EP1070849B1 - Axiallüfter - Google Patents

Axiallüfter Download PDF

Info

Publication number
EP1070849B1
EP1070849B1 EP20000114849 EP00114849A EP1070849B1 EP 1070849 B1 EP1070849 B1 EP 1070849B1 EP 20000114849 EP20000114849 EP 20000114849 EP 00114849 A EP00114849 A EP 00114849A EP 1070849 B1 EP1070849 B1 EP 1070849B1
Authority
EP
European Patent Office
Prior art keywords
axial flow
blade
flow fan
blades
fan
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
EP20000114849
Other languages
English (en)
French (fr)
Other versions
EP1070849A2 (de
EP1070849A3 (de
Inventor
Chang Joon Kim
Hong Yeol Yoon
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.)
LG Electronics Inc
Original Assignee
LG Electronics Inc
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
Priority claimed from KR1019990029803A external-priority patent/KR100336132B1/ko
Priority claimed from KR1019990029802A external-priority patent/KR100347048B1/ko
Application filed by LG Electronics Inc filed Critical LG Electronics Inc
Publication of EP1070849A2 publication Critical patent/EP1070849A2/de
Publication of EP1070849A3 publication Critical patent/EP1070849A3/de
Application granted granted Critical
Publication of EP1070849B1 publication Critical patent/EP1070849B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/54—Fluid-guiding means, e.g. diffusers
    • F04D29/541—Specially adapted for elastic fluid pumps
    • F04D29/545—Ducts
    • F04D29/547—Ducts having a special shape in order to influence fluid flow
    • 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
    • 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
    • F04D29/66—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
    • F25D2317/06—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
    • F25D2317/068—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the fans
    • F25D2317/0681—Details thereof

