L 3 and L 4 which pass through center C of the hub 110 and the middle C 3 and C 4 of each tip 124 of the two blades 120 , respectively is a tip-side distribution angle of the blade, it is preferable that the hub-side distribution angle A 1 r of blade and the tip-side distribution angle A 1 t of blade are same.
  • FIG. 9 is a partial front view for explaining a structure of the blade in the axial flow fan of the present invention shown in FIG. 8 .
  • a leading edge LE a trailing edge TE and a mid-chord line ML defined as a line which runs radially along middle points between the leading edge LE and the trailing edge TE.
  • the leading edge LE of the blade 120 has a sweeping angle of which direction is gradually changes from the maximum backward sweeping angle at the root 122 of the blade to the maximum forward sweeping angle at the tip 124 of the blade in a full section between the root 122 of the blade and the tip 124 of the blade.
  • leading edge LE has a flow dispersing area D, which is a small section starting from a first inflection point r 11 , at which the direction of the sweeping angle is changes from backward to forward, passing through a second inflection point r 12 , at which the direction of the sweeping angle is changes again from forward to backward, and reaching to a third inflection point r 13 , at which the direction of the sweeping angle is changes again from backward to forward.
  • the leading edge LE of the blade 120 is formed such that the direction of the sweeping angle gradually changes from backward at a side of root 122 of the blade in an order of forward, backward and forward, and finally to forward at a side of the tip 124 of the blade between a backward area of the side of the root 122 of the blade 120 and a forward area of the side of the tip 124 of the blade 120 .
  • the trailing edge TE of the blade 120 is also formed as same pattern as the leading edge LE, that is, such that the direction of the sweeping angle gradually changes from backward at a side of root 122 of the blade in an order of forward, backward and forward, and finally to forward at a side of the tip 124 of the blade between the backward area of the side of the root 122 of the blade 120 and the forward area of the side of the tip 124 of the blade 120 .
  • the flow dispersing area D forms two flow concentrating parts S 1 and S 2 at which flows are concentrated to a side of the trailing edge TE and thus acts to lessen greatly concentration of the flow, thereby increasing a blowing efficiency relative to power consumption and greatly reducing noise generation.
  • FIG. 10 to FIG. 15 are graphs comparatively showing noise levels throughout frequencies in the case that the clearance angle is 4° to 9° according to the present invention.
  • test to the axial flow fans according to the present invention (the first and second embodiments) and the conventional axial flow fan under the condition of same voltage showed that the axial flow fans according to the present are much lower in noise level than the conventional one.
  • the axial flow fans according to the present invention has much air flow rate in a low rpm and test to the axial flow fans according to the present invention and the conventional axial flow fan under the condition of same air flow rate showed that the axial flow fans according to the present are much lower in noise level, rpm and voltage than the conventional one.
  • noise level of even fan is denoted with black solid line and noise levels of each uneven fan are denoted with gray dotted lines.
  • noise levels of each uneven fan are denoted with gray dotted lines.
  • Table 1 lists data of variation in overall noise according to the clearance angle and FIG. 16 graphically shows the data of table 1.
  • FIG. 16 shows clearly a tendency, in which the noise is very high in the case that the distribution angle of blade is the equiangular distribution angle, that is, the clearance angle is 0°, and the noise is gradually reduced with increase of the clearance angle while the noise is increased again if the clearance angle passes over a specific value.
  • the noise is clearly reduced in the case that the clearance angle is 4° to 9° than in the case of the even fan, particularly noise reduction effect is maximized in the case that the clearance angle is 6° to 7°.
  • the above described axial flow fan is capable of promoting silence operation of an apparatus which employs an axial flow fan as noise can be greatly reduced compared to the conventional axial flow fan by determining the distribution angle of the blade 120 with an optimum clearance angle. Further, blowing efficiency and noise reduction effect can be much increased by adjusting the clearance angle as well as forming the flow dispersing area on the blade.
  • the axial flow fan according to the present invention can generate much air flow rate even in low rpm compared to the conventional one, it is capable of promoting structural stability and thus increasing durability of the axial fan.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US12/162,895 2006-02-03 2007-01-15 Axial flow fan Abandoned US20120003097A1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
KR10-2006-0010535 2006-02-03
KR20060010535 2006-02-03
KR10-2007-0001552 2007-01-05
KR1020070001552A KR101328559B1 (ko) 2006-02-03 2007-01-05 축류팬
PCT/KR2007/000234 WO2007089081A1 (en) 2006-02-03 2007-01-15 Axial flow fan

Publications (1)

Publication Number Publication Date
US20120003097A1 true US20120003097A1 (en) 2012-01-05

Family

ID=38600424

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/162,895 Abandoned US20120003097A1 (en) 2006-02-03 2007-01-15 Axial flow fan

Country Status (6)

