US20090038333A1 - Turbo fan for blowing and refrigerator having the same - Google Patents

Turbo fan for blowing and refrigerator having the same Download PDF

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Publication number
US20090038333A1
US20090038333A1 US12/280,879 US28087906A US2009038333A1 US 20090038333 A1 US20090038333 A1 US 20090038333A1 US 28087906 A US28087906 A US 28087906A US 2009038333 A1 US2009038333 A1 US 2009038333A1
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United States
Prior art keywords
blade
fan
turbofan
blowing
diameter
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Abandoned
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US12/280,879
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English (en)
Inventor
Jun-Ho Bae
Chang-joon Kim
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LG Electronics Inc
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LG Electronics Inc
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Assigned to LG ELECTRONICS INC. reassignment LG ELECTRONICS INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BAE, JUN-HO
Assigned to LG ELECTRONICS INC. reassignment LG ELECTRONICS INC. CORRECTIVE COVER SHEET TO ADD ASSIGNOR CHANG-JOON KIM ON THE LIST OF ASSIGNORS PREVIOUSLY RECORDED ON REEL/FRAME 021449/0194. Assignors: BAE, JUN-HO, KIM, CHANG-JOON
Publication of US20090038333A1 publication Critical patent/US20090038333A1/en
Abandoned legal-status Critical Current

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Classifications

    • 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
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
    • F25D17/06—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation
    • 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
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
    • 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
    • F25D2317/0683—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 the fans not of the axial type

