EP3922860B1 - Zentrifugalluftgebläse und klimaanlage damit - Google Patents

Zentrifugalluftgebläse und klimaanlage damit

Info

Publication number
EP3922860B1
EP3922860B1 EP19914580.6A EP19914580A EP3922860B1 EP 3922860 B1 EP3922860 B1 EP 3922860B1 EP 19914580 A EP19914580 A EP 19914580A EP 3922860 B1 EP3922860 B1 EP 3922860B1
Authority
EP
European Patent Office
Prior art keywords
rim
backing plate
cross
blade
centrifugal fan
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP19914580.6A
Other languages
English (en)
French (fr)
Other versions
EP3922860A4 (de
EP3922860A1 (de
Inventor
Atsushi Kono
Takuya Teramoto
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.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of EP3922860A1 publication Critical patent/EP3922860A1/de
Publication of EP3922860A4 publication Critical patent/EP3922860A4/de
Application granted granted Critical
Publication of EP3922860B1 publication Critical patent/EP3922860B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/301—Cross-sectional characteristics
    • 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
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/303—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the leading edge of a rotor blade

Definitions

  • the present disclosure relates to a centrifugal fan that changes the direction of flow of air sucked from a rim in a direction along a virtual rotation axis to a radial direction and blows the air radially and an air-conditioning apparatus including the centrifugal fan.
  • a developed centrifugal fan is configured such that an outside diameter defined by blades at a position closer to a backing plate than to the midpoint of a distance between the backing plate and a rim in a direction along a virtual rotation axis in an air outlet of the centrifugal fan is smaller than an outside diameter defined by the blades at a position closer to the rim than to the midpoint of the distance (refer to Patent Literature 1, for example).
  • a centrifugal fan which includes a plurality of blades having a three-dimensional shape, a main plate, an annular side plate, and a motor for rotating the blades via the main plate, wherein the radial length of a trailing edge of each blade at a part close to the main plate is set longer than the radial length of the trailing edge of each blade at a part close to the side plate (refer to Patent Literature 2, for example).
  • a typical centrifugal fan incudes a backing plate having a boss connected to a rotating shaft of a motor, a rim functioning as a suction guide wall, and a plurality of blades arranged between the backing plate and the rim, and has a structure in which air is sucked in a direction along the rotating shaft, the direction of flow of the air is changed to the radial direction, and the air is blown radially out of the fan.
  • centrifugal fan While the centrifugal fan is driven, an air flow tends to be located closer to the backing plate than to the midpoint of a distance between the backing plate and the rim in the direction along the rotating shaft in an air outlet of the centrifugal fan, causing a pressure loss due to a high-velocity air flow in a region adjacent to the backing plate. This tends to lead to lower fan efficiency.
  • the centrifugal fan has the property that the above-described tendency is notably observed when the centrifugal fan is installed in an air passage with a low air flow resistance.
  • an air flow in the centrifugal fan does not tend to be located closer to the rim than to the midpoint of the distance between the backing plate and the rim in the direction along the rotating shaft in the air outlet of the centrifugal fan. Therefore, the amount of work by parts of the blades that are adjacent to the rim is smaller than that adjacent to the backing plate.
  • an outside diameter defined by the blades at a position closer to the rim than to the midpoint of the distance between the backing plate and the rim in a direction along the virtual rotation axis in the air outlet of the centrifugal fan is larger than an outside diameter defined by the blades at a position closer to the backing plate than to the midpoint of the distance between the backing plate and the rim in the direction along the virtual rotation axis in the air outlet.
  • the present disclosure is intended to solve the above-described problem and aims to provide a centrifugal fan with a uniform distribution of velocity of air to be blown and an air-conditioning apparatus including the centrifugal fan.
  • An embodiment of the present disclosure provides a centrifugal fan including inter alia: a backing plate to be rotated, a ring-shaped rim facing the backing plate, and a plurality of blades arranged to surround a virtual rotation axis of the backing plate, the plurality of blades being arranged between the backing plate and the rim and each having an inner edge and an outer edge, wherein a blade chord distance has a maximum at one of first cross-sections that is located closer to the rim than to a middle cross-section where the first cross-sections are cross-sections of each of the plurality of blades in planes parallel to the backing plate, the blade chord distance is a linear distance between the inner edge and the outer edge of each of the plurality of blades in each of the first cross-sections, and the middle cross-section is one of the first cross-sections that has an intersection of the outer edge with a plane perpendicular to the virtual rotation
  • the blade chord distance has a maximum at one of the first cross-sections that is located closer to the rim than to the middle cross-section, which is one of the first cross-sections that has an intersection of the outer edge with a plane perpendicular to the virtual rotation axis, the plane being at the middle of the axial opening dimension of the air outlet in a direction along the virtual rotation axis.
  • an air flow tends to be located closer to a backing plate than to a rim.