Definitions

  • the present invention relates, in general, to an axial flow fan for refrigerators, used for feeding cool air from an evaporator into both a freezer compartment and a fresh compartment in refrigerators, and, more particularly, to an axial flow fan for refrigerators optimally designed in a variety of designing factors, such as the number of blades, hub ratio, sweep angle, pitch angle and maximum camber ratio, thus accomplishing a reduction in operational noise of the refrigerators and in vortex formed around the fan and thereby finally reducing its flow resistance.
  • Fig. 1 is a perspective view of a conventional axial flow fan for refrigerators.
  • Fig. 2 is a sectional view of the blade tip of the conventional axial flow fan.
  • the conventional axial flow fan comprises a hub 1, which is firmly mounted to the rotating shaft of the drive motor, with a plurality of blades 5 regularly fixed around the hub 1.
  • the number of the blades 5 is typically set to three to five, with a hub ratio of the hub diameter to the outer diameter of the fan being set to 0.25 ⁇ 0.3 and a pitch angle of each blade 5 ranging from 25° to 35°.
  • the pitch angle is formed between the radial straight line of each blade 5 and another straight line extending from the blade leading edge to the blade trailing edge. This pitch angle is determined by an inclination of each blade 5 relative to a plane perpendicular to the rotating axis of the fan.
  • each trailing blade 5 undesirably confronts the vortex stream formed by a leading blade 5, thus generating fluid noise.
  • BVI blade vortex interaction
  • the blade tip 5a of an axial flow fan forms a smoothly curved cross-section consisting of a pressure surface 5b and a negative pressure surface 5c.
  • air pressure caused by an air current acts on the pressure surface 5b, while negative pressure acts on the negative pressure surface 5c opposite to the surface 5b. Due to such a smoothly curved cross-section of the blade tip 5a, static pressure of the air current flowing from the pressure surface 5b to the negative pressure surface 5c is restored abruptly and quickly.
  • the blade passing frequency (BPF) which is the main frequency of fluid noise caused by a collision of the air current against the blades 5 during operation of the fan and is calculated by a plus integral times of the result of multiplication of the number of blades 5 by rpm of the fan, is reduced to a low level.
  • the conventional doors of a refrigerator used for intercepting noise leaking from the compressor and fan of the machine room and from the axial flow fan used for accomplishing a circulation of cool air within the refrigerator into the outside of the cabinet of the refrigerator through a variety of passages, have been typically designed to intercept high frequency noise of not lower than 700Hz. Therefore, it is almost impossible for such conventional doors to intercept such a low blade passing frequency (BPF) generated from the conventional axial flow fan.
  • BPF blade passing frequency
  • the conventional axial flow fan typically generates operational noise having a large low frequency band and a low BPF, and so the conventional doors of refrigerators fail to accomplish a desired noise intercepting effect in the case of operational noise of the conventional axial flow fan, but regrettably allow the noise to leak from the axial flow fan to the outside of the cabinet of the refrigerator. Such operational noise disturbs those around the refrigerator.
  • Fig. 3 is a front view, showing a conventional shroud installed around the axial flow fan for refrigerators.
  • Fig. 4 is a sectional view, showing the construction of the conventional shroud for axial flow fans.
  • the conventional shroud 7 is installed around the blades 5 of the fan, with an annular rim 9 being formed closely around the blades 5 while being bulged to the front of the fan in an air inlet direction.
  • Such a conventional shroud 7 is installed around the blade tips 5a of the fan while leaving a predetermined annular gap between the tips 5a and the inside edge of the shroud 7.
  • the above shroud 7 guides the cool air current when the air current flows in an axial direction of the fan during operation.
  • the annular rim 9 formed closely around the blades 5 while being bulged to the front of the fan in the air inlet direction, induces a smooth airflow during operation of the fan. That is, the cool air current flows over the bulged annular rim 9, thus smoothly flowing on the shroud 7 without forming an undesirable flow resistance.
  • the conventional shroud 7 has the following problem. That is, since the annular rim 9 is formed closely around the blades 5 while being bulged to the front of the fan in the air inlet direction as best seen in Fig. 5 , the rear surface of the rim 9 in the air outlet side of the fan is concaved, and so cool air discharged from the fan comes into undesirable collision against the concave surface of the rim 9 and forms an intensive and large-scaled vortex, thus finally increasing the flow loss.
  • the annular rim 9, positioned around the blades of the axial flow fan has so large a diameter that the inlet air is partially brought into collision against the concave surface of the rim 9 while undesirably forming an intensive and large-scaled vortex around the concave surface, thus resulting in a substantial flow loss during operation of the fan.