Definitions

  • the present invention relates to a turbofan for blowing and a refrigerator having the same, and more particularly, to a turbofan for blowing capable of improving a blowing efficiency for cool air and minimizing power consumption and noise, and a refrigerator having the same.
  • a refrigerator serves to store foodstuffs as a freezing state or a refrigerating state by circulating cool air generated by a refrigerating cycle.
  • the conventional refrigerator comprises a body 10 having a freezing chamber 1 and a refrigerating chamber 2 , and a door 3 disposed at a front surface of the body 10 for opening and closing the freezing chamber 1 and the refrigerating chamber 2 .
  • a turbofan 9 for forcibly blowing air cooled through an evaporator 7 into the freezing chamber 1 is installed at a rear side of the body 10 .
  • a shroud 8 for introducing air blown by the turbofan 9 into the freezing chamber 1 is mounted at one side of the turbofan 9 .
  • Air cooled by the evaporator 7 is introduced into the freezing chamber 1 by the turbofan 9 , and then is circulated, thereby cooling foodstuffs stored in the freezing chamber 1 and the refrigerating chamber 2 .
  • turbofan 9 Even if the turbofan 9 maintains an inner temperature of the refrigerater, it causes noise.
  • turbofan 9 it is required to design the turbofan 9 so as to reduce noise and power consumption and to improve a blowing efficiency for cool air.
  • turbofan for blowing capable of improving a blowing efficiency for cool air and minimizing power consumption and noise, and a refrigerator having the same.
  • a turbofan for blowing comprising: a base plate having a hub protruding from a center thereof; a plurality of blades disposed on an outer circumerential surface of the base plate with a constant interval therebetween in a circumferential direction; and a shroud connected to the blades in opposition to the base plate, wherein a height of the blade is 16% ⁇ 26% of an outer diameter of the fan, in which the height of the blade denotes a gap between the base plate and the shroud, and the outer diameter of the fan denotes a diameter of a circle that is obtained by connecting outer ends of the respective blades.
  • An inner diameter of the shroud is 72 % ⁇ 85% of the outer diameter of the fan.
  • An inner diameter of the blade is 55 % ⁇ 62% of the outer diameter of the fan, in which the inner diameter of the blade denotes a diameter of a circle that is obtained by connecting inner ends of the respective blades.
  • a refrigerator having a turbofan for blowing, the turbofan comprising: a base plate having a hub protruding from a center thereof; a plurality of blades disposed on an outer circumerential surface of the base plate with a constant interval therebetween in a circumferential direction; and a shroud connected to the blades in opposition to the base plate, wherein a height of the blade is 16% ⁇ 26% of an outer diameter of a fan, in which the height of the blade denotes a gap between the base plate and the shroud, and the outer diameter of the fan denotes a diameter of a circle that is obtained by connecting outer ends of the respective blades.
  • an inner diameter of the shroud is 72% ⁇ 85% of the outer diameter of the fan.
  • an inner diameter of the blade is 55% ⁇ 62% of the outer diameter of the fan, in which the inner diameter of the blade denotes a diameter of a circle that is obtained by connecting inner ends of the respective blades.
  • FIG. 1 is a perspective view showing a refrigerator in accordance with the conventional art
  • FIG. 2 is a sectional view showing a side of the refrigerator in accordance with the conventional art
  • FIG. 3 is a perspective view showing a turbofan for blowing according to the present invention.
  • FIG. 4 is a planar view showing the turbofan for blowing according to the present invention.
  • FIG. 5 is a lateral view showing a turbofan for blowing according to the present invention.
  • FIG. 6 is a graph showing power consumption according to a ratio between a height of a blade and an outer diameter of a fan (H/Do);
  • FIG. 7 is a graph showing noise according to the ratio between a height of a blade and an outer diameter of a fan (H/Do);
  • FIG. 8 is a graph showing power consumption according to a ratio between an inner diameter of a shroud and an outer diameter of a fan (Ds/Do);
  • FIG. 9 is a graph showing noise according to the ratio between an inner diameter of a shroud and an outer diameter of a fan (Ds/Do);
  • FIG. 10 is a graph showing power consumption according to a ratio between an inner diameter of a blade and an outer diameter of a fan (Di/Do);
  • FIG. 11 is a graph showing noise according to the ratio between an inner diameter of a blade and an outer diameter of a fan (Di/Do);
  • FIG. 12 is a graph showing power consumption according to an entrance angle of a blade (B 1 );
  • FIG. 13 is a graph showing noise according to the entrance angle of a blade (B 1 );
  • FIG. 14 is a graph showing power consumption according to an exit angle of a blade (B 2 );
  • FIG. 15 is a graph showing noise according to the exit angle of a blade (B 2 );
  • FIG. 16 is a graph showing power consumption according to an outer diameter of a fan (Do);
  • FIG. 17 is a graph showing noise according to an outer diameter of a fan (Do).
  • FIG. 18 is a graph comparing power consumption according to a fluid amount of the turbofan for blowing according to the present invention with that of the conventional axial flow fan and the conventional turbofan;
  • FIG. 19 is a graph comparing noise according to a fluid amount of the turbofan for blowing according to the present invention with that of the convent ional axial flow fan and the conventional turbofan.
  • the turbofan for blowing comprises: a base plate 110 of a disc shape having a hub 111 protruding from a center thereof; a plurality of blades 120 disposed on an outer circumerential surface of the base plate 110 with a constant interval therebetween in a circumferential direction, for blowing cool air introduced from the hub 111 in a radial direction; and a shroud 130 connected to the blades 120 in opposition to the base plate.
  • a circle that is obtained by connecting outer ends of the respective blades 120 in a radial direction corresponds to an outer circumference of the shroud 130 , and is more protruding than an outer circumference of the base plate 110 . That is, a diameter (Do) of a circle that is obtained by connecting outer ends of the respective blades 120 is equal to an outer diameter of the shroud 130 , but is larger than an outer diameter of the base plate 110 .