  • the blade chord distance at a cross-section adjacent to the rim is larger than that at a cross-section adjacent to the backing plate, thus making the area of parts of the blades that are adjacent to the rim larger than the area of parts of the blades that are adjacent to the backing plate. This results in an increase in air flow velocity in a region adjacent to the rim, leading to a uniform distribution of velocity of air to be blown from the fan.
  • Embodiment 1 is useful for understanding the claimed invention
  • Embodiment 2 is according to the claimed invention
  • Embodiments 3-5 show optional further features of the claimed invention.
  • a centrifugal fan 100 and an air-conditioning apparatus 200 will be described below with reference to the drawings.
  • components designated by the same reference signs in the following drawings are the same components or equivalents. This note applies to the entire description herein.
  • terms representing directions, such as “upper”, “lower”, “rightward”, “leftward”, “front”, and “rear”, will be used as appropriate. These terms are used herein only for the purpose of convenience of description and are not intended to restrict the location and orientation of the apparatus or part.
  • Fig. 1 is a perspective view of a centrifugal fan 100 according to Embodiment 1 of the present disclosure.
  • Fig. 2 is a side view of the centrifugal fan 100 according to Embodiment 1 of the present disclosure.
  • a fundamental structure of the centrifugal fan 100 will be described with reference to Figs. 1 and 2 .
  • the centrifugal fan 100 is rotated by, for example, a motor (not illustrated), and is configured to force air to be sent radially outward by using a centrifugal force produced by rotation.
  • the centrifugal fan 100 includes a backing plate 10, which is a rotating part, a substantially ring-shaped rim 20 facing the backing plate 10, and a plurality of blades 30 arranged between the backing plate 10 and the rim 20.
  • the backing plate 10 is a rotating part that rotates about a virtual rotation axis RS.
  • the backing plate 10 is circular as viewed in projection along the virtual rotation axis RS of the centrifugal fan 100.
  • a radially inner portion of the backing plate 10 has a substantially conical shape, or protrudes like a mountain toward the rim 20.
  • the backing plate 10 has a sloping surface that slopes from the center toward the periphery in a direction away from an air inlet 102, which will be described later.
  • the backing plate 10 includes a boss 12 at the center of the backing plate 10, or the top of the mountain-like portion.
  • the boss 12 is part to which a rotating shaft of the motor (not illustrated) is secured.
  • the boss 12 is connected to the rotating shaft of the motor.
  • the backing plate 10 is rotated about the virtual rotation axis RS by driving the motor (not illustrated).
  • the virtual rotation axis RS is the virtual rotation axis of the centrifugal fan 100 as well as the virtual rotation axis of the backing plate 10.
  • the backing plate 10 is a rotating part including the boss 12.
  • the shape of the backing plate 10 is not limited to a substantially conical shape that is circular as viewed in projection along the virtual rotation axis RS and protrudes like a mountain.
  • the backing plate 10 may have any other shape.
  • the backing plate 10 may be disc-shaped or may be substantially flat and polygonal as viewed in projection along the virtual rotation axis RS.
  • the backing plate 10 may be shaped such that the radially inner portion of the backing plate 10 protrudes like a mountain and a radially outer portion of the backing plate 10, or annular peripheral part of the radially inner protruding portion, is substantially flat.
  • the rim 20 faces the backing plate 10.
  • the rim 20 is a ring having a substantially arc-shaped section and functions as a suction guide wall.
  • the rim 20 is a shroud.
  • the rim 20 is ring-shaped as viewed in projection along the virtual rotation axis RS of the centrifugal fan 100.
  • the rim 20 protrudes inwardly from its radially outer edge to have a mountain-like shape.
  • the air inlet 102 is located at the center of the rim 20. More specifically, the rim 20 has an inner circumferential edge or end 22, which defines the air inlet 102 of the centrifugal fan 100, and has a radially inwardly curved surface such that the diameter increases from the air inlet 102 toward the backing plate 10.
  • the rim 20 has an outside diameter OS, which is larger than an outside diameter OM of the backing plate 10.
  • the configuration of the centrifugal fan 100 is not limited to the above-described configuration in which the outside diameter OS of the rim 20 is larger than the outside diameter OM of the backing plate 10.
  • the outside diameter OS of the rim 20 may be equal to the outside diameter OM of the backing plate 10 or may be smaller than the outside diameter OM of the backing plate 10.
  • the rim 20 connects the blades 30 to maintain the positional relationship of leading edges of the blades 30 and enhance the strengths of the blades 30.
  • the backing plate 10 is disposed at a distance from the rim 20 in a direction along the virtual rotation axis RS.
  • the centrifugal fan 100 has an air outlet 104 defined between the rim periphery 24 of the rim 20 and a backing-plate periphery 14 of the backing plate 10 such that the air outlet 104 is located between the rim periphery 24 and the backing-plate periphery 14.
  • the rim periphery 24 is a radially outer end of the rim 20 and constitutes the outer circumferential edge of the rim 20.
  • the backing-plate periphery 14 is a radially outer end of the backing plate 10 and constitutes an outer circumferential edge of the backing plate 10.