  • EP 0 913 584 A1 which represents the closest prior art discloses an axial flow fan comprising seven fan blades symmetrically arranged around a hub. Each blade has the shape of an airfoil.
  • EP 0 557 239 A2 discloses an axial flow fan provided with a plurality of fan blades having also an airfoil cross section profile.
  • the blade pitch angle decreases from the blade root to the blade tip and a mid chord skew angle is five to six tenths of a blade spacing angle.
  • EP 0 583 091 A2 discloses an axial fan having five fan blades and a hub ratio which is about 30% of the outer diameter of the fan.
  • EP 0 174 487 A1 discloses an axial fan having seven fan blades each of which is curved in a forward direction and gives a technical teaching concerning mathematical equations for defining the curved design of the blade surface.
  • the present invention has been made keeping in mind the above problems occurring in the prior art, and the object of the present invention is to provide an axial flow fan for refrigerators, which is optimally designed in a variety of designing factors, such as the number of blades, hub ratio, sweep angle, pitch angle and maximum camber ratio, thus accomplishing a desired reduction in operational noise of the refrigerators and in vortex formed around the fan and thereby finally reducing its flow resistance.
  • Another object of the present invention is to provide an axial flow fan for refrigerators, which is improved in the structure of its shroud so as to be free from a formation of a vortex in the discharged cool air current in the air outlet side of the fan, thus minimizing its flow loss.
  • the primary embodiment of the present invention provides an axial flow fan for refrigerators, comprising a hub mounted to the rotating shaft of a drive motor, with at least seven blades regularly fixed around the hub, wherein a variety of designing factors of the blades as defined in the characterizing portion of claim 1, such as the number of plates, hub ratio, sweep angle, pitch angle and maximum camber ratio, are optimally designed to allow a smooth flow of cool air agreeable with both the large pressure loss and complex flow passage of refrigerators while accomplishing a reduction in air flow noise of the refrigerators.
  • an axial flow fan for refrigerators comprising a hub mounted to a rotating shaft of a motor, with a plurality of blades regularly fixed around the hub and a shroud installed around the blades to guide an air current, wherein the shroud consists of an annular rim formed closely around the blades while being bulged to the front of the fan in an air inlet direction, and a vortex prevention means provided on a concave back surface of the annular rim for preventing discharged air from forming a vortex stream in back of the fan.
  • Fig. 6 is a perspective view of an axial flow fan for refrigerators in accordance with the preferred embodiment of the present invention.
  • Figs. 7a and 7b are front and side views of the axial flow fan according to the preferred embodiment of this invention.
  • Figs. 8a and 8b are sectional views, showing the shape of a blade included in the axial flow fan according to the preferred embodiment of this invention.
  • Fig. 9 is a sectional view of the blade tip of the axial flow fan according to this invention.
  • the axial flow fan of this invention comprises a hub 51, which is firmly mounted to the rotating shaft of the drive motor, with a plurality of blades 55 regularly fixed around the hub 51.
  • the number of the blades 55 is preferably set to at least seven.
  • the hub ratio of the hub diameter ID to the outer diameter OD of the fan is set to 0.45 ⁇ 0.55, with the diameter ID of the hub 51 being set to 55 mm ⁇ 5 mm and the outer diameter OD of the fan being set to 110 mm ⁇ 10 mm.
  • each blade 55 ranges from 30° to 34°.
  • each blade 55 is an angle formed between a straight line extending between the center of the blade hub 55b and the center of the blade tip 55a and another straight line extending between the center of the blade hub 55b and the center of the hub 51.
  • This sweep angle ⁇ of each blade 55 expresses the tilt of the blade 55 in the rotating direction of the blades 55.
  • the pitch angle ⁇ of each blade 55 is 32° ⁇ 2° at the blade tip 55a and 45° ⁇ 2° at the blade hub 55b.
  • each blade 55 is an angle formed between a straight line extending between the blade leading edge 57a to the blade trailing edge 57b and an X-axis perpendicular to a Z-axis that is the rotating axis of the fan.
  • This pitch angle ⁇ of each blade 55 expresses the slope of the blade 55 relative to a plane perpendicular to the Z-axis.
  • the maximum camber position of each blade 55 is set to 0.65, with the camber positions being uniformly distributed on each blade 55 from the blade hub 55b to the blade tip 55a.
  • the maximum camber ratio of each blade 55 is 11.5% at the blade tip 55a and 8% at the blade hub 55b.
  • the maximum camber position of each blade 55 is indicated as a ratio(CP/CX) of the distance CP from the blade leading edge 57a to a point being spaced furthest from the blade 55 on a cord CL that is a straight line extending from the blade leading edge 57a to the blade trailing edge 57b to the length CX of the cord CL.
  • the distance between said straight line and said position on the blade 55 is the maximum camber C.
