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 refrigerat or having the same, and more particularly, to a turbofan for blowing capable o f improving a blowing efficiency for cool air and minimizing power consumptio n and noise, and a refrigerator having the same.
• a refrigerator serves to store foodstuffs as a freezing state o r 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 disp osed at a front surface of the body 10 for opening and closing the freezing ch amber 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 b ody 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
• turbofan 9 Even if the turbofan 9 maintains an inner temperature of the refrigerato r, it causes noise. Accordingly, it is required to design the turbofan 9 so as to reduce nois e and power consumption and to improve a blowing efficiency for cool air.
• turbofan f or blowing capable of improving a blowing efficiency for cool air and minimizin g power consumption and noise, and a refrigerator having the same.
• a turbofan for blowing, com prising 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 c onnected 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 di ameter 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 t he fan.
• An inner diameter of the blade is 55% ⁇ 62% of the outer diameter of th e fan, in which the inner diameter of the blade denotes a diameter of a circle t hat 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 protr uding from a center thereof; a plurality of blades disposed on an outer circum erential surface of the base plate with a constant interval therebetween in a ci rcumferential 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 diamete r of a fan, in which the height of the blade denotes a gap between the base pi ate 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 conne cting inner ends of the respective blades.
• FIG. 1 is a perspective view showing a refrigerator in accordance with t he conventional art
• FIG. 2 is a sectional view showing a side of the refrigerator in accordan ce with the conventional art
• FIG. 3 is a perspective view showing a turbofan for blowing according t o the present invention.
• FIG. 4 is a planar view showing the turbofan for blowing according to th e 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 bet ween 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 heigh t of a blade and an outer diameter of a fan (H/Do);
• FIG. 8 is a graph showing power consumption according to a ratio bet ween 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 inne r 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 bet ween 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 inn er diameter of a blade and an outer diameter of a fan (Di/Do);
• FIG. 12 is a graph showing power consumption according to an entran ce angle of a blade (B1 );
• FIG. 13 is a graph showing noise according to the entrance angle of a blade (B1 );
• FIG. 14 is a graph showing power consumption according to an exit an gle of a blade (B2);
• FIG. 15 is a graph showing noise according to the exit angle of a blade (B2)
• FIG. 16 is a graph showing power consumption according to an outer d iameter of a fan (Do);
• FIG. 17 is a graph showing noise according to an outer diameter of a f an (Do);
• FIG. 18 is a graph comparing power consumption according to a fluid a mount of the turbofan for blowing according to the present invention with that of the conventional axial flow fan and the conventional turbofan; and
• FIG. 19 is a graph comparing noise according to a fluid amount of the t urbofan 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 p late 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 bas e 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 s hroud 130 connected to the blades 120 in opposition to the base plate.
• a circle that is obtained by connecting outer ends of the respective bla des 120 in a radial direction corresponds to an outer circumference of the shr oud 130, and is more protruding than an outer circumference of the base plat e 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 th e base plate 110 moves between the blades 120 thus to be exhausted in a cir cumferential 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 efficien cy.
• each optimum component of the turbofan 100 for blowing will be explained.
• a diameter of a circle (I) that is obtained by connec ting 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 obta ined by connecting outer ends of the respective blades 120 in a radial directio n is defined as an outer diameter (Do) of a fan.
• An angle formed between an extension line (E1) from the inner end of the blade 120 and a tangential line ( T1 ) of the circle (I) that is obtained by connecting inner ends of the respective blades 120 is defined as an entrance angle (B1) of the blade.
• An angle forme d between an extension line (E2) from the outer end of the blade 120 and a ta ngential line (T2) of the circle (O) that is obtained by connecting outer ends of the respective blades 120 is defined as an exit angle (B2) of the blade.
• a gap between the base plate 110 and the shroud 130 is defined as a height (H) of the blade 120, and a diameter of inside of th e 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 a n optimum condition will be explained.
• FIG. 6 is a graph showing power consumption according to a ratio (H/D o) between a height (H) of the blade 120 and an outer diameter (Do) of the fa n
