EP1070849A2 - Ventilateur axial - Google Patents

Ventilateur axial Download PDF

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Publication number
EP1070849A2
EP1070849A2 EP00114849A EP00114849A EP1070849A2 EP 1070849 A2 EP1070849 A2 EP 1070849A2 EP 00114849 A EP00114849 A EP 00114849A EP 00114849 A EP00114849 A EP 00114849A EP 1070849 A2 EP1070849 A2 EP 1070849A2
Authority
EP
European Patent Office
Prior art keywords
axial flow
flow fan
blades
hub
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.)
Granted
Application number
EP00114849A
Other languages
German (de)
English (en)
Other versions
EP1070849A3 (fr
EP1070849B1 (fr
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 KR1019990029802A external-priority patent/KR100347048B1/ko
Priority claimed from KR1019990029803A external-priority patent/KR100336132B1/ko
Application filed by LG Electronics Inc filed Critical LG Electronics Inc
Publication of EP1070849A2 publication Critical patent/EP1070849A2/fr
Publication of EP1070849A3 publication Critical patent/EP1070849A3/fr
Application granted granted Critical
Publication of EP1070849B1 publication Critical patent/EP1070849B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—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.
  • an 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 a plurality of blades regularly fixed around the hub, wherein a variety of designing factors of the blades, such as the number of blades, 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.
  • Fig. 16 is a front view, showing a shroud installed around the axial flow fan in accordance with an embodiment of the present invention.
  • Fig. 17 is a sectional view taken along the line B-B of Fig. 16, showing the construction of the shroud according to the embodiment of this invention.
  • the shroud 60 of this invention is installed around the blades 55 of the fan, with an annular rim 62 being formed closely around the blades 55 while being bulged to the front of the fan in an air inlet direction.
  • a vortex prevention means is provided on the back surface of the annular rim 62 for preventing an undesirable collision of a discharged air current against the back surface of the rim 62 in back of the blades 55, thus preventing a formation of a vortex stream.
  • the vortex prevention means of this invention comprises an annular skirt 64, which is perpendicularly mounted along the central circular line on the concave back surface of the rim 62 so as to project to a length L from the flat surface of the shroud 60 in the air discharging direction.
  • annular skirt 64 which is perpendicularly mounted along the central circular line on the concave back surface of the rim 62 so as to project to a length L from the flat surface of the shroud 60 in the air discharging direction.
  • the projection length L of the annular skirt 64 is preferably set to about 1 ⁇ 2 mm. That is, the width of the annular skirt 64 is larger than the radius of the annular rim 62 by about 1 ⁇ 2 mm.
  • the rim 62 undesirably generates a large-sized vortex, and so it may be necessary to install a plurality of annular skirts 64 on the concave back surface of the rim 62 so as to appropriately divide the space on the concave back surface into a plurality of small sections. This finally reduces the size of a vortex formed on the back surface of the annular rim 62.
  • the width of the annular skirt 64 is designed to be larger than the radius of the annular rim 62 by the projection length L, it is possible to prevent the discharged air current from an undesired collision against the concave back surface of the rim 62 and to more effectively prevent a formation of an undesired vortex on the back surface of the shroud 60.
  • Fig. 18 is a view, showing an air current formed around the shroud 60.
  • the bulged annular rim 62 formed closely around the blades 55 of the fan, guides the air to flow on its rounded front surface, thus minimizing an airflow resistance on the shroud 60.
  • the annular skirt 64 effectively prevents such discharged air from flowing into the concave back surface of the rim 62, but guides the discharged air so as to allow the air to flow in the axial direction of the fan. Therefore, the vortex prevention means of this invention effectively prevents a formation of a vortex in back of the fan while allowing a smooth circulation of discharged cool air around the fan.
  • the discharged air, flowing around the edge of the blade tips 55a regrettably moves outwardly in a radial direction of the fan and flows into the concave back surface of the rim 62 while forming a vortex.
  • the annular skirt 64, formed on the concave back surface of the rim 64 while projecting in the air discharging direction of the fan effectively prevents such discharged air from flowing into the concave back surface of the rim 62 or from a collision against the concave back surface, thus finally preventing a formation of a vortex on the back surface. Therefore, it is possible for the discharged cool air to smoothly flow in back of the fan without forming any vortex.
  • Fig. 19 is a sectional view, showing the construction of a shroud having a vortex prevention means in accordance with another embodiment of this invention.
  • the vortex prevention means comprises a vortex prevention bracket 68, which has an annular shape and is mounted to the back surface of the shroud 60 to cover the concave back surface of the circular rim 62.
  • This bracket 68 thus prevents the discharged cool air from flowing into the concave back surface of the rim 62.
  • the vortex prevention bracket 68 consists of an angled portion 70 mounted to the back surface of the flat portion of the shroud 60.
  • a slope portion 72 integrally and inclinedly extends from the edge of the angled portion 70 so as to cover the concave back surface of the rim 62 prior to being mounted to the inside edge of the rim 62.
  • the slope portion 72 of the bracket 68 thus almost completely prevents discharged cool air from flowing into the concave back surface of the rim 62.
  • the vortex prevention bracket 68 of this embodiment almost completely covers the concave back surface of the circular rim 62, it almost completely prevents discharged cool air from flowing into the concave back surface of the rim 62 and prevents a formation of a vortex around said concave back surface. This finally minimizes the airflow resistance of the axial flow fan.
  • the vortex prevention means of this embodiment effectively prevents such discharged air from flowing into the concave back surface of the rim 62 or from a collision against the concave back surface. This finally prevents a formation of a vortex on the back surface of the rim 62 and minimizes airflow resistance of the axial flow fan.
  • Fig. 20 is a graph showing operational noise of the axial flow fan with the shroud according to the invention as a function of air volume.
  • the curve P is of an axial flow fan with a conventional shroud, and expresses that the fan generates some upsetting operational noise of 23.6dB in the case of an air volume of 0.81 CMM.
  • the curve Q is of an axial flow fan with the shroud according to the embodiment of Fig. 18 of this invention, and expresses that the fan generates some agreeable operational noise of 22.4dB in the case of an air volume of 0.81 CMM.
  • the curve R is of an axial flow fan with the shroud according to the embodiment of Fig 19 of this invention, and expresses that the fan generates more agreeable operational noise of 21.3dB in the case of an air volume of 0.81 CMM.
  • 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Cold Air Circulating Systems And Constructional Details In Refrigerators (AREA)
EP20000114849 1999-07-22 2000-07-11 Ventilateur axial Expired - Lifetime EP1070849B1 (fr)