  • cool air introduced to the hub 111 of the base plate 110 moves between the blades 120 thus to be exhausted in a circumferential direction.
  • the turbofan 100 for blowing is designed with an optimum condition so as to reduce power consumption and noise and to improve a blowing efficiency.
  • each optimum component of the turbofan 100 for blowing will be explained.
  • a diameter of a circle (I) that is obtained by connecting inner ends of the respective blades 120 in a radial direction is defined as an inner diameter (Di) of the blades 120 .
  • a diameter of a circle (O) that is obtained by connecting outer ends of the respective blades 120 in a radial direction is defined as an outer diameter (Do) of a fan.
  • An angle formed between an extension line (E 1 ) from the inner end of the blade 120 and a tangential line (T 1 ) of the circle (I) that is obtained by connecting inner ends of the respective blades 120 is defined as an entrance angle (B 1 ) of the blade.
  • An angle formed between an extension line (E 2 ) from the outer end of the blade 120 and a tangential line (T 2 ) of the circle (O) that is obtained by connecting outer ends of the respective blades 120 is defined as an exit angle (B 2 ) of the blade.
  • a gap between the base plate 110 and the shroud 130 is defined as a height (H) of the blade 120
  • a diameter of inside of the shroud 130 to which cool air is introduced is defined as an inner diameter (Ds) of the shroud.
  • the turbofan for blowing 100 optimized by designing each factor with an optimum condition will be explained.
  • FIG. 6 is a graph showing power consumption according to a ratio (H/Do) between a height (H) of the blade 120 and an outer diameter (Do) of the fan
  • FIG. 7 is a graph showing noise according to the ratio (H/Do) between the height (H) of the blade 120 and the outer diameter (Do) of the fan.
  • the power consumption and the noise of FIGS. 6 and 7 are represented as a secondary function, respectively.
  • the power consumption is increased to be more than approximately 4.5 W.
  • the ratio (H/Do) is approximately 16% ⁇ 26%, a maximum value of the power consumption is approximately 2.75 W.
  • the power consumption when the ratio (H/Do) between the height (H) of the blade 120 and the outer diameter (Do) of the fan is approximately 16% ⁇ 26% corresponds to approximately 61% of the power consumption when the ratio (H/Do) is approximately 10% or 30%.
  • the noise is increased to be more than approximately 22 dB.
  • the ratio (H/Do) between the height (H) of the blade 120 and the outer diameter (Do) of the fan is approximately 16% ⁇ 26%, the noise is approximately 19.5 dB.
  • the noise when the ratio (H/Do) between the height (H) of the blade 120 and the outer diameter (Do) of the fan is approximately 16% ⁇ 26% corresponds to approximately 86% of the noise when the ratio (H/Do) is approximately 10% or 30%.
  • an optimum value of the ratio (H/Do) between the height (H) of the blade 120 and the outer diameter (Do) of the fan is determined as approximately 16% ⁇ 26%.
  • FIG. 8 is a graph showing power consumption according to a ratio between an inner diameter of a shroud and an outer diameter of a fan (Ds/Do)
  • FIG. 9 is a graph showing noise according to the ratio between an inner diameter of a shroud and an outer diameter of a fan (Ds/Do).
  • FIGS. 8 and 9 The power consumption and the noise of FIGS. 8 and 9 are represented as a secondary function, respectively.
  • the power consumption when the ratio (Ds/Do) between the inner diameter (Ds) of the shroud and the outer diameter (Do) of the fan is approximately 72% ⁇ 85% corresponds to approximately 85% of the power consumption when the ratio (Ds/Do) is approximately 60% or 93%.
  • the noise is more than 19.8 dB. Also, when the ratio (Ds/Do) is approximately 92.5%, the noise is more than 19.55 dB. However, when the ratio (Ds/Do) is approximately 72% ⁇ 87%, a maximum value of the noise is approximately 19.2 dB.
  • the noise when the ratio (Ds/Do) between the inner diameter (Ds) of the shroud and the outer diameter (Do) of the fan is approximately 72% ⁇ 87% corresponds to approximately 96% of the noise when the ratio (Ds/Do) is approximately 65% or 92.5%.
  • an optimum value of the ratio (Ds/Do) between the inner diameter (Ds) of the shroud and the outer diameter (Do) of the fan is determined as approximately 72% ⁇ 85%.
  • FIG. 10 is a graph showing power consumption according to a ratio between an inner diameter of a blade and an outer diameter of a fan (Di/Do)
  • FIG. 11 is a graph showing noise according to the ratio between an inner diameter of a blade and an outer diameter of a fan (Di/Do).
  • FIGS. 10 and 11 The power consumption and the noise of FIGS. 10 and 11 are represented as a secondary function, respectively.
  • the power consumption is approximately 3.65 W. Also, when the ratio (Di/Do) is approximately 54% ⁇ 62%, a maximum value of the power consumption is approximately 3.3 W and a minimum value of the power consumption is approximately 3.25 W.
  • the power consumption when the ratio (Di/Do) between the inner diameter (Di) of the blade and the outer diameter (Do) of the fan is approximately 54% ⁇ 62% corresponds to approximately 90% of the power consumption when the ratio (Di/Do) is approximately 50% or 65%.
  • the noise is approximately 20.4 dB. Also, when the ratio (Di/Do) is more than approximately 67%, the noise is approximately 20 dB. However, when the ratio (Di/Do) is approximately 55% ⁇ 64%, a maximum value of the noise is approximately 19.8 dB and a minimum value of the noise is approximately 19.6 dB.
  • the power consumption when the ratio (Di/Do) between the inner diameter (Di) of the blade and the outer diameter (Do) of the fan is approximately 55% ⁇ 64% corresponds to approximately 97% of the power consumption when the ratio (Di/Do) is approximately 50% or 67%.
  • an optimum value of the ratio (Di/Do) between the inner diameter (Di) of the blade 120 and the outer diameter (Do) of the fan is determined as approximately 55% ⁇ 62%.
  • FIG. 12 is a graph showing power consumption according to an entrance angle of a blade (B 1 )
  • FIG. 13 is a graph showing noise according to the entrance angle of a blade (B 1 ).
  • FIGS. 12 and 13 The power consumption and the noise of FIGS. 12 and 13 are represented as a secondary function, respectively.
  • the power consumption has a low value of approximately 3.35 W. Also, when the entrance angle (B 1 ) of the blade is approximately 32°, the power consumption has a minimum value. When the entrance angle (B 1 ) of the blade 120 is approximately 40°, the power consumption is approximately 3.5 W.
  • the power consumption when the entrance (B 1 ) of the blade 120 is approximately 27° ⁇ 35° corresponds to approximately 95% of the power consumption when the entrance (B 1 ) of the blade 120 is less than approximately 25° or more than approximately 40°.
  • the noise has a low value of approximately 18.7 dB. AI so, when the entrance angle (B 1 ) of the blade is approximately 33°, the noise has a minimum value. When the entrance angle (B 1 ) of the blade 120 is approximately 24°, the noise is approximately 19.8 dB.
  • the noise when the entrance (B 1 ) of the blade 120 is approximately 28° ⁇ 37° corresponds to approximately 94% of the noise when the entrance (B 1 ) of the blade 120 is less than approximately 24°.
  • an optimum value of the entrance angle (B 1 ) of the blade 120 is determined as approximately 28° ⁇ 35°.
  • FIG. 14 is a graph showing power consumption according to an exit angle of a blade (B 2 )
  • FIG. 15 is a graph showing noise according to the exit angle of a blade (B 2 ).
  • FIGS. 14 and 15 The power consumption and the noise of FIGS. 14 and 15 are represented as a secondary function, respectively.
  • the power consumption has a low value of approximately 3.32 W.
  • the exit angle (B 2 ) of the blade is approximately 34°, the noise has a minimum value.
  • the noise is approximately 3.52 W.
  • the power consumption when the exit angle (B 2 ) of the blade 120 is approximately 31 ° ⁇ 40 ° corresponds to approximately 94% of the power consumption when the exit angle (B 2 ) of the blade 120 is approximately 22°.
  • the noise has a low value of approximately 18.75 dB. Also, when the exit angle (B 2 ) of the blade is approximately 34°, the noise has a minimum value of approximately 18.7 dB. When the exit angle (B 2 ) of the blade 120 is approximately 48°, the noise is approximately 19.1 dB.
  • the noise when the exit angle (B 2 ) of the blade 120 is approximately 30° ⁇ 41° corresponds to approximately 98% of the noise when the exit angle (B 2 ) of the blade 120 is approximately 48°.
  • an optimum value of the exit angle (B 2 ) of the blade 120 is determined as approximately 31° ⁇ 40°.
  • FIG. 16 is a graph showing power consumption according to an outer diameter of a fan (Do)
  • FIG. 17 is a graph showing noise according to an outer diameter of a fan (Do).
  • FIGS. 16 and 17 The power consumption and the noise of FIGS. 16 and 17 are represented as a secondary function, respectively.
  • the power consumption has a maximum value of approximately 2.4 W.
  • the power consumption has a minimum value of approximately 2.2 W.
  • the power consumption is approximately 2.9 W.
  • the power consumption when the outer diameter (Do) of the fan is approximately 122 mm ⁇ 155 mm corresponds to approximately 83% of the power consumption when the outer diameter (Do) of the fan is approximately 110 mm.
  • the noise has a maximum value of approximately 21 dB.
  • the noise has a minimum value of approximately 19 dB.
  • the noise is approximately 25 dB.
  • the noise when the outer diameter (Do) of the fan is approximately 130 mm ⁇ 170 mm corresponds to approximately 84% of the noise when the outer diameter (Do) of the fan is approximately 110 mm.
  • an optimum value of the outer diameter (Do) of the fan is determined as approximately 130 mm ⁇ 155 mm.
  • a function of the turbofan for blowing 100 according to the present invention will be compared with that of the conventional axial flow fan and the conventional turbofan.
  • FIG. 18 is a graph comparing power consumption according to a fluid amount of the turbofan for blowing according to the present invention with that of the conventional axial flow fan and the conventional turbofan
  • FIG. 19 is a graph comparing noise according to a fluid amount of the turbofan for blowing according to the present invention with that of the conventional axial flow fan and the conventional turbofan.
  • the outer diameter (Do) of the fan is set to be 140 mm, and the rest factors are set to have a medium value in the aforementioned optimum range, respectively. That is, the height (H) of the blade 120 is 29 mm ⁇ 140*(0.16+0.26)/ 2 ⁇ , the inner diameter (Ds) of the shroud 130 is 110 mm, the inner diameter (Di) of the blade 120 is 82 mm, the entrance angle (B 1 ) of the blade 120 is 31.5°, and the exit angle (B 2 ) of the blade 120 is 35.5°.
  • the turbofan for blowing 100 according to the present invention, the conventional turbofan, and the conventional axial flow fan show each increasing function in which the power consumption is increased as the fluid amount is increased.
  • the turbofan for blowing 100 according to the present invention has less power consumption than the conventional axial flow fan and the conventional turbofan, and shows the smallest gradient.
  • the conventional axial flow fan has a gradient of 10 ⁇ (5.4-3.4)/0.2 ⁇ by in creasing the power consumption to 5.4 W from 3.4 W.
  • the conventional turbofan has a gradient of 9 by increasing the power consumption to 4.6 W from 2.8 W.
  • the turbofan for blowing according to the present invention has a gradient of 5 by increasing the power consumption 2.9 W from 1.9 W.
  • the turbofan for blowing 100 has a smaller power consumption and a smaller gradient than the conventional axial flow fan and the conventional turbofan, thereby having an excellent economical characteristic.
  • the turbofan for blowing 100 according to the present invention, the conventional turbofan, and the conventional axial flow fan show each increasing function in which the noise is increased as the fluid amount is increased.
  • the turbofan for blowing 100 according to the present invention has less noise than the conventional axial flow fan and the conventional turbofan, and shows the smallest gradient.
  • the turbofan for blowing 100 has smaller noise and a smaller gradient than the conventional axial flow fan and the conventional turbofan, thereby having a low noise characteristic.
  • a refrigerator installed at a rear surface of a grill of a freezing chamber and having the turbofan for blowing cool air generated from an evaporator into the freezing chamber.
  • the turbofan an optimized turbofan capable of reducing power consumption and noise is used.
  • the grill of the freezing chamber and the evaporator (not shown) can be easily understood with reference to FIG. 2 .
  • each component of the turbofan for blowing is designed with an optimum state. Accordingly, power consumption is lowered thus to enhance a cooling efficiency and to reduce noise.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US12/280,879 2006-10-19 2006-10-19 Turbo fan for blowing and refrigerator having the same Abandoned US20090038333A1 (en)