  • the air outlet 104 is an opening through which air sucked into the centrifugal fan 100 through the air inlet 102 is discharged by rotation of the centrifugal fan 100.
  • the blades 30 rotate together with the backing plate 10 during rotation of the backing plate 10 and create a current of air flowing from the center of the backing plate 10 to the periphery thereof.
  • the blades 30 are arranged between the backing plate 10 and the rim 20.
  • One end of each of the blades 30 in the direction along the virtual rotation axis RS of the centrifugal fan 100 is joined to the backing plate 10.
  • the other end thereof is joined to the rim 20.
  • the blades 30 are arranged on a circumference about the virtual rotation axis RS and are regularly spaced apart from each other along the circumference of the backing plate 10.
  • the blades 30 extend rearward in a rotation direction R in which the backing plate 10 rotates.
  • Each of the blades 30 has an inner edge 31 and an outer edge 32 such that the inner edge 31 is located closer to the virtual rotation axis RS than the outer edge 32.
  • the inner edge 31 is a leading edge of the blade 30.
  • the outer edge 32 is a trailing edge of the blade 30.
  • Each of the inner edges 31 of the blades 30 is located at a predetermined distance from the virtual rotation axis RS.
  • Each of the outer edges 32 is located in proximity to the backing-plate periphery 14 and the rim periphery 24.
  • a virtual extension of a chord that is a straight line connecting the inner edge 31 and the outer edge 32 of each blade 30 extends so as not to pass through the virtual rotation axis RS.
  • the inner edge 31 is located forward of a virtual radial line connecting the virtual rotation axis RS and the outer edge 32 in the rotation direction R.
  • a blade outer surface 30a is a surface of the blade remote from the virtual rotation axis RS.
  • the distance of the blade outer surface 30a from the virtual rotation axis RS increases toward the trailing edge in the rotation direction R.
  • a blade inner surface 30b is a surface of the blade adjacent to the virtual rotation axis RS.
  • the distance of the blade inner surface 30b from the virtual rotation axis RS increases toward the trailing edge in the rotation direction R such that a predetermined distance is kept between the blade inner surface 30b and the blade outer surface 30a.
  • the blade 30 has a thickness, which corresponds to the predetermined distance, gradually decreasing from the middle of the blade 30 toward the inner edge 31 and the outer edge 32.
  • the blade 30 has a cross-section in a plane perpendicular to the virtual rotation axis RS and the cross-section resembles that of a typical wing.
  • a blade outside diameter OW of the centrifugal fan 100 in a region AS between the rim 20 and a middle HB of an axial opening dimension of the air outlet 104 in the direction along the virtual rotation axis RS is larger than the blade outside diameter OW at the middle HB. Furthermore, the blade outside diameter OW of the centrifugal fan 100 in a region AM between the backing plate 10 and the middle HB of the axial opening dimension of the air outlet 104 in the direction along the virtual rotation axis RS is smaller than the blade outside diameter OW at the middle HB.
  • the centrifugal fan 100 has a maximum blade outside diameter OW at a position closer to the rim 20 than to the middle HB of the axial opening dimension of the air outlet 104 in the direction along the virtual rotation axis RS, and has a minimum blade outside diameter OW at a position closer to the backing plate 10 than to the middle HB of the axial opening dimension of the air outlet 104 in the direction along the virtual rotation axis RS.
  • the axial opening dimension of the air outlet 104 in the direction along the virtual rotation axis RS is a distance between the backing-plate periphery 14 of the backing plate 10 and the rim periphery 24 of the rim 20 in the direction along the virtual rotation axis RS.
  • the blade outside diameter OW is a diameter of a portion including the blades 30 of the centrifugal fan 100.
  • the blade outside diameter OW is a diameter of a rotation circle defined by the outer edges 32 of the blades 30 during rotation of the centrifugal fan 100 while the centrifugal fan 100 is operated.
  • Fig. 3 is a schematic diagram illustrating the backing plate 10, the rim 20, and one blade 30 of the centrifugal fan 100 in Fig. 2 as viewed from the side.
  • Fig. 4 is a schematic diagram illustrating a cross-section CS of the blade 30 in a plane parallel to the backing plate 10 of the centrifugal fan 100 according to Embodiment 1 of the present disclosure as viewed in the direction along the virtual rotation axis RS.
  • Fig. 5 is a graph illustrating the relationship between a blade chord distance Da between the inner edge 31 and the outer edge 32 of the blade 30 at a cross-section parallel to the backing plate 10 of the centrifugal fan 100 according to Embodiment 1 of the present disclosure and the position of a cross-section CS of the blade 30.
  • Fig. 3 illustrates only one blade 30 of the blades 30 and depiction of the other blades 30 is omitted to reveal the geometry of the blade 30.
  • Cross-sections CS of the blade 30 in planes parallel to the backing plate 10 are defined as first cross-sections of the blade 30.