Applications Claiming Priority (4)

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

Publications (3)

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

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP20000114849 Expired - Lifetime EP1070849B1 (fr) 1999-07-22 2000-07-11 Ventilateur axial

Country Status (3)

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EP (1) EP1070849B1 (fr)
JP (1) JP3469857B2 (fr)
DE (1) DE60044049D1 (fr)

Cited By (9)

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EP1316731A1 (fr) * 2001-12-03 2003-06-04 Fläkt Solyvent-Ventec Ventilateur helicoide avec un moyen réducteur de bruit
EP1326482A2 (fr) * 2002-01-03 2003-07-09 Lg Electronics Inc. Ventilateur de refroidissement pour four à micro-ondes
AU2003207098B2 (en) * 2002-02-28 2004-12-23 Daikin Industries, Ltd. Fan
US7946824B2 (en) 2006-10-31 2011-05-24 Nidec Servo Co., Ltd. Electric axial flow fan
EP2886384A1 (fr) * 2013-12-20 2015-06-24 Valeo Systemes Thermiques Ventilateur pour automobile comportant un stator
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
US20170218972A1 (en) * 2014-10-24 2017-08-03 Changzhou Globe Co., Ltd. Axial-flow air blower fan blades
EP3253970B1 (fr) * 2015-02-06 2020-04-29 Safran Aircraft Engines Aube de soufflante
CN111425459A (zh) * 2020-05-25 2020-07-17 佛山市南海九洲普惠风机有限公司 一种0.5毂比的轴流式风机