Country Link
US (1) US20120003097A1 (ko)
EP (1) EP1979624A4 (ko)
JP (1) JP4895314B2 (ko)
KR (1) KR101328559B1 (ko)
CN (1) CN101379300B (ko)
WO (1) WO2007089081A1 (ko)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110114286A1 (en) * 2008-12-05 2011-05-19 Mitsubishi Heavy Industries, Ltd. Vehicle heat-exchange module and vehicle having the same
US20130189132A1 (en) * 2012-01-23 2013-07-25 Shinano Kenshi Co., Ltd. Compressor and vacuum machine
US9447725B2 (en) 2012-03-23 2016-09-20 Shinano Kenshi Co., Ltd. Compressor and vacuum machine
US20190063464A1 (en) * 2017-08-31 2019-02-28 Ford Global Technologies, Llc Engine cooling fans with uneven blade spacing
USD848485S1 (en) * 2016-03-01 2019-05-14 Yanmar Co., Ltd. Cooling fan for working vehicle
KR20210046800A (ko) * 2018-10-15 2021-04-28 광둥 미디어 화이트 홈 어플라이언스 테크놀로지 이노베이션 센터 컴퍼니 리미티드 이중 반전 팬
US11149551B2 (en) 2017-04-28 2021-10-19 Mitsubishi Electric Corporation Propeller fan
US20220112901A1 (en) * 2019-01-23 2022-04-14 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Impeller of a motor vehicle
US11795975B2 (en) 2015-11-16 2023-10-24 R.E.M. Holding S.R.L. Low noise and high efficiency blade for axial fans and rotors and axial fan or rotor comprising said blade

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101470004B1 (ko) * 2008-07-21 2014-12-05 한라비스테온공조 주식회사 축류팬
KR101218536B1 (ko) * 2010-01-06 2013-01-07 한라공조주식회사 축류팬
KR101681772B1 (ko) * 2010-02-02 2016-12-01 한온시스템 주식회사 차량용 축류팬
CN102207106A (zh) * 2010-03-31 2011-10-05 鸿富锦精密工业（深圳）有限公司 风扇整流架
FR2965314B1 (fr) 2010-09-29 2017-01-27 Valeo Systemes Thermiques Helice pour ventilateur dont la longueur de corde varie
FR2965315B1 (fr) * 2010-09-29 2012-09-14 Valeo Systemes Thermiques Helice pour ventilateur dont l'angle de calage varie
CN102465917A (zh) * 2010-11-05 2012-05-23 台达电子工业股份有限公司 风扇结构
KR101408917B1 (ko) * 2012-01-30 2014-06-18 한라비스테온공조 주식회사 축류팬
CN102788043B (zh) * 2012-08-03 2015-04-01 南充工塑零部件有限公司 发动机风扇
GB2507493B (en) * 2012-10-30 2015-07-15 Solyvent Flakt Ab Air movement fans
WO2017061236A1 (ja) * 2015-10-05 2017-04-13 日立マクセル株式会社 送風装置
JP6704232B2 (ja) * 2015-10-05 2020-06-03 マクセルホールディングス株式会社 送風装置
CN105275854A (zh) * 2015-10-26 2016-01-27 日本电产凯宇汽车电器（江苏）有限公司 一种汽车散热器用的电子风扇总成
KR102548590B1 (ko) * 2016-12-28 2023-06-29 한온시스템 주식회사 축류팬
JP6414197B2 (ja) * 2016-12-28 2018-10-31 ダイキン工業株式会社 軸流ファンおよび送風ユニット
CN106870013A (zh) * 2017-02-21 2017-06-20 戴劲松 叶片间通道扩张的涡轮机工作叶片
CN109424580B (zh) * 2017-08-31 2020-11-20 佛山市顺德区美的电热电器制造有限公司 叶轮和具有其的风机、烹饪器具
KR102496677B1 (ko) * 2018-05-24 2023-02-07 한온시스템 주식회사 축류팬

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6139275A (en) * 1998-07-28 2000-10-31 Kabushiki Kaisha Toshiba Impeller for use in cooling dynamoelectric machine
US20030012656A1 (en) * 2001-06-12 2003-01-16 Kyung Seok Cho Axial flow fan

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5000660A (en) * 1989-08-11 1991-03-19 Airflow Research And Manufacturing Corporation Variable skew fan
IT206701Z2 (it) * 1985-08-02 1987-10-01 Gate Spa Ventilatore assiale particolarmente per autoveicoli
JPH0727096A (ja) * 1993-07-07 1995-01-27 Nippondenso Co Ltd 軸流ファン
JPH10122193A (ja) * 1996-10-22 1998-05-12 Denso Corp 軸流送風機
US6065937A (en) 1998-02-03 2000-05-23 Siemens Canada Limited High efficiency, axial flow fan for use in an automotive cooling system
EP0945627B1 (en) * 1998-03-23 2004-01-02 SPAL S.r.l. Axial flow fan
EP0945625B1 (en) * 1998-03-23 2004-03-03 SPAL S.r.l. Axial flow fan
KR100332539B1 (ko) * 1998-12-31 2002-04-13 신영주 축류팬
JP4075264B2 (ja) * 2000-01-28 2008-04-16 セイコーエプソン株式会社 軸流ファン、遠心力ファン、およびこれらを用いた電子機器
KR100761153B1 (ko) 2001-06-12 2007-09-21 한라공조주식회사 축류팬
KR100761152B1 (ko) 2001-06-12 2007-09-21 한라공조주식회사 축류팬
KR101018925B1 (ko) * 2004-03-19 2011-03-02 한라공조주식회사 축류팬