  • the maximum camber ratio is a ratio of the maximum camber C to the cord length CX.
  • each blade 55 is zero. This rake angle expresses the slope of the blade 55 relative to a positive axial direction.
  • each blade of the axial flow fan when designing each blade of the axial flow fan to have a large sweep angle ⁇ , a large pitch angle ⁇ , and a large maximum camber ratio, it is possible to desirably reduce fluid noise generated by the fan during operation.
  • the blade passing frequency (BPF) which is the main frequency of fluid noise caused by a collision of the air current against the blades 55 during operation of the fan and is calculated by a plus integral times of the result of multiplication of the number of blades 55 by rpm of the fan, is increased to a high level. Therefore, the doors of a refrigerator typically designed to intercept high frequency noise effectively intercept such a BPF. It is thus possible to desirably reduce operational noise of refrigerators.
  • the blade tip 55a of each blade 55 of the axial flow fan forms a curved cross-section consisting of a pressure surface 56b and a negative pressure surface 56a.
  • air pressure caused by an air current acts on the pressure surface 56b, while negative pressure acts on the negative pressure surface 56a opposite to the surface 56b.
  • the blade tip 55a is curved from the pressure surface 56b to the negative pressure surface 56a while forming a predetermined radius of curvature. In such a case, it is preferable to set the radius of curvature of the blade tip 55a to the same as the radius of not larger than 0.1 times of the diameter of the fan.
  • Figs. 10 to 14 are graphs showing operational noise of the axial flow fan of the invention as a function of a variety of designing factors of the axial flow fan.
  • Fig. 10 is a graph showing operational noise of the axial flow fan as a function of the hub ratio of the fan. This graph shows that it is possible to accomplish a desired low operational noise of 22.3 ⁇ 0.2dB when the hub ratio of the blades 55 is set to 0.45 ⁇ 0.55. Particularly when setting the hub ratio of the blades to 0.5, it is possible to accomplish a minimum operational noise of the fan.
  • Fig. 11 is a graph showing operational noise of the axial flow fan as a function of the sweep angle ⁇ of the blades 55. This graph shows that it is possible to accomplish a desired minimum operational noise of 22.4 ⁇ 0.2dB when the sweep angle ⁇ of each blade 55 is set to 32° ⁇ 34°.
  • Fig. 12 is a graph showing the operational noise of the axial flow fan as a function of the pitch angle ⁇ of the blades 55. This graph shows that it is possible to accomplish a desired minimum operational noise of 22.3 ⁇ 0.2dB when the pitch angle ⁇ of each blade 55 is set to 32° ⁇ 2° at the blade tip 55a and to 45° ⁇ 2° at the blade hub (55b).
  • Fig. 13 is a graph showing the operational noise of the axial flow fan as a function of the maximum camber position of the axial flow fan. This graph shows that it is possible to accomplish a desired minimum operational noise of 22.5dB when the maximum camber position is set to 0.65, with the maximum camber ratio of each blade 55 being set to 11.5% at the blade tip 55a and to 8% at the blade hub 55b.
  • Fig. 14 is a graph showing operational noise of the axial flow fan according to the invention as a function of the rake angle of the axial flow fan. This graph shows that it is possible to accomplish a desired minimum operational noise of 23dB when the rake angle is set to zero.
  • the shrouds of this invention effectively reduce the operational noise of the axial flow fan by 1.2dB to 2.3dB in comparison with the conventional shroud.
  • the present invention provides an axial flow fan for refrigerators.
  • This axial flow fan is optimally designed in a variety of designing factors, such as the number of blades, hub ratio, sweep angle, pitch angle and maximum camber ratio, thus allowing a smooth flow of cool air agreeable with both the large pressure loss and complex flow passage of refrigerators while accomplishing a reduction in air flow noise of the refrigerators.
  • the axial flow fan of this invention increases the blade passing frequency (BPF), which is the main frequency of fluid noise caused by a collision of the air current against the blades during operation of the fan, at least two times.
  • BPF blade passing frequency
  • the doors of a refrigerator typically designed to intercept high frequency noise effectively intercept such a high level BPF. It is thus possible to desirably reduce operational noise of refrigerators.
  • the blade tip of each blade is curved from its pressure surface to its negative pressure surface while forming a predetermined radius of curvature.
  • the blades during rotation are thus less likely to form a vortex stream in their trailing positions and desirably reduce the blade vortex interaction (BVI), in which each trailing blade undesirably confronts a vortex stream formed by a leading blade during operation of a conventional axial flow fan, thus generating fluid noise.
  • BVI blade vortex interaction
  • a vortex prevention means is provided on the back surface of the shroud's annular rim for preventing an undesirable collision of a discharged air current against the concave back surface of the rim, thus preventing a formation of a vortex stream in back of the rim and reducing air flow loss of the fan, and reducing operational noise of the fan.