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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
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
KR101833559B1 (ko) * 2010-02-26 2018-02-28 로베르트 보쉬 게엠베하 프리팁형 축류팬 조립체
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
US11965522B2 (en) 2015-12-11 2024-04-23 Delta Electronics, Inc. Impeller
JP2019056309A (ja) * 2017-09-20 2019-04-11 ミネベアミツミ株式会社 軸流ファン

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EP0174487A1 (fr) 1984-08-16 1986-03-19 Siemens Aktiengesellschaft Ventilateur axial
DE8525674U1 (de) 1985-08-02 1985-11-21 Gate S.p.A., Asti Axialventilator, vornehmlich für Kraftfahrzeuge
EP0557239A2 (fr) 1992-02-18 1993-08-25 Carrier Corporation Ventilateur axial et orifice
EP0913584A1 (fr) 1992-05-15 1999-05-06 Siemens Canada Limited Ventilateur axial
EP0583091A2 (fr) 1992-07-22 1994-02-16 Valeo Thermique Moteur Ventilateur
DE19631093A1 (de) 1996-08-01 1998-02-05 Deutsche Forsch Luft Raumfahrt Verfahren zur aeroakustischen Optimierung eines Axiallüfters

Cited By (15)

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EP1316731A1 (fr) * 2001-12-03 2003-06-04 Fläkt Solyvent-Ventec Ventilateur helicoide avec un moyen réducteur de bruit
FR2833050A1 (fr) * 2001-12-03 2003-06-06 Abb Solyvent Ventec Ventilateur helicoide avec un moyen reducteur de bruit
EP1326482A2 (fr) * 2002-01-03 2003-07-09 Lg Electronics Inc. Ventilateur de refroidissement pour four à micro-ondes
EP1326482A3 (fr) * 2002-01-03 2003-08-13 Lg Electronics Inc. Ventilateur de refroidissement pour four à micro-ondes
AU2003207098B2 (en) * 2002-02-28 2004-12-23 Daikin Industries, Ltd. Fan
US6994523B2 (en) 2002-02-28 2006-02-07 Daikin Industries Ltd. Air blower apparatus having blades with outer peripheral bends
US7946824B2 (en) 2006-10-31 2011-05-24 Nidec Servo Co., Ltd. Electric axial flow fan
CN101173676B (zh) * 2006-10-31 2012-05-23 日本电产伺服有限公司 电气轴流式风扇
EP2886384A1 (fr) * 2013-12-20 2015-06-24 Valeo Systemes Thermiques Ventilateur pour automobile comportant un stator
FR3015379A1 (fr) * 2013-12-20 2015-06-26 Valeo Systemes Thermiques Ventilateur pour automobile comportant un stator en amont de l'helice
CN104763649A (zh) * 2013-12-20 2015-07-08 法雷奥热系统公司 用于机动车辆的包括定子的风扇
US20170218972A1 (en) * 2014-10-24 2017-08-03 Changzhou Globe Co., Ltd. Axial-flow air blower fan blades
EP3253970B1 (fr) * 2015-02-06 2020-04-29 Safran Aircraft Engines Aube de soufflante
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
CN111425459A (zh) * 2020-05-25 2020-07-17 佛山市南海九洲普惠风机有限公司 一种0.5毂比的轴流式风机

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DE60044049D1 (de) 2010-05-06
EP1070849A3 (fr) 2002-07-17
JP2001059499A (ja) 2001-03-06
JP3469857B2 (ja) 2003-11-25
EP1070849B1 (fr) 2010-03-24

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