• 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 po were consumption and the noise of FIGS. 6 and 7 are represented as a second ary function, respectively.
• the power consumption when the ratio (H/Do) betwee n the height (H) of the blade 120 and the outer diameter (Do) of the fan is app roximately 16% ⁇ 26% corresponds to approximately 61% of the power consu mption when the ratio (H/Do) is approximately 10% or 30%.
• the noise is increased to be more than approximately 22dB.
• the r atio (H/Do) between the height (H) of the blade 120 and the outer diameter (D o) of the fan is approximately 16% ⁇ 26%, the noise is approximately 19.5dB.
• 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%.
• FIG. 8 is a graph showing power consumption according to a ratio bet ween an inner diameter of a shroud and an outer diameter of a fan (Ds/Do), a nd FIG. 9 is a graph showing noise according to the ratio between an inner di ameter of a shroud and an outer diameter of a fan (Ds/Do).
• the power consumption and the noise of FIGS. 8 and 9 are represente d as a secondary function, respectively.
• the ratio (Ds/Do) between an inner diameter (Ds) of the shroud and the outer diameter (Do) of the fan is less than approxi mately 60% or more than approximately 93%, the power consumption is incre ased to be more than approximately 3.8W.
• the ratio (Ds/Do) i s approximately 72% ⁇ 85% a maximum value of the power consumption is ap proximately 3.25W.
• the power consumption when the ratio (Ds/Do) betwe en the inner diameter (Ds) of the shroud and the outer diameter (Do) of the fa n 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 19.8dB.
• the ratio (Ds/Do) is a pproximately 92.5%, the noise is more than 19.55dB.
• the rati o (Ds/Do) is approximately 72% ⁇ 87%, a maximum value of the noise is appro ximately 19.2dB.
• the noise when the ratio (Ds/Do) between the inner di ameter (Ds) of the shroud and the outer diameter (Do) of the fan is approxima tely 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 d iameter (Ds) of the shroud and the outer diameter (Do) of the fan is determine d as approximately 72% ⁇ 85%.
• FIG. 10 is a graph showing power consumption according to a ratio bet ween 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 dia meter 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 represe nted as a secondary function, respectively.
• the ratio (Di/Do) between the inner diamete r (Di) of the blade and the outer diameter (Do) of the fan is approximately 50
• the power consumption is approximately 3.65W. Also, when the ratio (Di/D o) is approximately 54% ⁇ 62%, a maximum value of the power consumption is approximately 3.3W and a minimum value of the power consumption is appr oximately 3.25W.
• the power consumption when the ratio (Di/Do) betwe en the inner diameter (Di) of the blade and the outer diameter (Do) of the fan i s approximately 54% ⁇ 62% corresponds to approximately 90% of the power c onsumption when the ratio (Di/Do) is approximately 50% or 65%.
• the ratio (Di/Do) between the inner diamete r (Di) of the blade 120 and the outer diameter (Do) of the fan is approximately
• the noise is approximately 20.4dB. Also, when the ratio (Di/Do) is more t han approximately 67%, the noise is approximately 2OdB. However, when the ratio (Di/Do) is approximately 55% ⁇ 64%, a maximum value of the noise is a pproximately 19.8dB and a minimum value of the noise is approximately 19.6 dB.
• the power consumption when the ratio (Di/Do) betwe en the inner diameter (Di) of the blade and the outer diameter (Do) of the fan i s approximately 55% ⁇ 64% corresponds to approximately 97% of the power c onsumption when the ratio (Di/Do) is approximately 50% or 67%. Accordingly, an optimum value of the ratio (Di/Do) between the inner di ameter (Di) of the blade 120 and the outer diameter (Do) of the fan is determi ned as approximately 55% ⁇ 62%.
• FIG. 12 is a graph showing power consumption according to an entran ce angle of a blade (B1)
• FIG. 13 is a graph showing noise according to t he entrance angle of a blade (B1 ).
• FIGS. 12 and 13 The power consumption and the noise of FIGS. 12 and 13 are represe nted as a secondary function, respectively.
• the power consumption has a low value of approxima tely 3.35W.
• the entrance angle (B1) of the blade is approximately 32°, the power consumption has a minimum value.
• the power consumption is approxi mately 3.5W. More concretely, 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 (B1 ) of the blade 120 is less than ap proximately 25° or more than approximately 40°.
• the noise has a low value of approximately 18.7dB. Al so, when the entrance angle (B1 ) of the blade is approximately 33°, the noise has a minimum value. When the entrance angle (B1) of the blade 120 is appr oximately 24°, the noise is approximately 19.8dB.
• an optimum value of the entrance angle (B1 ) of the blade 120 is determined as approximately 28° ⁇ 35°.
• FIG. 14 is a graph showing power consumption according to an exit an gle of a blade (B2)
• FIG. 15 is a graph showing noise according to the exi t angle of a blade (B2).
• FIGS. 14 and 15 The power consumption and the noise of FIGS. 14 and 15 are represe nted as a secondary function, respectively.