  • the blade chord distance Da is defined as a linear distance between the inner edge 31 and the outer edge 32 of each of the blades 30, arranged to surround the virtual rotation axis RS of the backing plate 10, in each of the cross-sections CS of each of the blades 30 in planes parallel to the backing plate 10. Since the backing plate 10 of the centrifugal fan 100 according to Embodiment 1 of the present disclosure is substantially conical, a plane parallel to the backing plate 10 is a substantially conical plane. In Fig. 3 , broken lines illustrate the positions of cross-sections CS of the blade 30 in planes parallel to the backing plate 10.
  • a cross-section CS having an intersection of the outer edge 32 with a plane F, which is perpendicular to the virtual rotation axis RS and is at the middle HB of the axial opening dimension of the air outlet 104 in the direction along the virtual rotation axis RS, is defined as a middle cross-section MS.
  • the blade chord distance Da has a maximum at one of the cross-sections CS that is located closer to the rim 20 than to the middle cross-section MS.
  • the blade chord distance Da between the inner edge 31 and the outer edge 32 of each blade 30 increases from the backing plate 10 toward the rim 20, reaches a maximum at a position closer to the rim 20 than to the middle HB between the backing plate 10 and the rim 20, and then decreases toward the rim 20.
  • the blades 30 secured to the backing plate 10 circumferentially move about the virtual rotation axis RS.
  • the rotation of the backing plate 10 in the rotation direction R causes air outside the centrifugal fan 100 to be sucked into a space defined by the backing plate 10, the rim 20, and the blades 30 through the air inlet 102.
  • the blades 30 rotate together with the backing plate 10, causing the air sucked into the space defined by the backing plate 10 and the blade 30 to pass through spaces between the adjacent blades 30 and be sent outward in a radial direction of the backing plate 10.
  • the blade chord distance Da has a maximum at one of the cross-sections CS that is located closer to the rim 20 than to the middle cross-section MS.
  • an air flow tends to be located closer to a backing plate than to a rim.
  • the blade chord distance Da of each blade 30 at a cross-section adjacent to the rim 20 is larger than that at a cross-section adjacent to the backing plate 10 such that the area of blade part adjacent to the rim 20 is larger than the area of blade part adjacent to the backing plate 10, resulting in an increase in air flow velocity in a region adjacent to the rim 20. This leads to a uniform distribution of velocity of air to be blown from the fan.
  • the outside diameter defined by the blades 30 at a position adjacent to the rim 20 is larger than that at a position adjacent to the backing plate 10, thus increasing the amount of work by parts of the blades 30 that are adjacent to the rim 20.
  • the uniform distribution of velocity of air to be blown from the centrifugal fan 100 results in a reduction in pressure loss in a high-velocity air flow region caused by an uneven air flow, leading to improved fan efficiency.
  • the blade chord distance Da between the inner edge 31 and the outer edge 32 of each blade 30 increases from the backing plate 10 toward the rim 20, reaches a maximum at a position closer to the rim 20 than to the middle HB between the backing plate 10 and the rim 20, and then decreases toward the rim 20.
  • a reduction in blade chord distance Da in a region in proximity to the rim 20 can reduce or eliminate noise that arises from a collision between turbulent air flows caused by a wake downstream of a bell mouth connected to the rim 20 and a leakage flow of air entering a gap between the bell mouth and the rim 20.
  • Fig. 6 is a cross-sectional view of a blade 30 in a plane perpendicular to the virtual rotation axis RS of a centrifugal fan 100 according to Embodiment 2 of the present disclosure, which is an embodiment according to the invention.
  • Fig. 7 is a side schematic diagram of the centrifugal fan 100 according to Embodiment 2 of the present disclosure.
  • Fig. 8 is a graph illustrating the relationship between an inlet angle ⁇ of the blade 30 of the centrifugal fan 100 according to Embodiment 2 of the present disclosure and the position of a cross-section CR.
  • Fig. 6 is a cross-sectional view of a blade 30 in a plane perpendicular to the virtual rotation axis RS of a centrifugal fan 100 according to Embodiment 2 of the present disclosure, which is an embodiment according to the invention.
  • Fig. 7 is a side schematic diagram of the centrifugal fan 100 according to Embodiment 2 of the present disclosure.
  • FIG. 9 is a cross-sectional view of the blade 30 in a plane perpendicular to the virtual rotation axis RS of the centrifugal fan 100 at a position Pb in Figs. 7 and 8 .
  • Fig. 10 is a cross-sectional view of the blade 30 in a plane perpendicular to the virtual rotation axis RS of the centrifugal fan 100 at a position Pc in Figs. 7 and 8 .
  • Fig. 11 is a cross-sectional view of the blade 30 in a plane perpendicular to the virtual rotation axis RS of the centrifugal fan 100 at a position Pd in Figs. 7 and 8 .
  • the centrifugal fan 100 according to Embodiment 2 is obtained by further determining details of the geometry of each blade 30 in the centrifugal fan 100 according to Embodiment 1. The following description will focus on the geometry of each blade 30 of the centrifugal fan 100 according to Embodiment 2 of the present disclosure.