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6139275A (en) * 1998-07-28 2000-10-31 Kabushiki Kaisha Toshiba Impeller for use in cooling dynamoelectric machine
US20030012656A1 (en) * 2001-06-12 2003-01-16 Kyung Seok Cho Axial flow fan

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110114286A1 (en) * 2008-12-05 2011-05-19 Mitsubishi Heavy Industries, Ltd. Vehicle heat-exchange module and vehicle having the same
US8573343B2 (en) * 2008-12-05 2013-11-05 Mitsubishi Heavy Industries, Ltd. Vehicle heat-exchange module and vehicle having the same
US20130189132A1 (en) * 2012-01-23 2013-07-25 Shinano Kenshi Co., Ltd. Compressor and vacuum machine
US9447725B2 (en) 2012-03-23 2016-09-20 Shinano Kenshi Co., Ltd. Compressor and vacuum machine
US11795975B2 (en) 2015-11-16 2023-10-24 R.E.M. Holding S.R.L. Low noise and high efficiency blade for axial fans and rotors and axial fan or rotor comprising said blade
USD848485S1 (en) * 2016-03-01 2019-05-14 Yanmar Co., Ltd. Cooling fan for working vehicle
US11149551B2 (en) 2017-04-28 2021-10-19 Mitsubishi Electric Corporation Propeller fan
US20190063464A1 (en) * 2017-08-31 2019-02-28 Ford Global Technologies, Llc Engine cooling fans with uneven blade spacing
KR20210046800A (ko) * 2018-10-15 2021-04-28 광둥 미디어 화이트 홈 어플라이언스 테크놀로지 이노베이션 센터 컴퍼니 리미티드 이중 반전 팬
US11506211B2 (en) * 2018-10-15 2022-11-22 Guangdong Midea White Home Appliance Technology Innovation Center Co., Ltd. Counter-rotating fan
KR102518997B1 (ko) * 2018-10-15 2023-04-05 광둥 미디어 화이트 홈 어플라이언스 테크놀로지 이노베이션 센터 컴퍼니 리미티드 이중 반전 팬
US20220112901A1 (en) * 2019-01-23 2022-04-14 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Impeller of a motor vehicle

Also Published As

Publication number Publication date
JP4895314B2 (ja) 2012-03-14
KR101328559B1 (ko) 2013-11-13
EP1979624A4 (en) 2012-05-16
EP1979624A1 (en) 2008-10-15
KR20070079905A (ko) 2007-08-08
JP2009531578A (ja) 2009-09-03
CN101379300A (zh) 2009-03-04
WO2007089081A1 (en) 2007-08-09
CN101379300B (zh) 2011-11-23

Similar Documents

Publication Publication Date Title
US20120003097A1 (en) Axial flow fan
JP4046164B2 (ja) 軸流フアン
KR100332539B1 (ko) 축류팬
US6908287B2 (en) Axial flow fan
KR100820857B1 (ko) 축류팬
US20070020103A1 (en) High efficiency axial fan
US20080044292A1 (en) Axial Impeller with Enhance Flow
KR20050046000A (ko) 회전축에 대하여 경사진 블레이드를 구비한 원심 팬 임펠러
EP1455095B1 (en) Axial-flow fan
KR100663965B1 (ko) 축류팬
CN101772651A (zh) 轴流式风机
KR101160991B1 (ko) 차량용 냉각팬
KR20080098937A (ko) 축류팬
KR100761153B1 (ko) 축류팬
KR20220043729A (ko) 축류팬
KR101218536B1 (ko) 축류팬
KR20100041127A (ko) 팬 및 쉬라우드 조립체
CN113123977A (zh) 风机、空调室外机和空调器
KR101469982B1 (ko) 차량용 냉각팬 조립체
KR20100009789A (ko) 축류팬
KR101427429B1 (ko) 차량용 냉각팬 조립체
CN116997724A (zh) 螺旋桨式风扇及制冷装置
KR100484825B1 (ko) 축류팬
KR100224737B1 (ko) 휀과 쉬라우드 조립체

Legal Events

Date Code Title Description
AS Assignment

Owner name: HALLA CLIMATE CONTROL CORP., KOREA, REPUBLIC OF

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:CHO, KYUNG SEOK;PARK, SE YOUNG;KIM, WOO JUNE;REEL/FRAME:026935/0993

Effective date: 20110311

AS Assignment

Owner name: HALLA VISTEON CLIMATE CONTROL CORPORATION, KOREA,

Free format text: CHANGE OF NAME;ASSIGNOR:HALLA CLIMATE CONTROL CORPORATION;REEL/FRAME:030704/0574

Effective date: 20130312

AS Assignment

Owner name: HANON SYSTEMS, KOREA, REPUBLIC OF

Free format text: CHANGE OF NAME;ASSIGNOR:HALLA VISTEON CLIMATE CONTROL CORPORATION;REEL/FRAME:037007/0103

Effective date: 20150728

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION