EP1512918B1 - Axiallüftereinheit - Google Patents

Axiallüftereinheit Download PDF

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Publication number
EP1512918B1
EP1512918B1 EP04077405A EP04077405A EP1512918B1 EP 1512918 B1 EP1512918 B1 EP 1512918B1 EP 04077405 A EP04077405 A EP 04077405A EP 04077405 A EP04077405 A EP 04077405A EP 1512918 B1 EP1512918 B1 EP 1512918B1
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EP
European Patent Office
Prior art keywords
axial flow
flow fan
blade
hub
blades
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 - Fee Related
Application number
EP04077405A
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English (en)
French (fr)
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EP1512918A2 (de
EP1512918A3 (de
Inventor
Won Chin Sim
Kee Chung Moon
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LG Electronics Inc
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LG Electronics Inc
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Filing date
Publication date
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Publication of EP1512918A2 publication Critical patent/EP1512918A2/de
Publication of EP1512918A3 publication Critical patent/EP1512918A3/de
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Publication of EP1512918B1 publication Critical patent/EP1512918B1/de
Expired - Fee Related legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/38—Fan details of outdoor units, e.g. bell-mouth shaped inlets or fan mountings
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F7/00—Ventilation
    • F24F7/007—Ventilation with forced flow

Definitions

  • the present invention relates to an axial flow fan of an air conditioner.
  • An axial flow fan according to the preamble of claim 1 is indicated in US 6,447,251 B1 .
  • an air conditioner is mounted therein with a refrigerating cycle s ystem composed of a compressor, a condenser, a capillary tube, an evaporator and a heat exchanger.
  • the air conditioner is an apparatus for properly sending cold air formed at t he evaporator or warm air generated at the condenser according to an indoor condition, a nd thus convincingly maintaining indoor atmosphere.
  • the air conditioner may be divided into a window type air conditioner wher e the refrigerating cycle system is mounted in a single body, a spilt type air conditioner w here an indoor unit and an outdoor unit are separated and installed indoors and outdoors r espectively, and so forth.
  • the spilt type air conditioner is again divided, acc ording to an installation method, into a wall-mounted type, a permanent-mounted type (in cluding a package air conditioner), a ceiling-mounted type, a ceiling-embedded type and so on.
  • the indoor unit of the spilt type air conditioner may has a structure ca pable of alternatively using the wall-mounted type and the permanent-mounted type and being simultaneously applied as the ceiling-mounted type according to need of a user, wh ich is referred to as a convertible type indoor unit.
  • Fig. 1 schematically shows a general air conditioner.
  • the conventional air conditioner is composed of an outd oor unit 20 which is disposed outdoors and exchanges heat with outdoor air, an indoor un it 10 which is disposed indoors and conditions indoor air, and a connecting line 30 which connects the outdoor unit and the indoor unit with each other.
  • the outdoor unit 20 is a means for converting a gas refr igerant of low temperature and low pressure, which is inputted from the indoor unit 10 by exchanging heat with the outdoor air, into a liquid refrigerant of low temperature and lo w pressure, and is composed of a compressor 11, a condenser 12 and an expansion valve 13.
  • the compressor 11 is a component for converting the gas refrigeran t of low temperature and low pressure, which is inputted from the indoor unit 10, into the gas refrigerant of high temperature and high pressure
  • the condenser 12 is a compone nt for converting the gas refrigerant of high temperature and high pressure into a liquid re frigerant of middle temperature and high pressure
  • the expansion valve 13 is a compo nent for converting the liquid refrigerant of middle temperature and high pressure into the liquid refrigerant of low temperature and low pressure.
  • the condenser 12 is a component for directly exchanging the heat wit h the outdoor air, and has a separate fan for introducing the outdoor air.
  • the indoor unit 10 lowers an indoor temperature by means of e vaporation, which occurs when the liquid refrigerant of low temperature and low pressure introduced from the outdoor unit 20 is converted into the gas refrigerant of low temperat ure and low pressure.
  • the indoor unit 10 is composed of an evaporator 21 and a fan 21a, wherein the evaporator 21 converts the liquid refrigerant of low temperature and low pressure into the gas refrigerant of low temperature and low pressure.
  • the connecting line 30 is a co mponent for connecting the indoor unit 10 and the outdoor unit 20 to circulate the refriger ant, and is properly disposed according to a distance between the outdoor unit 10 and the indoor unit 10.
  • the outdoor unit 20 of the split-type air conditioner inclu des the compressor, the condenser, a cooling fan (hereinafter, referred to as "axial flow fa n") which usually generate many noises, and a driving motor for rotating the axial flow fa n.
  • the indoor unit 10 includes the evaporator 21 and the blow fan 21 a, and performs ref rigeration and circulation of the indoor air.
  • Fig. 2 is a perspective view illustrating a general split type air conditioner.
  • the indoor unit 10 and the outdoor unit 20 are connecte d to each other by the connecting line 30.
  • the axial flow fan 40 has a hub 42 couple d to a rotational shaft of the driving motor (not shown), and a plurality of blades 44 forme d on an outer circumferential surface of the hub 42, wherein the hub 42 is integrally form ed with the blades 44.
  • This pressure difference generates a suction force capable of sucking up the air, thus sucking up the outdoor air toward the outdoor unit 20 through the suction.
  • the outdoor air passes through the condenser 12 provided on an intake side of the outd oor unit.
  • the outdoor air exchanges the heat with the gas refrigerant flowin g through the condenser to condense the gas refrigerant into a liquid state, and then flows out outside the outdoor unit 20 through ventilation of the axial flow fan 40.
  • characteristic factors determining a ventilation characteristic of the a xial flow fan 40 are divided into two types: general factors such as the number of th e blades 44, a (outer) diameter D of the axial flow fan, a (outer) diameter d of the hub and so forth, and so-called blade factors such as a pitch angle ⁇ , a peak point of the camber P, a maximum quantity of the camber MC, a length of a chord, a sweep angle ⁇ and so fo rth at the blade, which will be described below with reference to Figs. 3A and 3B .
  • the pitch angle ⁇ of the blade is an angle between a flow dir ection of the fluid or the air (x-axis in the figure) and a straight line, namely a chord, runn ing from a leading edge (L.E) of the blade 44 and its trailing edge (T.E).
  • the quantity of the camber refers to a length joining the camber (a cen tral line across a cross section of the blade) and the chord.
  • the maximum point of the c amber quantity i.e., the maximum quantity of the camber MC, as in Fig. 3B , refers to the camber quantity between the L.E. of the blade 44 and the camber peak point P on the cho rd C running from the L.E to the T.E.
  • the sweep angle ⁇ refers to an angle between two lines that intersect, one o f which is one which connects the center of an inner end of the blade 44 or the center of a portion where the blade 44 comes into contact with the hub 42 but goes with a curvature of the blade 44, and the other is one (Y axis in the figure) which passes through the cent er (point) of the inner end of the blade 44 and the center (point) of the hub 42.
  • the sweep angle ⁇ is a factor determining a noise of an airflow o f the axial flow fan 40.
  • the sweep angle ⁇ is great, a phase difference of the airflo w between the hub 42 and a tip of the blade 44 becomes great.
  • the sw eep angle ⁇ is great, the phase difference of the airflow becomes small.
  • the phase difference of the airflow causes a phase difference between a noi se generated at the outer end of the blade 44 and a noise generated at the inner end of the blade 44.
  • the greater this noise phase difference is, the lower a frequency of the airflow passing through the blade 44 becomes. Hence, the noise becomes lower.
  • the number of the blades 44 is an important factor determining the airf low noise generated when the axial flow fan 40 is operated.
  • this conventional axial flow fan 40 is disclosed in Korean Patent Publication No. 2003-14960 , titled AXIAL FLOW FAN OF OUTDOOR UNIT OF AIR CONDITIONER, previously filed by the present applicant and published as of Febru ary 20, 2003.
  • the disclosed axial flow fan of the outdoor unit of the air condition er includes a hub 42 connected with a rotational shaft of a motor and a plurality of blad es 44 integrally formed on an outer circumferential surface of the hub, wherein the numb er of the blades 44 is set to three, a whole outer diameter of the fan is set to 340 ⁇ 2mm, a nd a diameter of the hub 42 is set to 100 ⁇ 2mm.
  • each blade 44 is configured so that the pitch angle ⁇ is linearly chan ged from the hub 42 to the end thereof in a range between 20 degrees and 37 degrees.
  • Each blade 44 is also configured so that the peak point of the camber P is fo rmed at a point corresponding to 70% of the chord length in a direction from the L.E ther eof to the T.E thereof, and that the maximum quantity of the camber MC is set to 0.5% w ithin each radius from the hub 42 to the end of the blade 44.
  • each blade 44 has a range between 47 degrees and 49 degrees when a dimensionless radius coordinate is less than 0.3 and is linearly in creased when the dimensionless radius coordinate exceeds 0.3 to have a range between 5 5 degrees and 57 degrees at the end of the blade.
  • the dimensionless radius coordinate is a factor for taking into consideration of performance of the axial flow fan only by the blades 44 except for the h ub 42, and is determined between 0 and 1 when a position where the blades and the hub c ome into contact with each other is set to 0, and the end of each blade 44 is set to 1.
  • a pressure coefficient and co nstant pressure efficiency are enhanced as compared to another conventional axial flow fa n having four blades.
  • the motor for the axial flow fan having three blades ca n be also enhanced in operation efficiency at an operation point, and can be driven with a size smaller than that for another conventional axial flow fan having four blades.
  • the motor for the axial flow fan having three blades is reduced by about 22% in con sumption electrical power required for operation.
  • an objective of the present invention is to design an axial flow fa n within an optimal design range capable of suppressing increase in intensity of a turbule nt flow generated from a surface of each blade, increase in thickness of a boundary layer on the surface of each blade and disturbance of an airflow within a region of the hub.
  • the present invention provides an axial flo w fan according to claim 1.
  • the axial flow fan can reduc e the noise as low as possible and increase the pressure coefficient and the constant press ure efficiency compared to the conventional axial flow fan.
  • Fig. 1 schematically shows a general air conditioner
  • Fig. 2 is a perspective view illustrating a general split type air conditioner
  • Figs. 3A and 3B are front and side views of a conventional axial flow fan, r espectively;
  • Fig. 4 is a graph showing comparison of relation between a pressure coeffic ient and a flow rate coefficient in a conventional axial flow fan with that of another conve ntional axial flow fan;
  • Fig. 5 is a graph showing comparison of relation between constant pressure efficiency and a flow rate coefficient in a conventional axial flow fan with that of another conventional axial flow fan;
  • Figs. 6A and 6B are front and side views of an axial flow fan according to t he present invention, respectively;
  • Figs. 7A and 7B show a state where blades are tilted on an outer circumfere ntial surface of a hub at a certain rake angle in axial flow fans according to the prior art and the present invention
  • Fig. 8 is a graph showing a state where a noise is changed according to a ch ange of a solidity with respect to axial flow fans of the prior art and the present invention
  • Fig. 9 is a graph showing a state where a noise is changed according to a ch ange of a quantity of a camber with respect to axial flow fans of the prior art and the pres ent invention
  • Fig. 10 is graph showing relation between a (constant) pressure coefficient, a constant pressure efficiency and a flow rate coefficient with respect to axial flow fans o f the prior art and the present invention.
  • Fig. 11 is a graph showing comparison of a state where a noise is changed a ccording to a change of a frequency of an axial flow fan of the present invention with that of an axial flow fan of the prior art.
  • Figs. 6A and 6B are front and side views of an axial flow fan according to t he present invention, respectively.
  • Figs. 7A and 7B show a state where blades are tilted on an outer circumferential surface of a hub at a certain rake angle in axial flow fans acco rding to the prior art and the present invention.
  • An axial flow fan 140 of an outdoor unit of an air conditioner according to t he present invention is composed of a hub 142 connected with a rotational shaft 141 of a motor, and a plurality of blades 144 integrally formed on an outer circumferential surface of the hub 142.
  • the axial flow fan 140 is configured so that the number of the blades is two , that a ratio of an inner diameter to an outer diameter (i.e. a ratio of the outer diameter of the hub and the outer diameter of the fan) is between about 0.35 and about 0.4, that a soli dity, a ratio of the whole area of the fan 140 and an area of the blades, has a range of 0.85 ⁇ 0.05, and that a quantity of a camber of the hub 142 has a range of 5.0% ⁇ 1.0%.
  • a slip stream or wake co mponent may be generated at a leading edge (L.E) and a trailing edge (T.E) of the leading blade 144, and a turbulent flow component may be generated by separation on a negativ e pressure surface.
  • L.E leading edge
  • T.E trailing edge
  • a turbulent flow component may be generated by separation on a negativ e pressure surface.
  • the present invention is to suppress increase in intensity of the turb ulent flow generated from a surface of each blade 144, increase in thickness of a boundar y layer on the surface of each blade 144, and disturbance of an ariflow within a region of the hub 142.
  • the axial flow fan 140 is formed so th at the number of the blades 144 is two, that the ratio of the inner diameter to the outer dia meter ( i . e . the ratio of the outer diameter of the hub and the outer diameter of the axial flo w fan) is between about 0.35 and about 0.4, that the solidity, the ratio of the whole area of the fan 140 and the area of the blades, has the range of 0.85 ⁇ 0.05, and that the camber q uantity of the hub 142 has the range of 5.0% ⁇ 1.0%.
  • the detailed co nfiguration of the present invention is as follows.
  • the axial flow fan 140 of the outdoor unit of the air conditioner according t o the present invention is composed of the hub 142 connected with the rotational shaft 141 of the motor, and the plurality of blades 144 integrally formed on the outer circumferential surface of the hub 142.
  • the number of the blades 144 is set to two.
  • the inner and outer dia meter ratio of the axial flow fan 140 i . e . the ratio of the outer diameter of the hub 142 an d the outer diameter of the axial flow fan 140, is set to a range between about 0.35 and ab out 0.40.
  • the ratio of the whole area of the axial flow fan 140 and the area of the blades i.e. the solidity
  • the camber quantity of the hu b 142 has the range of 5.0% ⁇ 1.0%.
  • the solidity can be expressed by the following form ula.
  • a value of the solidity presented in the present invention may become a mean value from the hub and a tip, for example, an integral value.
  • a rake base line of each blade 144 formed on the outer circumferential surface of the hub 142 is tilted from that formed horizontal to the outer circumferential surface of the conventional hub 42 by a rake angle between about 20 degrees and about 23 degrees.
  • the rake angle refers to an angle determining how much to tilt and form the blades 144 on the circumferential surface of the hub 142.
  • a part from the outer circumferential surface of the hub 142 to a pred etermined portion of each blade 144 is tilted at the rake angle, and the other part from the predetermined portion of each blade 144 and the tip of each blade 144 is provided with a bulge 146 protruded toward a pressure surface.
  • each blade 144 has the same angle as the rake angle from the outer circumferential surface of the hub 142 to the predet ermined portion of each blade 144. In this manner, a profile of the axial flow fan 140 is formed as a whole.
  • the first section performs rotat ional displacement at the identical angle
  • the second section forms a non-linear angle raised toward the pressure surface.
  • the tip i.e. a section except for the two sections
  • the tip is adapted to apply an identical value of the first section.
  • the outer diameter D of the axial flow fan is 460 ⁇ 2mm, and th e outer diameter d of the hub 142 is 170 ⁇ 2mm.
  • a pitch angle, a peak point of a camber, and a sweep angle of each bla de 144 are the same as the pitch angle ⁇ , the peak point of the camber P, the maximum qu antity of the camber MC, and the sweep angle ⁇ of the conventional blade 44 shown in Fi gs. 3A and 3B.
  • the pitch angle, the peak point of the camber, and the sweep angle of each blade 144 will be described in detail below.
  • each blade 144 is configured to be linearly changed fro m the hub 142 to the end of the blade 144 within a range between 37 degrees and 20 degr ees.
  • Each blade 144 is configured so that the peak point of the camber P is form ed at a position corresponding to 70% of a length of a chord in a direction from the front end of the blade to the rear end of the blade, and that that the maximum quantity of the ca mber MC is kept constant at a value of 0.5% within each radius from the hub 142 to the e nd of the blade 144.
  • each blade 144 has a range between abo ut 47 degrees and about 49 degrees when a dimensionless radius coordinate is less than 0. 3 and is linearly increased when the dimensionless radius coordinate exceeds 0.3 to have a range between about 55 degrees and about 57 degrees at the end of the blade.
  • Fig. 8 is a graph showing a state where a noise is changed according to a ch ange of a solidity with respect to axial flow fans of the prior art and the present invention.
  • Fig. 9 is a graph showing a state where a noise is changed according to a change of a q uantity of a camber with respect to axial flow fans of the prior art and the present inventio n.
  • Fig. 10 is graph showing relation between a (constant) pressure coefficient, a constan t pressure efficiency and a flow rate coefficient with respect to axial flow fans of the prior art and the present invention.
  • Fig. 11 is a graph showing comparison of a state where a noise is changed according to a change of a frequency of an axial flow fan of the present invention with that of an axial flow fan of the prior art.
  • the solidity applie d to the present invention has a range of 0.85 ⁇ 0.05 and the camber quantity of the hub ha s a range of 5.0% ⁇ 1.0%.
  • an upper line shows a comparison of relation of the (constant) pressure coefficient and the flow rate coefficient in the axial flow fan 140 with that of the conventional axial flow fan 40
  • a lower line shows a comparison of relati on of the constant pressure efficiency and the flow rate coefficient in the axial flow fan 1 40 with that of the conventional axial flow fan 40.
  • the noise cha nge was measured depending on the change of the solidity as the ratio of the whole area o f the fan 140 to the area of the blades. It was found that as a result of the measurement, as shown in Fig. 8 , when the ratio of the whole area of the fan 140 to the area of the blades, i.e. the solidity, was about 0.87, the noise was the lowest. Further, the noise change wa s measured depending on the change of the camber quantity of each blade of the axial flo w fan 140. It was found that as a result of the measurement, as shown in Fig. 9 , when th e camber quantity of the blade 144 was about 0.5%, the noise was lowest.
  • the pressure coefficient and the constant pressure efficiency were e enhanced over the conventional axial flow fan 40, and that the operation efficiency was also enhanced at the operation point according to the enhancement of the pressure coeffic ient and the constant pressure efficiency of the axial flow fan 140 as set forth above.
  • Fig. 11 is a graph showing comparison of a state where a noise is c hanged according to a change of a frequency of an axial flow fan of the present invention with that of an axial flow fan of the prior art.
  • w hen having an air volume equal to that of the conventional axial flow fan 40
  • the axial flo w fan 140 was subjected to great reduction of the noise in a range between about 300 Hz and about 1000Hz.
  • the present invention relates to the axial flow fan config ured so that the number of the blades is two, that a predetermined rake angle is kept const ant in the part from the hub to the predetermined portion of the blade among the whole pa rt from the hub to the outer end of the blade and is increased in the pressure surface direct ion in the other part from the predetermined portion of the blade to the the outer end of th e blade, and the ratio of the inner diameter to the outer diameter is between about 0.35 an d about 0.4.
  • the axial flow fan of the present invention is designed within an optimal design range (that the solidity, the ratio of the whole area of the axial flow fan an d the area of the blades, is about 0.87 and that the camber quantity of the hub is about 5.0 %), for example, capable of suppressing increase in intensity of the turbulent flow genera ted from the surface of each blade, increase in thickness of the boundary layer on the surf ace of each blade and disturbance of the airflow within the region of the hub.
  • the axial flow fan of the present invention can reduce the noise as low as possible and i ncrease the pressure coefficient and the constant pressure efficiency compared to the con ventional axial flow fan.
  • the axial flow fan of the present invention can remarkably reduce t he noise within the predetermined frequency range (e.g. between about 300 Hz and about 1000 Hz) with respect to the same air volume as the conventional axial flow fan.
  • the predetermined frequency range e.g. between about 300 Hz and about 1000 Hz
  • the axial flow fan of the present invention may be applied to a refrigerator or other apparatuses for condensing and evaporating a refrigerant.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (5)

  1. Axiallüfter (140), umfassend:
    eine Nabe (142), die mit einer Rotationswelle (141) eines Motors verbunden ist; und
    zumindest ein Blatt (144), das die Nabe (142) kontaktiert,
    wobei das Blatt (144) einen Teil von der Nabe (142) zu einem Vorbestimmten Abschnitt des Blatts (144), als Teil eines Gesamtteils von der Nabe (142) zu einem äußeren Ende des Blatts (144), und den anderen Teil von dem Vorbestimmten Abschnitt des Blatts (144) zu dem äußeren Ende des Blatts (144) aufweist, wobei der Teil gleichmäßig in einem Vorbestimmten Einsteckwinkel aufgebracht ist und der andere Teil in einer Richtung einer Druckoberfläche des Blatts (144) angehoben ist, dadurch gekennzeichnet, dass
    die äußere Kante denselben Winkel wie den Einsteckwinkel aufweist;
    eine Einsteckgrundlinie des Blatts (144) an einer äußeren Umfangsoberfläche der Nabe (142) und innerhalb des Teils von der Nabe (142) zu dem Vorbestimmten Abschnitt ausgebildet ist, um den Einsteckwinkel zwischen etwa 20 Grad und etwa 23 Grad gekippt ist;
    und dass ein Verhältnis eines Innendurchmessers und eines Außendurchmessers des Axiallüfters (140), welches das Verhältnis des Außendurchmessers der Nabe (142) und des Außendurchmessers des Axiallüfters (140) ist, zwischen 0,35 und etwa 0,4 liegt.
  2. Axiallüfter (140) nach Anspruch 1, wobei die Anzahl der Blätter zwei ist.
  3. Axiallüfter (140) nach Anspruch 1, wobei ein Bedeckungsgrad einen Bereich von 0,85 ± 0,05 aufweist.
  4. Axiallüfter (140) nach Anspruch 1, wobei der Außendurchmesser des Axiallüfters (140) in einem Bereich von 460 ± 2 mm liegt.
  5. Axiallüfter (140) nach Anspruch 1, wobei die Nabe (142) einen Durchmesser in einem Bereich von 170 ± 2 mm hat.
EP04077405A 2003-09-05 2004-08-25 Axiallüftereinheit Expired - Fee Related EP1512918B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR2003062005 2003-09-05
KR1020030062005A KR100547328B1 (ko) 2003-09-05 2003-09-05 에어컨 실외기의 축류팬

Publications (3)

Publication Number Publication Date
EP1512918A2 EP1512918A2 (de) 2005-03-09
EP1512918A3 EP1512918A3 (de) 2010-03-24
EP1512918B1 true EP1512918B1 (de) 2011-10-26

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Country Status (5)

Country Link
US (1) US20050053493A1 (de)
EP (1) EP1512918B1 (de)
JP (1) JP2005083386A (de)
KR (1) KR100547328B1 (de)
CN (2) CN1982729A (de)

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KR100547328B1 (ko) 2006-01-26
EP1512918A2 (de) 2005-03-09
KR20050024158A (ko) 2005-03-10
US20050053493A1 (en) 2005-03-10
EP1512918A3 (de) 2010-03-24
JP2005083386A (ja) 2005-03-31
CN1982729A (zh) 2007-06-20
CN1590779A (zh) 2005-03-09
CN100339601C (zh) 2007-09-26

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