  • the blade 30 of the centrifugal fan 100 according to Embodiment 2 will be described with reference to Figs. 6 to 11 .
  • the inlet angle ⁇ of the blade 30 is defined as an angle formed by a center line CL of the blade 30 and a tangent TL1 to a virtual circle C1, which has a center at the virtual rotation axis RS and intersects a leading edge 35 of the blade 30, at the leading edge 35.
  • the cross-sections CR of each of the blades 30 in planes perpendicular to the virtual rotation axis RS of the backing plate 10 are defined as second cross-sections of the blade 30. As illustrated in Figs.
  • the inlet angle ⁇ of each blade 30 has a minimum at one of the cross-sections CR that is located closer to the rim 20 than a middle Pm of the leading edge 35 of the blade 30 between the backing plate 10 and the rim 20. More specifically, as represented by an inlet angle ⁇ 1 at the position Pb and an inlet angle ⁇ 2 at the position Pc, the inlet angle ⁇ of the blade 30 decreases from the backing plate 10 toward the rim 20 and reaches a minimum at a position closer to the rim 20 than the middle Pm between the backing plate 10 and the rim 20.
  • the inlet angle ⁇ of the blade 30 increases from the position Pc with the inlet angle ⁇ 2, which is a minimum, toward the rim 20.
  • the middle Pm of the leading edge 35 between the backing plate 10 and the rim 20 is the middle of a dimension along the leading edge 35 between the backing plate 10 and the rim 20.
  • the inlet angle ⁇ of each blade 30 has a minimum at one of the cross-sections CR that is located closer to the rim 20 than the middle Pm of the leading edge 35 of the blade 30 between the backing plate 10 and the rim 20.
  • a reduction in inlet angle ⁇ at a position closer to the rim 20 than the middle Pm reduces air flow separation at the leading edge 35 of the blade 30, resulting in an increase in air flow velocity in a region adjacent to the rim 20. This leads to a more uniform distribution of velocity of air to be blown from the fan.
  • the inlet angle ⁇ of each blade 30 increases from the position Pc with the inlet angle ⁇ 2, which is a minimum, toward the rim 20.
  • a leakage flow of air entering a gap between a rim 20 and a bell mouth connected to the rim 20 is likely to occur in proximity to the rim 20.
  • Such a leakage air flow which includes a component rotating in the rotation direction R of the centrifugal fan 100, enters the centrifugal fan.
  • an increase in inlet angle ⁇ at a position in proximity to the rim 20 can reduce or eliminate a pressure loss caused by air flow separation at the leading edge 35 of each blade 30.
  • Fig. 12 is a cross-sectional view of a blade 30 in a plane perpendicular to the virtual rotation axis RS of a centrifugal fan 100 according to Embodiment 3 of the present disclosure.
  • Fig. 13 is a graph illustrating the relationship between a camber height H of the blade 30 of the centrifugal fan 100 according to Embodiment 3 of the present disclosure and the position of a cross-section CR.
  • the same components and parts as those in the centrifugal fans 100 in Figs. 1 to 11 are designated by the same reference signs and a description of these components and parts is omitted.
  • the centrifugal fan 100 according to Embodiment 3 is obtained by further determining details of the geometry of each blade 30 in the centrifugal fan 100 according to Embodiment 1 or Embodiment 2. The following description will focus on the geometry of each blade 30 of the centrifugal fan 100 according to Embodiment 3 of the present disclosure. The geometry of the blade 30 of the centrifugal fan 100 according to Embodiment 3 will be described with reference to Figs. 12 and 13 .
  • the camber height H is defined as a perpendicular distance from the center line CL of each blade 30 to a straight line SL connecting the leading edge 35 and a trailing edge 36 of the blade 30 in each cross-section CR of the blade 30 in a plane perpendicular to the virtual rotation axis RS.
  • the camber height H is zero at the leading edge 35 of the blade 30 and the trailing edge 36 of the blade 30.
  • the cross-section CR of the blade 30 includes an outer curve having a large curvature and an inner curve having a small curvature or a straight line.
  • a maximum camber height H is located closer to the trailing edge 36 than a midpoint CM of a linear distance between the leading edge 35 and the trailing edge 36.
  • the term “outer” refers to being adjacent to the trailing edge 36 and the term “inner” refers to being adjacent to the leading edge 35.
  • the camber height H of each blade 30 has a maximum at one of the cross-sections CR that is located closer to the rim 20 than to the middle Pm of the leading edge 35 of the blade 30 between the backing plate 10 and the rim 20.
  • the maximum camber height Ha of the entire blade 30 is located closer to the rim 20 than to the middle Pm between the backing plate 10 and the rim 20.
  • the camber height H of the blade 30 increases from the backing plate 10 toward the rim 20 and reaches a maximum at a position closer to the rim 20 than to the middle Pm between the backing plate 10 and the rim 20. Then, the camber height H of the blade 30 decreases from the position of the cross-section CR with the maximum camber height toward the rim 20.
  • the camber height H of each blade 30 of the centrifugal fan 100 has a maximum at one of the cross-sections CR that is located closer to the rim 20 than to the middle Pm between the backing plate 10 and the rim 20.
  • the camber height H at a position closer to the rim 20 than to the middle Pm between the backing plate 10 and the rim 20 is larger than that at the middle Pm, thus increasing the amount of work by parts of the blades that are adjacent to the rim 20. This results in an increase in air flow velocity in a region adjacent to the rim 20, leading to a more uniform distribution of velocity of air to be blown from the fan.
  • the camber height H of each blade 30 in the centrifugal fan 100 according to Embodiment 3 of the present disclosure decreases from the position of the cross-section CR with the maximum camber height toward the rim 20.
  • a region in proximity to the rim 20 of the centrifugal fan 100 according to Embodiment 3 of the present disclosure tends to experience air flow separation because the blade chord distance Da between the inner edge 31 and the outer edge 32 of each blade 30 decreases in this region.
  • a reduction in camber height H can reduce air flow separation.
  • Fig. 14 is a cross-sectional view of a blade 30 in a plane perpendicular to the virtual rotation axis RS of a centrifugal fan 100 according to Embodiment 4 of the present disclosure.
  • Fig. 15 is a side schematic diagram of the centrifugal fan 100 according to Embodiment 4 of the present disclosure.
  • Fig. 16 is a graph illustrating the relationship between an outlet angle ⁇ of the blade 30 of the centrifugal fan 100 according to Embodiment 4 of the present disclosure and the position of a cross-section CR.
  • Fig. 17 is a cross-sectional view of the blade 30 in a plane perpendicular to the virtual rotation axis RS of the centrifugal fan 100 at a position Pe in Figs.
  • Fig. 18 is a cross-sectional view of the blade 30 in a plane perpendicular to the virtual rotation axis RS of the centrifugal fan 100 at a position Pf in Figs. 15 and 16 .
  • Fig. 19 is a cross-sectional view of the blade 30 in a plane perpendicular to the virtual rotation axis RS of the centrifugal fan 100 at a position Pg in Figs. 15 and 16 .
  • the same components and parts as those in the centrifugal fans 100 in Figs. 1 to 13 are designated by the same reference signs and a description of these components and parts is omitted.
  • the centrifugal fan 100 according to Embodiment 4 is obtained by further determining details of the geometry of each blade 30 in the centrifugal fan 100 according to Embodiment 1. The following description will focus on the geometry of each blade 30 of the centrifugal fan 100 according to Embodiment 4 of the present disclosure.
  • the blade 30 of the centrifugal fan 100 according to Embodiment 4 will be described with reference to Figs. 14 to 19 .
  • the outlet angle ⁇ of the blade 30 is defined as an angle formed by the center line CL of the blade 30 and a tangent TL2 to a virtual circle C2, which has a center at the virtual rotation axis RS and intersects the trailing edge 36 of the blade 30, at the trailing edge 36.
  • the outlet angle ⁇ of the blade 30 increases from the backing plate 10 toward the rim 20 as represented by an outlet angle ⁇ 1 at the position Pe, an outlet angle ⁇ 2 at the position Pf, and an outlet angle ⁇ 3 at the position Pg.
  • the outlet angle ⁇ of each blade 30 at one of the cross-sections CR that is located closer to the rim 20 than to the middle Pf of the trailing edge 36 of the blade 30 between the backing plate 10 and the rim 20 is larger than the outlet angle ⁇ thereof at one of the cross-sections CR that is located closer to the backing plate 10 than to the middle Pf.
  • the middle Pf of the trailing edge 36 between the backing plate 10 and the rim 20 is the middle of a dimension along the trailing edge 36 between the backing plate 10 and the rim 20.
  • the outlet angle ⁇ of each blade 30 increases from the backing plate 10 toward the rim 20.
  • the outlet angle ⁇ at a position adjacent to the rim 20 is larger than that at a position adjacent to the backing plate 10, thus increasing the amount of work by parts of the blades 30 that are adjacent to the rim 20. This results in an increase in air flow velocity in a region adjacent to the rim 20, leading to a more uniform distribution of velocity of air to be blown from the fan.
  • the outside diameter defined by the blades at a position adjacent to the rim 20 is larger than that at a position adjacent to the backing plate 10, resulting in an increase in air flow in a region adjacent to the rim 20. Therefore, air flow separation from the blade surfaces can be reduced even though the outlet angle ⁇ increases toward the rim 20.
  • Fig. 20 is a sectional view of the air-conditioning apparatus 200, which includes the centrifugal fan 100, according to Embodiment 5 of the present disclosure.
  • the air-conditioning apparatus 200 is of a floor-standing type.
  • the type of air-conditioning apparatus 200 is not limited to the floor-standing type.
  • the air-conditioning apparatus 200 may be of any other type, such as a ceiling concealed type.