• the power consumption when the exit angle (B2) of th e blade 120 is approximately 31° ⁇ 40°corresponds to approximately 94% of th e power consumption when the exit angle (B2) of the blade 120 is approximat ely 22°.
• the noise has a low value of approximately 18.75dB. Also, when the exit angle (B2) of the blade is approximately 34°, the noise has a minimum value of approximately 18.7dB. When the exit angle (B2) of the blad e 120 is approximately 48°, the noise is approximately 19.1dB.
• FIG. 16 is a graph showing power consumption according to an outer d iameter of a fan (Do)
• FIG. 17 is a graph showing noise according to an o uter diameter of a fan (Do).
• FIGS. 16 and 17 The power consumption and the noise of FIGS. 16 and 17 are represe nted as a secondary function, respectively.
• the power consumption has a maximum value of app roximately 2.4W.
• the power consumption has a minimum value of approximately 2.2W.
• the power consumption is approximately 2.9W.
• the power consumption when the outer diameter (Do) of the fan is approximately 122mm ⁇ 155mm corresponds to approximately 8 3% of the power consumption when the outer diameter (Do) of the fan is appr oximately 110mm.
• the noise has a maximum value of approximately 21 dB.
• the outer diameter (Do) of the fan is approximately 155mm, the noi se has a minimum value of approximately 19dB.
• the noise is approximately 25dB.
• the noise when the outer diameter (Do) of the fan is a pproximately 130mm ⁇ 170mm corresponds to approximately 84% of the noise when the outer diameter (Do) of the fan is approximately 110mm. Accordingly, an optimum value of the outer diameter (Do) of the fan is determined as approximately 130mm ⁇ 155mm.
• FIGS. 18 and 19 a function of the turbofan for blowing 10 0 according to the present invention will be compared with that of the conventi onal axial flow fan and the conventional turbofan.
• FIG. 18 is a graph comparing power consumption according to a fluid a mount of the turbofan for blowing according to the present invention with that of the conventional axial flow fan and the conventional turbofan
• FIG. 19 i s a graph comparing noise according to a fluid amount of the turbofan for bio wing 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 140mm, and the rest fac tors are set to have a medium value in the aforementioned optimum range, re spectively. That is, the height (H) of the blade 120 is 29mm ⁇ 140*(0.16+0.26)/ 2 ⁇ , the inner diameter (Ds) of the shroud 130 is 110mm, the inner diameter (D i) of the blade 120 is 82mm, the entrance angle (B1 ) of the blade 120 is 31.5°, and the exit angle (B2) of the blade 120 is 35.5°.
• the turbofan for blowing 100 according to the pre sent invention, the conventional turbofan, and the conventional axial flow fan show each increasing function in which the power consumption is increased a s the fluid amount is increased.
• the turbofan for blowing 100 according to the present invention has les s power consumption than the conventional axial flow fan and the convention al turbofan, and shows the smallest gradient. More concretely, when the fluid amount is increased to 1.5m 3 /s from 1. 3m 3 /s, the conventional axial flow fan has a gradient of 10 ⁇ (5.4-3.4)/0.2 ⁇ by in creasing the power consumption to 5.4W from 3.4W. In the same condition, th e conventional turbofan has a gradient of 9 by increasing the power consumpt ion to 4.6W from 2.8W. However, in the same condition, the turbofan for blowi ng according to the present invention has a gradient of 5 by increasing the po was consumption 2.9W from 1.9W.
• the turbofan for blowing 100 according to the present inv ention has a smaller power consumption and a smaller gradient than the conv entional axial flow fan and the conventional turbofan, thereby having an excell ent economical characteristic.
• the turbofan for blowing 100 according to the pre sent invention, the conventional turbofan, and the conventional axial flow fan show each increasing function in which the noise is increased as the fluid am ount is increased.
• the turbofan for blowing 100 according to the present invention has les s noise than the conventional axial flow fan and the conventional turbofan, an d shows the smallest gradient.
• the turbofan for blowing 100 according to the present inv ention has smaller noise and a smaller gradient than the conventional axial flo w 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 ha ving the turbofan for blowing cool air generated from an evaporator into the fr eezing chamber.
• the turbofan an optimized turbofan capable of reducing p ower consumption and noise is used.
• the grill of the freezing chamber and th e 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 t hus 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)

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Publications (1)

Family

ID=39314166

Family Applications (1)

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Cited By (3)

Families Citing this family (5)

Citations (10)

Family Cites Families (6)

• 2006
  • 2006-10-19 WO PCT/KR2006/004266 patent/WO2008047962A1/en active Application Filing
  • 2006-10-19 CN CN2006800561476A patent/CN101529177B/zh not_active Expired - Fee Related
  • 2006-10-19 EP EP06799340.2A patent/EP1984683A4/en not_active Withdrawn
  • 2006-10-19 US US12/280,879 patent/US20090038333A1/en not_active Abandoned

Patent Citations (10)

Non-Patent Citations (1)

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