Claims (4)

  1. Axialstromlüfter für Kühlschränke, der eine Nabe (51) umfasst, die an einer Drehwelle eines Motors montiert ist und wenigstens sieben um die Nabe (51) regelmäßig befestigte Schaufeln (55) besitzt,
    dadurch gekennzeichnet, dass
    ein Nabenverhältnis zwischen einem Nabendurchmesser (ID) und einem Außendurchmesser des Lüfters auf 0,45-0,55 gesetzt ist, ein Anstellwinkel (Ψ), jeder der Schaufeln an einer Schaufelspitze (55a) 32° ± 2° und an einer Schaufelnabe (55b) 45° ± 2° beträgt, ein maximales Krümmungsverhältnis jeder der Schaufeln (55) an der Schaufelspitze (55a) 11,5 ± 0,5 % und an der Schaufelnabe (55b) 8 ± 0,5 % beträgt und ein Kippwinkel (Θ) jeder der Schaufeln (55) im Bereich von 32° bis 34° liegt, wobei ein Neigungswinkel jedes der Schaufeln (55) null ist.
  2. Axialstromlüfter nach Anspruch 1, wobei die Anzahl der Schaufeln (55) neun ist.
  3. Axialstromlüfter nach Anspruch 1,
    wobei eine Position mit maximaler Krümmung jeder der Schaufeln (55) auf 0,65 ± 0,05 gesetzt ist, wobei die Krümmungspositionen auf jeder der Schaufeln (55) von einer Schaufelnabe (55b) zu einer Schaufelspitze (55a) gleichmäßig verteilt sind.
  4. Axialstromlüfter nach Anspruch 1,
    wobei eine Schaufelspitze (55a) jeder der Schaufeln (55) von ihrer Überdruckfläche (55b) zu ihrer Unterdruckfläche (56a) gekrümmt ist und dabei einen vorgegebenen Krümmungsradius bildet.
EP20000114849 1999-07-22 2000-07-11 Axiallüfter Expired - Lifetime EP1070849B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
KR9929803 1999-07-22
KR1019990029803A KR100336132B1 (ko) 1999-07-22 1999-07-22 냉장고용 시라우드
KR9929802 1999-07-22
KR1019990029802A KR100347048B1 (ko) 1999-07-22 1999-07-22 냉장고의 냉기순환용 축류팬

Publications (3)

Publication Number Publication Date
EP1070849A2 EP1070849A2 (de) 2001-01-24
EP1070849A3 EP1070849A3 (de) 2002-07-17
EP1070849B1 true EP1070849B1 (de) 2010-03-24

Family

ID=26635904

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20000114849 Expired - Lifetime EP1070849B1 (de) 1999-07-22 2000-07-11 Axiallüfter

Country Status (3)

Country Link
EP (1) EP1070849B1 (de)
JP (1) JP3469857B2 (de)
DE (1) DE60044049D1 (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

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100347050B1 (ko) * 1999-11-02 2002-08-03 엘지전자주식회사 냉장고용 축류팬
KR100402477B1 (ko) * 2001-05-17 2003-10-22 엘지전자 주식회사 냉장고의 송풍팬 어셈블리
KR100420519B1 (ko) * 2001-08-30 2004-03-02 엘지전자 주식회사 냉장고용 복합팬
FR2833050B1 (fr) * 2001-12-03 2005-11-11 Abb Solyvent Ventec Ventilateur helicoide avec un moyen reducteur de bruit
US6911636B2 (en) * 2002-01-03 2005-06-28 Lg Electronics Inc. Cooling fan for microwave oven
DE60313147T2 (de) 2002-02-28 2007-12-13 Daikin Industries, Ltd. Lüfter
JP4745626B2 (ja) * 2004-06-29 2011-08-10 ループウイング株式会社 軸流式送風装置
JP4943817B2 (ja) * 2006-10-31 2012-05-30 日本電産サーボ株式会社 軸流ファン
US9004860B2 (en) * 2010-02-26 2015-04-14 Robert Bosch Gmbh Free-tipped axial fan assembly
JP6215296B2 (ja) * 2013-02-22 2017-10-18 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド プロペラファン及びこれを備えた空気調和機
FR3015379B1 (fr) * 2013-12-20 2017-06-09 Valeo Systemes Thermiques Ventilateur pour automobile comportant un stator en amont de l'helice
CN204213047U (zh) * 2014-10-24 2015-03-18 常州格力博有限公司 轴流吹风机风叶
FR3032494B1 (fr) * 2015-02-06 2018-05-25 Safran Aircraft Engines Aube de soufflante
CN114810661A (zh) * 2015-12-11 2022-07-29 台达电子工业股份有限公司 叶轮及风扇
JP2019056309A (ja) * 2017-09-20 2019-04-11 ミネベアミツミ株式会社 軸流ファン