  • the air-conditioning apparatus 200 includes a casing 210, which constitutes a shell of the air-conditioning apparatus 200, a heat exchanger 220 disposed in the casing 210, and the centrifugal fan 100 disposed in the casing 210 and configured to create a current of air passing through the heat exchanger 220.
  • the casing 210 has a rectangular cuboid shape.
  • the shape of the casing 210 is not limited to a rectangular cuboid shape.
  • the casing 210 may have any other shape, such as a cylindrical shape, a rectangular columnar shape, a conical shape, a shape with multiple corners, or a shape with multiple curved surfaces.
  • the casing 210 has an upper surface 211 having an air inlet 212.
  • the casing 210 has a lower surface 213 having an air outlet 214.
  • the air inlet 212 is an opening through which air is sucked into the casing 210 from the outside by operation of the centrifugal fan 100.
  • the air outlet 214 is an opening though which air is discharged from the casing 210 to the outside by operation of the centrifugal fan 100.
  • the positions of the air inlet 212 and the air outlet 214 are not limited to those in the above-described configuration.
  • the air inlet 212 and the air outlet 214 may be located in the same surface.
  • either one of the air inlet 212 and the air outlet 214 may be located in one side.
  • the casing 210 contains the centrifugal fan 100 and the heat exchanger 220.
  • An internal space of the casing 210 is divided into a space S11 containing the heat exchanger 220 and a space S12 containing the centrifugal fan 100 by a partition 215.
  • the casing 210 contains electric equipment 250 for control of the air-conditioning apparatus 200.
  • the centrifugal fan 100 creates a current of air such that the air is sucked into the casing 210 through the air inlet 212 of the casing 210 and is then blown to an air-conditioned space through the air outlet 214 of the casing 210.
  • the centrifugal fan 100 has a bell mouth 230.
  • the bell mouth 230 is disposed between the partition 215 and the centrifugal fan 100.
  • the centrifugal fan 100 is connected to a motor 240.
  • the motor 240 is supported by a motor support 241 secured to the lower surface 213 of the casing 210.
  • the motor 240 includes an output shaft 242.
  • the boss 12 of the centrifugal fan 100 is attached to the output shaft 242 of the motor 240.
  • the number of centrifugal fans 100 in the casing 210 is not limited to one. Multiple centrifugal fans may be arranged in the casing.
  • the heat exchanger 220 is disposed upstream of the centrifugal fan 100 in an air flow direction in which the air current created by the centrifugal fan 100 flows in the casing 210.
  • the heat exchanger 220 adjusts the temperature of air that is sucked into the casing 210 through the air inlet 212 of the casing 210 and is then blown to the air-conditioned space through the air outlet 214.
  • the heat exchanger 220 having a known structure can be used.
  • a removable filter 221 is disposed upstream of the heat exchanger 220 in the air flow direction in which the air current created by the centrifugal fan 100 flows in the casing 210.
  • the filter 221 removes dust from air that is to pass through the heat exchanger 220.
  • a drain pan 222 to collect condensate water is disposed under the heat exchanger 220.
  • the air-conditioning apparatus 200 includes any one of the centrifugal fans 100 according to Embodiments 1 to 4. Such a configuration can provide a uniform distribution of velocity of air to be blown, leading to improved fan efficiency. Furthermore, this configuration, in which any one of the centrifugal fans 100 according to Embodiments 1 to 4 is included, can reduce or eliminate noise that arises from a collision between turbulent air flows caused by a wake downstream of the bell mouth and a leakage flow of air entering the gap between the bell mouth and the rim 20.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (6)

  1. Zentrifugallüfter (100), umfassend:
    eine zu drehende Trägerplatte (10),
    einen ringförmigen Rand (20), der der Trägerplatte (10) zugewandt ist, und
    eine Vielzahl von Flügeln (30), die so angeordnet sind, dass sie eine virtuelle Drehachse (RS) der Trägerplatte (10) umgeben, wobei die Vielzahl von Flügeln (30) zwischen der Trägerplatte (10) und dem Rand (20) angeordnet sind und jeweils eine Innenkante (31) und eine Außenkante (32) aufweisen,
    wobei eine Flügelsehnenlänge (Da) ein Maximum an einem von ersten Querschnitten (CS) aufweist, der näher am Rand (20) als an einem mittleren Querschnitt (MS) angeordnet ist,
