EP3995698A1 - Zentrifugalgebläse für kühlmaschine - Google Patents

Zentrifugalgebläse für kühlmaschine Download PDF

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Publication number
EP3995698A1
EP3995698A1 EP21155058.7A EP21155058A EP3995698A1 EP 3995698 A1 EP3995698 A1 EP 3995698A1 EP 21155058 A EP21155058 A EP 21155058A EP 3995698 A1 EP3995698 A1 EP 3995698A1
Authority
EP
European Patent Office
Prior art keywords
blades
centrifugal fan
refrigerator
hub
side end
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.)
Pending
Application number
EP21155058.7A
Other languages
English (en)
French (fr)
Inventor
Younggyu Jung
Hakkyu CHOI
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
Application filed by LG Electronics Inc filed Critical LG Electronics Inc
Publication of EP3995698A1 publication Critical patent/EP3995698A1/de
Pending 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
    • F04D29/28—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
    • 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
    • F04D29/283—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 rotors of the squirrel-cage type
    • 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
    • F04D29/30—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/70—Shape
    • 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 disclosure relates to centrifugal fans for refrigerators. More particularly, the disclosure relates to a centrifugal fan for a refrigerator that provides air cooled by an evaporator to a refrigerating compartment or a freezing compartment.
  • a refrigerator may cool food or prevent spoilage by providing cold air using a refrigeration cycle device including a compressor, a condenser, an expansion mechanism, and an evaporator.
  • a refrigerator is a device that stores food for a long time in a fresh state using cold air.
  • a centrifugal fan for a refrigerator is installed on the flow path, which blows air into the refrigerating compartment and freezing compartment after forcing the air to flow from the refrigerating compartment and the freezing compartment through an evaporator.
  • FIG. 17 is a cross-sectional view of a refrigerator according to the prior art.
  • the refrigerator 10 typically includes an outer case 11 with a front opening, an inner case 12 disposed in the outer case 11, a storage compartment (e.g., a refrigerating compartment or a freezing compartment) disposed in the inner case 12, and a door disposed on the front surface of the outer case 11 to open and close the storage compartment.
  • an inner case 12 disposed in the outer case 11
  • a storage compartment e.g., a refrigerating compartment or a freezing compartment
  • a door disposed on the front surface of the outer case 11 to open and close the storage compartment.
  • the refrigerator 10 includes an evaporator 14 formed on a side of the storage compartment to heat-exchange the refrigerant and air to generate cold air, a cold air flow path 16 disposed between the outer case 11 and the inner case 12, a refrigerator centrifugal fan 17 for circulating the cold air from the evaporator 14 to the storage compartment through the cold air flow path 16, and a motor 15 for providing power to the refrigerator centrifugal fan 17.
  • the centrifugal fan for refrigerator requires more than twice the work.
  • turbo fan The diameter of a turbo fan, as disclosed in prior document 1 (Korean Patent No. 10-0389395 ) and prior document 2 (Korean Patent No. 10-1577875 ), is generally about 110 mm to 140 mm, and the rotation speed is about 1200 rpm.
  • the turbo fan may mean a fan in which blades are convexly formed in the rotation direction of the fan.
  • the rotational speed of the fan is inversely proportional to the third power of the diameter of the fan according to the law of similarity of the fan, so that the rotational speed of the fan increases up to 2600 rpm.
  • More noise may be caused due to aerodynamic or vibration resultant from the excessive increase in the rpm of the fan.
  • the disclosure aims to provide a centrifugal fan for a refrigerator capable of reducing the number of rotations of the fan while increasing the internal capacity of the refrigerator.
  • the disclosure also aims to provide a centrifugal fan for a refrigerator that reduces noise due to aerodynamic or vibration generated by an increase in the rotation speed of the fan.
  • the disclosure also aims to provide a centrifugal fan for a refrigerator capable of increasing the lifespan of components of the refrigerator.
  • the disclosure also aims to provide a high-efficiency refrigerator centrifugal fan capable of increasing the discharge pressure under the same flow rate condition.
  • the disclosure aims to provide a centrifugal fan for a refrigerator that may maximize discharge pressure efficiency under the same flow rate condition.
  • the disclosure aims to provide a centrifugal fan for a refrigerator capable of preventing interference of a product that may occur when injection molding is used.