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT8353039V0 (it) * 1982-03-15 1983-03-10 Sueddeutsche Kuehler Behr Ventilatore assiale particolarmente per radiatori di raffreddamento di motori termici raffreddati ad acqua
EP0174487A1 (de) 1984-08-16 1986-03-19 Siemens Aktiengesellschaft Axialventilator
IT206701Z2 (it) 1985-08-02 1987-10-01 Gate Spa Ventilatore assiale particolarmente per autoveicoli
US5244347A (en) * 1991-10-11 1993-09-14 Siemens Automotive Limited High efficiency, low noise, axial flow fan
US5273400A (en) 1992-02-18 1993-12-28 Carrier Corporation Axial flow fan and fan orifice
EP0569863B1 (de) * 1992-05-15 2000-03-29 Siemens Canada Limited Flacher Axiallüfter
US5393199A (en) 1992-07-22 1995-02-28 Valeo Thermique Moteur Fan having a blade structure for reducing noise
DE19631093A1 (de) 1996-08-01 1998-02-05 Deutsche Forsch Luft Raumfahrt Verfahren zur aeroakustischen Optimierung eines Axiallüfters

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

Also Published As

Publication number Publication date
EP1070849A2 (de) 2001-01-24
JP3469857B2 (ja) 2003-11-25
EP1070849A3 (de) 2002-07-17
JP2001059499A (ja) 2001-03-06
DE60044049D1 (de) 2010-05-06

Similar Documents

Publication Publication Date Title
EP1070849B1 (de) Axiallüfter
US11506211B2 (en) Counter-rotating fan
KR100818407B1 (ko) 고효율의 유입 적응형 축류팬
AU2003207098B2 (en) Fan
JP5525429B2 (ja) 二重反転式軸流送風機
US6935835B2 (en) Anti-noise and anti-vortex stabilizer
EP0601119A1 (de) Ventilator mit vorwärtsgekrümmten schaufeln und angepasster schaufelkrümmung und -anstellung
US7186080B2 (en) Fan inlet and housing for a centrifugal blower whose impeller has forward curved fan blades
AU714395B2 (en) Axial fan
JPS63124900A (ja) 軸流送風機
US6863500B2 (en) Blast fan
JP3629702B2 (ja) 送風機
JP2003232295A (ja) 遠心ファンおよびその遠心ファンを備えた加熱調理器
WO2001005652A1 (en) Centrifugal impeller with high blade camber
JP2001227498A (ja) プロペラファン
US6911636B2 (en) Cooling fan for microwave oven
CN217002382U (zh) 离心风机叶轮及应用其的离心风机、吸油烟机
KR100420519B1 (ko) 냉장고용 복합팬
CN112648201B (zh) 具有限定转子上方的腔的风扇外壳的涵道风扇
KR100789812B1 (ko) 크로스플로우 팬
KR20070035568A (ko) 원심 송풍기 및 원심 송풍기를 구비한 공기 조화 장치
KR100326997B1 (ko) 축류팬
KR20230078295A (ko) 시로코팬
KR19990011846A (ko) 공기조화기용 실외기의 송풍장치
KR20010010748A (ko) 냉장고의 냉기순환용 축류팬

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

RIC1 Information provided on ipc code assigned before grant

Free format text: 7F 04D 29/32 A, 7F 04D 29/38 B, 7F 04D 29/66 B, 7F 04D 29/54 B, 7F 04D 19/00 B

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

17P Request for examination filed

Effective date: 20020724

AKX Designation fees paid

Designated state(s): DE GB IT

17Q First examination report despatched

Effective date: 20070131

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: LG ELECTRONICS, INC.

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REF Corresponds to:

Ref document number: 60044049

Country of ref document: DE

Date of ref document: 20100506

Kind code of ref document: P

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20101228

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20150615

Year of fee payment: 16

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20150612

Year of fee payment: 16

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20150710

Year of fee payment: 16

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 60044049

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20160711

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170201

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160711

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160711