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PCT/KR2006/004266 WO2008047962A1 (en) 2006-10-19 2006-10-19 Turbo fan for blowing and refrigerator having the same

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EP (1) EP1984683A4 (zh)
CN (1) CN101529177B (zh)
WO (1) WO2008047962A1 (zh)

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US20100126206A1 (en) * 2008-11-26 2010-05-27 Park Jeong Taek Indoor unit for air conditioning apparatus
CN102996508A (zh) * 2012-12-27 2013-03-27 常州格力博有限公司 用于吹吸机的风叶
US20150118037A1 (en) * 2013-10-28 2015-04-30 Minebea Co., Ltd. Centrifugal fan
CN106593946A (zh) * 2016-11-08 2017-04-26 青岛海尔股份有限公司 离心风机及具有该离心风机的风冷冰箱
US20170314568A1 (en) * 2016-05-02 2017-11-02 Dongbu Daewoo Electronics Corporation In-refrigerator blower and refrigerator including the same
EP3401547A1 (fr) * 2017-05-11 2018-11-14 Vti Ventilateur centrifuge d'extraction d'air à basse pression

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KR102645031B1 (ko) * 2016-10-24 2024-03-07 엘지전자 주식회사 냉장고용 송풍팬

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100126206A1 (en) * 2008-11-26 2010-05-27 Park Jeong Taek Indoor unit for air conditioning apparatus
CN102996508A (zh) * 2012-12-27 2013-03-27 常州格力博有限公司 用于吹吸机的风叶
US20150118037A1 (en) * 2013-10-28 2015-04-30 Minebea Co., Ltd. Centrifugal fan
US20170314568A1 (en) * 2016-05-02 2017-11-02 Dongbu Daewoo Electronics Corporation In-refrigerator blower and refrigerator including the same
CN106593946A (zh) * 2016-11-08 2017-04-26 青岛海尔股份有限公司 离心风机及具有该离心风机的风冷冰箱
EP3401547A1 (fr) * 2017-05-11 2018-11-14 Vti Ventilateur centrifuge d'extraction d'air à basse pression
FR3066235A1 (fr) * 2017-05-11 2018-11-16 Vti Ventilateur centrifuge d'extraction d'air a basse pression.

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CN101529177A (zh) 2009-09-09
EP1984683A4 (en) 2015-09-16
EP1984683A1 (en) 2008-10-29
CN101529177B (zh) 2011-01-05

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