  • the disclosure also aims to provide a centrifugal fan for a refrigerator capable of reducing the number of rotations of the fan under the same flow rate and pressure condition by reducing the length of the blade cord.
  • a centrifugal fan for a refrigerator comprises a hub coupled to a rotation shaft, and a plurality of blades disposed radially about the rotation shaft on the hub, wherein the blades are formed to be entirely concave along a rotational direction.
  • the blades may meet an equation expressed as:0.67 ⁇ D I /D O ⁇ 0.77 (where, D I is a distance between an inner end of the blades and a center area of the rotation shaft, and D O is a distance between an outer end of the blades and the center area of the rotation shaft).
  • the blades may meet an equation expressed as: 0.25 ⁇ L3/L2 ⁇ 0.3 (where, L3 is a maximum camber amount of the blades, and L2 is a chord length of the blades).
  • the blades may meet an equation expressed as: 044 ⁇ L4/L2 ⁇ 0.58 (where L4 is a maximum camber position of the blades, and L2 is the chord length of the blades).
  • An inner diameter of a suction-side end of the blades may be smaller than an inner diameter of a hub-side end of the blades.
  • a predetermined angle may be formed between a chord line of a hub-side end of the blades and a chord line of a suction-side end of the blades.
  • the predetermined angle formed between the chord line of the hub-side end of the blades and the chord line of the suction-side end of the blades may range from 18.7 degrees to 21 degrees.
  • the predetermined angle formed between the chord line of the hub-side end of the blades and the chord line of the suction-side end of the blades may be 19.8 degrees.
  • a radial outer end of the blades may be disposed in the rotational direction, as compared with an inner end of the blades.
  • a centrifugal fan for a refrigerator comprises a hub coupled to a rotation shaft, and a plurality of blades disposed radially about the rotation shaft on the hub, wherein a predetermined angle is formed between a chord line of a hub-side end of the blades and a chord line of a suction-side end of the blades.
  • the predetermined angle formed between the chord line of the hub-side end of the blades and the chord line of the suction-side end of the blades may range from 18.7 degrees to 21 degrees.
  • the predetermined angle formed between the chord line of the hub-side end of the blades and the chord line of the suction-side end of the blades may be 19.8 degrees.
  • the blades may be formed to be entirely concave in the rotational direction.
  • the blades may meet an equation expressed as:0.67 ⁇ D I /D O ⁇ 0.77 (where, D I is a distance between an inner end of the blades and a center area of the rotation shaft, and D O is a distance between an outer end of the blades and the center area of the rotation shaft).
  • the blades may meet an equation expressed as: 0.25 ⁇ L3/L2 ⁇ 0.3 (where, L3 is a maximum camber amount of the blades, and L2 is a chord length of the blades).
  • the blades may meet an equation expressed as: 044 ⁇ L4/L2 ⁇ 0.58 (where L4 is a maximum camber position of the blades, and L2 is the chord length of the blades).
  • a radial outer end of the blades may be disposed in the rotational direction, as compared with an inner end of the blades.
  • the disclosure may provide a centrifugal fan for a refrigerator capable of reducing the number of rotations of the fan while increasing the internal capacity of the refrigerator.
  • the disclosure may provide a centrifugal fan for a refrigerator that reduces noise due to aerodynamic or vibration generated by an increase in the rotation speed of the fan.
  • the disclosure may provide a centrifugal fan for a refrigerator capable of increasing the lifespan of components of the refrigerator.
  • the disclosure may provide a high-efficiency refrigerator centrifugal fan capable of increasing the discharge pressure under the same flow rate condition.
  • the disclosure may provide a centrifugal fan for a refrigerator that may maximize discharge pressure efficiency under the same flow rate condition.
  • the disclosure may provide a centrifugal fan for a refrigerator capable of preventing interference of a product that may occur when injection molding is used.
  • the disclosure may provide a centrifugal fan for a refrigerator capable of reducing the number of rotations of the fan under the same flow rate and pressure condition by reducing the length of the blade cord.
  • FIG. 1 is a cross-sectional view illustrating a refrigerator according to an embodiment of the disclosure.
  • a refrigerator 10 may include an outer case 11, an inner case 12, a door 13, an evaporator 14, a cold air flow path 16, a blower 100, and a motor 15.
  • some of the components may be excluded, or the refrigerator 10 may include more components.
  • the outer case 11 may have a front opening and an inner space.
  • the outer case 11 may form the exterior of the refrigerator 10.
  • the outer case 11 may be formed overall in a hexahedral shape with a front opening but, without limitations thereto, the outer case 11 may be formed in other various shapes.
  • the inner case 12 may be disposed inside the outer case 11.
  • the inner case 12 may be spaced apart from the outer case 11.
  • the inner case 12 may include an inner space.
  • a storage compartment may be formed in the inner space of the inner case 12.
  • the storage compartment may be referred to as a refrigerator compartment or a freezer compartment.
  • There may be provided a plurality of storage compartments.
  • the plurality of storage compartments may be maintained in different temperature zones.
  • One of the plurality of storage compartments may be a refrigerating compartment, and the other may be a freezing compartment.
  • the door 13 may be disposed on the front surface of the outer case 11.
  • the door 13 may be selectively opened and closed by a user.
  • a plurality of doors 13 may be provided according to the number of storage compartments.
  • the evaporator 14 may be disposed between the outer case 11 and the inner case 12. The evaporator 14 may be disposed on one side or rear of the storage compartment. The evaporator 14 may be disposed under the cold air flow path 16. The evaporator 14 may be disposed under the blower 100. The evaporator 14 may be disposed in a lower portion of the refrigerator 10. The evaporator 14 may generate cold air by exchanging air supplied from the storage compartment with a refrigerant. The cold air generated by the evaporator 14 may be provided to the blower 100.
  • a plurality of evaporators 14 may be provided.
  • One of the plurality of evaporators may cool the refrigerating compartment, and the other may cool the freezing compartment.
  • both the refrigerating compartment and freezing compartment may be cooled by one evaporator.
  • the refrigerator 10 may include a refrigeration cycle device including a compressor (not shown) for compressing the refrigerant, a condenser (not shown) for condensing the refrigerant compressed by the compressor, an expansion mechanism for expanding the refrigerant condensed by the condenser, and the evaporator 14 to which the refrigerant expanded by the expansion mechanism is provided.
  • a refrigeration cycle device including a compressor (not shown) for compressing the refrigerant, a condenser (not shown) for condensing the refrigerant compressed by the compressor, an expansion mechanism for expanding the refrigerant condensed by the condenser, and the evaporator 14 to which the refrigerant expanded by the expansion mechanism is provided.
  • the cold air flow path 16 may be disposed between the outer case 11 and the inner case 12.
  • the cold air flow path 16 may be disposed on one side or rear of the storage compartment.
  • the cold air flow path 16 may extend in upper and lower directions or a vertical direction.
  • the cold air flow path 16 may provide a flow path through which cold air flows.
  • One side of the cold air flow path 16 may be connected to the blower 100 and the other side may be connected to the storage compartment.
  • the cold air flow path 16 may be disposed over the blower 100.
  • the cold air flow path 16 may be disposed over the evaporator 14.
  • the blower 100 may be disposed between the outer case 11 and the inner case 12.
  • the blower 100 may be disposed under the cold air flow path 16.
  • the blower 100 may be disposed in a lower portion of the cold air flow path 16.
  • the blower 100 may be disposed in front of the motor 15.
  • the blower 100 may be coupled with the motor 15.
  • the blower 100 may be disposed over the evaporator 14.
  • the blower 100 may flow cold air generated by the evaporator 14 to the storage compartment through the cold air flow path 16.
  • the motor 15 may be coupled to the blower 100.
  • the motor 15 may drive the blower 100 through external power.
  • the motor 15 may be disposed behind the blower 100.
  • the motor 15 may be disposed over the evaporator 14.
  • the motor 15 may be disposed under the cold air flow path 16.
  • the internal capacity of the refrigerator 10 may be increased in volume V as compared to the internal capacity of the refrigerator according to the prior art. Accordingly, the sizes of the blower 100 and the evaporator 14 may be reduced, and the cold air flow path 16 may be narrowed. This is described below in greater detail.
  • FIG. 2 is a cross-sectional view illustrating a blower according to an embodiment of the disclosure.
  • the blower 100 may include a housing 120, a motor 150, and a centrifugal fan 200 for a refrigerator, but some of the components may be omitted, or the blower 100 may include more components.
  • the housing 120 may include a suction port 120a through which cold air generated by the evaporator 14 is sucked, and a discharge port 120b for discharging the refrigerant passing through the refrigerator centrifugal fan 200.
  • the housing 120 may be fixed to the motor 150.
  • the centrifugal fan 200 for a refrigerator may be rotatably disposed in the housing 120.
  • the housing 120 may form a flow path for cold air and air.
  • a bell mouth 110 may extend from the housing 120.
  • the bell mouth 110 may be formed in a rea center area of the housing 120.
  • the inner diameter of the bell mouth 110 may increase toward the centrifugal fan 200 for a refrigerator.
  • the blower 100 may include a convex portion 110a formed to be convex towards the centrifugal fan 200 for a refrigerator between the bell mouth 110 and the housing 120.
  • the motor 150 may be driven by external power.
  • the motor 150 may be coupled to the housing 120.
  • the rotation shaft of the motor 150 may be coupled to the centrifugal fan 200 for a refrigerator.
  • the centrifugal fan 200 for a refrigerator may be rotated in one direction according to the rotation of the rotation shaft of the motor 150.
  • the motor 150 may be understood as identical to the motor 15 described above in connection with FIG. 1 .
  • the centrifugal fan 200 for a refrigerator may be disposed in the housing 120.
  • the centrifugal fan 200 for a refrigerator may be rotatably connected to the motor 150.
  • the centrifugal fan 200 for a refrigerator may rotate in one direction according to the rotation of the rotation shaft of the motor 150.
  • the centrifugal fan 200 for a refrigerator may be disposed in front of the motor. A detailed configuration of the centrifugal fan 200 for a refrigerator will be described later.
  • a shroud (not shown) may be installed to introduce the air and refrigerant to be introduced through the suction port 120a and to guide the air through the discharge port 120b.
  • FIG. 3 is a perspective view illustrating a refrigerator centrifugal fan according to an embodiment of the disclosure.
  • FIG. 4 is a plan view illustrating a refrigerator centrifugal fan according to an embodiment of the disclosure.
  • FIG. 5 is a cross-sectional view illustrating a refrigerator centrifugal fan according to an embodiment of the disclosure;
  • FIG. 6 is an enlarged view of part A of FIG. 4 .
  • FIG. 7 is a view schematically illustrating a blade according to an embodiment of the disclosure;
  • FIG. 8 is a graph illustrating the discharge pressure according to the diameter ratio of a blade according to an embodiment of the disclosure.
  • FIG. 9 is a graph illustrating the discharge pressure according to the maximum camber amount of a blade according to an embodiment of the disclosure.
  • FIG. 10 is a graph illustrating the discharge pressure according to the maximum camber position of a blade according to an embodiment of the disclosure.
  • the centrifugal fan 200 for a refrigerator may include a hub 210, a blade 230, a connecting member 220, and a coupling part 240.
  • the refrigerator centrifugal fan 200 may include more or less components according to an embodiment.
  • the hub 210 may be disposed in the housing 120.
  • the hub 210 may be rotatably coupled to the motor 150.
  • the hub 210 may be coupled to the rotation shaft of the motor 150.
  • the hub 210 may rotate in one direction according to the rotation of the rotation shaft of the motor 150.
  • the blade 230 may be disposed on the hub 210.
  • the hub 210 may include a first area 212.
  • the blade 230 may be disposed in the first area 212.
  • the blade 230 may be disposed on the front surface of the first area 212.
  • the first area 212 may be formed flat.
  • the first area 212 may be disposed adjacent to the motor 150 as compared to a second area 214.
  • the first area 212 may be disposed behind the second area 214.
  • the hub 210 may include the second area 214.
  • the second area 214 may extend from the first area 212.
  • the second area 214 may have curvature.
  • the second area 214 may be formed to be convex in the opposite direction or forward of the motor 150.
  • the second area 214 may be formed in a semicircular shape.
  • the second area 214 may have an infection point.
  • the blade 230 may be disposed on the hub 210.
  • the blade 230 may be disposed in the first area 212 of the hub 210.
  • the blade 230 may be disposed on the front surface of the first area 212 of the hub 210.
  • the blade 230 may be spaced apart from the center area of the hub 210.
  • the blade 230 overall may have curvature.
  • the blade 230 may have no inflection point.
  • the width of the blade 230 may be constant. Here, the width of the blade 230 may mean the minimum distance between the pressure surface 233 and the negative pressure surface 232.
  • the blade 230 may include a leading edge 231 disposed radially inward of the centrifugal fan 200 for a refrigerator, a trailing edge 234 disposed radially outward of the centrifugal fan 200 for a refrigerator, the pressure surface 233 connecting the leading edge 231 and the trailing edge 234 and disposed along the rotation direction of the refrigerator centrifugal fan 200, and the negative pressure surface 232 connecting the leading edge 231 and the trailing edge 234 and disposed in the opposite direction of the rotation direction of the refrigerator centrifugal fan 200.
  • the pressure surface 233 has a higher pressure than the atmospheric pressure, thus pushing out the air.
  • the negative pressure surface 232 is the opposite surface of the pressure surface 233 and may have a pressure lower than the atmospheric pressure.
  • the leading edge 231 may contact the cold air introduced through the suction port 120a, and the trailing edge 234 may discharge the cold air toward the discharge port 120b.
  • the minimum distance between the center of the leading edge 231 and the center of the trailing edge 234 is defined as a chord length L2
  • the virtual straight line connecting the center of the leading edge 231 with the center of the trailing edge 234 is defined as a chord line
  • the line connecting the midpoints of the pressure surface 233 and the negative pressure surface 232 is defined as a camber line L1.
  • the maximum camber amount L3 is defined as the maximum camber amount L3
  • the distance from the center of the leading edge 231 to the maximum camber is defined as the maximum camber position L4.
  • the blade 230 may be formed overall concave in the rotation direction.
  • the blade 230 when the centrifugal fan 200 for a refrigerator rotates clockwise, the blade 230 may be concave clockwise or convex counterclockwise.
  • the trailing edge 234, which is the radially outer end of the centrifugal fan 200 for a refrigerator, of the blade 230 may be disposed more in the rotational direction than the leading edge 231, which is the radially inner end.
  • the trailing edge 234 may be disposed more clockwise or to the right than the leading edge 231.
  • the length L2 of the cord may be shorter than that of the conventional turbofan, and the number of blades 230a, 230b, and 230c may be increased.
  • the plurality of blades 230 may be formed a plurality of blades 230 including blades 230a, 230b, and 230c.
  • the plurality of blades 230a, 230b, and 230c may be disposed radially with respect to the rotation shaft of the motor 150.
  • the plurality of blades 230a, 230b, and 230c may be disposed radially with respect to the central area of the hub 210.
  • the plurality of blades 230a, 230b, and 230c may be spaced apart from each other in the circumferential direction.
  • a connecting member 220 may be coupled to the front surface of the blade 230.
  • the connecting member 220 may be coupled to an outer surface or a trailing edge of the blade 230.
  • the connecting member 220 may be connected to the plurality of blades 230.
  • the connecting member 220 may be shaped as a circular band or ring.
  • a coupling part 240 may be formed on the hub 210.
  • the coupling part 240 may be formed in a central area of the hub 210.
  • the coupling part 240 may be formed in the central area of the second area 214 of the hub 210.
  • the coupling part 240 may be coupled to the rotation shaft of the motor 150.
  • the blade 230 may satisfy Equation 1 below. 0.67 ⁇ D I / D O ⁇ 0.77 where D I is the distance between an inner end or leading edge 231 of the blade 230 and a center area of the rotation shaft of the motor 150, and D O is the distance between an outer end or trailing edge 234 of the blade and the center area of the rotation shaft of the motor 150.
  • the discharge pressure of the refrigerator centrifugal fan 200 falls within 5% of the maximum value and, when the ratio is not more than 0.67 and not less than 0.77, the discharge pressure of the refrigerator centrifugal fan 200 may sharply decrease. Accordingly, it is possible to increase the discharge pressure of the centrifugal fan 200 for a refrigerator under the same flow rate condition and increase the efficiency of the centrifugal fan 200 for a refrigerator.
  • the blade 230 may satisfy Equation 2 below. 0.67 ⁇ D I / D O ⁇ 0.72 where D I is the distance between an inner end or leading edge 231 of the blade 230 and a center area of the rotation shaft of the motor 150, and D O is the distance between an outer end or trailing edge 234 of the blade and the center area of the rotation shaft of the motor 150.
  • the discharge pressure of the refrigerator centrifugal fan 200 may be at its maximum. Accordingly, it is possible to maximize the discharge pressure of the centrifugal fan 200 for a refrigerator under the same flow rate condition and maximize the efficiency of the centrifugal fan 200 for a refrigerator.
  • the blade 230 may satisfy Equation 3 below. 0.25 ⁇ L 3 / L 2 ⁇ 0.3 where L3 is the maximum camber amount of the blade 230, and L2 is the cord length L2 of the blade 230.
  • the blade 230 may satisfy Equation 4 below.
  • L 3 / L 2 0.275 where L3 is the maximum camber amount of the blade 230, and L2 is the cord length L2 of the blade 230.
  • the discharge pressure of the centrifugal fan 200 for a refrigerator is at its maximum. Accordingly, it is possible to maximize the discharge pressure of the centrifugal fan 200 for a refrigerator under the same flow rate condition and maximize the efficiency of the centrifugal fan 200 for a refrigerator.
  • the blade may satisfy Equation 5 below. 044 ⁇ L 4 / L 2 ⁇ 0.58 where L4 denotes the maximum camber position L4 of the blade 230, and L2 denotes the cord length L2 of the blade 230.
  • the discharge pressure of the refrigerator centrifugal fan 200 falls within 5% of the maximum value and, when the ratio is not more than 0.44 and not less than 0.58, the discharge pressure of the refrigerator centrifugal fan 200 may sharply decrease. Accordingly, it is possible to increase the discharge pressure of the centrifugal fan 200 for a refrigerator under the same flow rate condition and increase the efficiency of the centrifugal fan 200 for a refrigerator.
  • the blade 230 may satisfy Equation 6 below.
  • L 4 / L 2 0.51 where L4 denotes the maximum camber position L4 of the blade 230, and L2 denotes the cord length L2 of the blade 230.
  • the discharge pressure of the centrifugal fan 200 for a refrigerator is at its maximum. Accordingly, it is possible to maximize the discharge pressure of the centrifugal fan 200 for a refrigerator under the same flow rate condition and maximize the efficiency of the centrifugal fan 200 for a refrigerator.
  • FIG. 11 is a perspective view illustrating a refrigerator centrifugal fan according to another embodiment of the disclosure.
  • FIG. 12 is a plan view illustrating a refrigerator centrifugal fan according to another embodiment of the disclosure.
  • FIG. 13 is an enlarged view of part B of FIG. 12 .
  • FIG. 14 is a cross-sectional view illustrating a refrigerator centrifugal fan according to another embodiment of the disclosure.
  • FIG. 15 is a graph illustrating the discharge pressure according to an angle between a cord line at a hub-side end of a blade and a cord line at a suction-side end according to another embodiment of the disclosure.
  • the centrifugal fan 200 for a refrigerator may include a hub 210, a blade 250, a connecting member 220, and a coupling part 240.
  • the refrigerator centrifugal fan 200 may include more or less components according to an embodiment.
  • a configuration not described below may be appreciated as substantially identical to the detailed configuration of the centrifugal fan 200 for a refrigerator according to an embodiment of the disclosure.
  • the inner diameter D T of a suction port (120a)-side end of the blades 250 may be smaller than the inner diameter D H of a hub-side end.
  • the blade 250 of the centrifugal fan 200 for a refrigerator may be manufactured by injection molding.
  • such a molded structure has two bodies, i.e., an upper body and a lower body, and when the two bodies are assembled together, an inner space corresponding to the shape of the centrifugal fan 200 for a refrigerator is formed.
  • a liquid resin e.g., plastic resin
  • the shape of the centrifugal fan 200 for a refrigerator is solidified.
  • an under-cut occurs, causing interference between components.
  • the inner diameter D T of the suction port (120a)-side end of the blades 250 is formed to be smaller than the inner diameter D H of the hub-side end, it is possible to prevent inter-component interference due to an under-cut.
  • a predetermined angle may be formed between the chord line CL1 at the suction-side end of the blade 250 and the chord line CL2 at the hub-side end.
  • the angle between the chord line CL1 at the suction-side end of the blade 250 and the chord line CL2 at the hub-side end may range from 18.7 degrees to 21 degrees.
  • the discharge pressure of the refrigerator centrifugal fan 200 may fall within 5% of the maximum value, and when the angle is not more than 18.7 degrees or not less than 21 degrees, the discharge pressure of the refrigerator centrifugal fan 200 may sharply decrease. Accordingly, it is possible to increase the discharge pressure of the centrifugal fan 200 for a refrigerator under the same flow rate condition and increase the efficiency of the centrifugal fan 200 for a refrigerator.
  • the angle between the chord line CL1 at the suction-side end of the blade 250 and the chord line CL2 at the hub-side end may be 19.8 degrees.
  • the discharge pressure of the refrigerator centrifugal fan 200 may be at its maximum. Accordingly, it is possible to maximize the discharge pressure of the centrifugal fan 200 for a refrigerator under the same flow rate condition and maximize the efficiency of the centrifugal fan 200 for a refrigerator.
  • FIG. 16 is a graph illustrating the discharge pressure according to the flow rate of a centrifugal fan for a refrigerator according to the prior art and according to an embodiment of the disclosure.
  • the graph for the prior art shows the results of a test performed using a conventional turbo fan with a diameter of 110 mm and a rotation speed of 1950 rpm
  • the graph shows the results of a test performed using the refrigerator centrifugal fan 200 with a diameter of 85 mm and a rotation speed of 1790 rpm.
  • centrifugal fan 200 for a refrigerator may increase the discharge pressure relative to the same flow rate.
  • component A described in connection with a particular embodiment and the drawings may be combined or merged with component B described in connection with another embodiment and the drawings.
  • component B described in connection with another embodiment and the drawings may be rendered possible unless stated as impossible.

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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)
  • Cold Air Circulating Systems And Constructional Details In Refrigerators (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP21155058.7A 2020-11-05 2021-02-03 Zentrifugalgebläse für kühlmaschine Pending EP3995698A1 (de)

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KR1020200146914A KR20220060844A (ko) 2020-11-05 2020-11-05 냉장고용 원심 팬

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Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2063365A (en) * 1979-10-08 1981-06-03 Punker Gmbh Radial Flow Fans
JP2003035293A (ja) * 2001-07-19 2003-02-07 Daikin Ind Ltd 遠心送風機の羽根車及びそれを備えた遠心送風機
KR100389395B1 (ko) 2000-09-05 2003-06-27 주식회사 엘지이아이 공기조화기용 터보팬
US20070217908A1 (en) * 2006-03-15 2007-09-20 Denso Corporation Centrifugal multiblade fan
FR2984971A1 (fr) * 2011-12-21 2013-06-28 Seb Sa Roue de ventilation centrifuge, ventilateur correspondant et appareil de cuisson incluant un tel ventilateur
DE102012021845A1 (de) * 2012-10-27 2014-04-30 Ebm-Papst St. Georgen Gmbh & Co. Kg Lüfter mit einem Lüfterrad
US20150056910A1 (en) * 2012-04-06 2015-02-26 Mitsubishi Electric Corporation Indoor unit for air-conditioning apparatus
US20150192143A1 (en) * 2012-06-26 2015-07-09 Denso Corporation Centrifugal multi-blade blower
KR101577875B1 (ko) 2013-12-30 2015-12-28 동부대우전자 주식회사 냉장고용 원심팬

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2063365A (en) * 1979-10-08 1981-06-03 Punker Gmbh Radial Flow Fans
KR100389395B1 (ko) 2000-09-05 2003-06-27 주식회사 엘지이아이 공기조화기용 터보팬
JP2003035293A (ja) * 2001-07-19 2003-02-07 Daikin Ind Ltd 遠心送風機の羽根車及びそれを備えた遠心送風機
US20070217908A1 (en) * 2006-03-15 2007-09-20 Denso Corporation Centrifugal multiblade fan
FR2984971A1 (fr) * 2011-12-21 2013-06-28 Seb Sa Roue de ventilation centrifuge, ventilateur correspondant et appareil de cuisson incluant un tel ventilateur
US20150056910A1 (en) * 2012-04-06 2015-02-26 Mitsubishi Electric Corporation Indoor unit for air-conditioning apparatus
US20150192143A1 (en) * 2012-06-26 2015-07-09 Denso Corporation Centrifugal multi-blade blower
DE102012021845A1 (de) * 2012-10-27 2014-04-30 Ebm-Papst St. Georgen Gmbh & Co. Kg Lüfter mit einem Lüfterrad
KR101577875B1 (ko) 2013-12-30 2015-12-28 동부대우전자 주식회사 냉장고용 원심팬

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