    wobei
    die ersten Querschnitte (CS) Querschnitte jeder der Vielzahl von Flügeln (30) in Ebenen sind, die parallel zur Trägerplatte (10) verlaufen,
    die Flügelsehnenlänge (Da) ein linearer Abstand zwischen der Innenkante (31) und der Außenkante (32) eines jeden der Vielzahl von Flügeln (30) in jedem der ersten Querschnitte (CS) ist, und
    der mittlere Querschnitt (MS) einer der ersten Querschnitte (CS) ist, der einen Schnittpunkt der Außenkante (32) mit einer Ebene (F) senkrecht zur virtuellen Drehachse (RS) aufweist, wobei sich die Ebene in einer Mitte einer axialen Öffnungsabmessung eines Luftauslasses (104) befindet, der zwischen einem Umfang (24) des Randes (20) und einem Umfang (14) der Trägerplatte (10) definiert ist, wobei die axiale Öffnungsabmessung als eine Abmessung entlang der virtuellen Drehachse (RS) definiert ist,
    der Flügelsehnenabstand (Da) von der Trägerplatte (10) zum Rand (20) hin zunimmt, ein Maximum an einer Position erreicht, die näher an dem Rand (20) als am mittleren Querschnitt (MS) zwischen der Trägerplatte (10) und dem Rand (20) liegt, und dann zum Rand (20) hin abnimmt,
    dadurch gekennzeichnet, dass
    ein Einlasswinkel (α) jedes der Vielzahl von Flügeln (30) ein Minimum an einem von zweiten Querschnitten (CR) aufweist, der näher an dem Rand (20) als eine Mitte einer Vorderkante (35) jedes der Vielzahl von Flügeln (30) zwischen der Trägerplatte (10) und dem Rand (20) angeordnet ist, wobei die zweiten Querschnitte (CR) Querschnitte jedes der Vielzahl von Flügeln (30) in Ebenen senkrecht zur virtuellen Drehachse (RS) sind,
    wobei in jedem Querschnitt (CR) von jedem der Flügel (30) in einer Ebene senkrecht zur virtuellen Drehachse (RS) der Trägerplatte (10) der Einlasswinkel (α) des Flügels (30) als ein Winkel definiert ist, der durch eine Mittellinie (CL) des Flügels (30) und eine Tangente (TL1) an einen virtuellen Kreis (C1) gebildet wird, der ein Zentrum an der virtuellen Drehachse (RS) aufweist und die Vorderkante (35) des Flügels (30) an der Vorderkante (35) schneidet.
  2. Zentrifugallüfter (100) nach Anspruch 1, wobei der Einlasswinkel (α) von einer Position des zweiten Querschnitts mit dem minimalen Einlasswinkel (α) zum Rand (20) hin zunimmt.
  3. Zentrifugallüfter (100) nach Anspruch 1 oder 2, wobei eine Wölbungshöhe (H) ein Maximum an einem der zweiten Querschnitte (CR) aufweist, der näher an dem Rand (20) als an der Mitte der Vorderkante (35) jedes der Vielzahl von Flügeln (30) zwischen der Trägerplatte (10) und dem Rand (20) angeordnet ist,
    wobei die Wölbungshöhe (H) ein senkrechter Abstand von einer Mittellinie jeder der Vielzahl von Flügeln (30) zu einer geraden Linie ist, die die Vorderkante (35) und eine Hinterkante (36) jedes der Vielzahl von Flügeln (30) in jedem der zweiten Querschnitte (CR) verbindet.
  4. Zentrifugallüfter (100) nach Anspruch 3, wobei die Wölbungshöhe (H) von einer Position des zweiten Querschnitts mit der maximalen Wölbungshöhe (H) zum Rand (20) hin abnimmt.
  5. Zentrifugallüfter (100) nach Ansprüchen 1-4,
    wobei ein Auslasswinkel (β) jedes der Vielzahl von Flügeln (30) an einem der zweiten Querschnitte (CR), der näher an dem Rand (20) als eine Mitte einer Hinterkante (36) jedes der Vielzahl von Flügeln (30) zwischen der Trägerplatte (10) und dem Rand (20) angeordnet ist, größer ist als der Auslasswinkel (β) an einem der zweiten Querschnitte (CR), der näher an der Trägerplatte (10) als die Mitte der Hinterkante (36) angeordnet ist,
    wobei in jedem Querschnitt (CR) von jedem der Flügel (30) in einer Ebene senkrecht zur virtuellen Drehachse (RS) der Trägerplatte (10) der Auslasswinkel (β) des Flügels (30) als ein Winkel definiert ist, der durch die Mittellinie (CL) des Flügels (30) und eine Tangente (TL2) an einen virtuellen Kreis (C2) gebildet wird, der ein Zentrum an der virtuellen Drehachse (RS) aufweist und die Hinterkante (36) des Flügels (30) an der Hinterkante (36) schneidet.
  6. Klimaanlage (200), umfassend:
    den Zentrifugallüfter (100) nach einem der Ansprüche 1 bis 5, und einen Wärmetauscher (220).
EP19914580.6A 2019-02-07 2019-02-07 Zentrifugalluftgebläse und klimaanlage damit Active EP3922860B1 (de)

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CN111878455B (zh) * 2020-09-17 2024-11-12 珠海格力电器股份有限公司 离心叶轮、离心风机及制冷设备
CN115405560A (zh) * 2022-08-15 2022-11-29 卧龙电气驱动集团股份有限公司 一种离心叶轮及风机
WO2025088698A1 (ja) * 2023-10-24 2025-05-01 三菱電機株式会社 遠心送風機およびこれを備えた空気調和装置

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JP3260544B2 (ja) * 1994-04-06 2002-02-25 松下精工株式会社 多翼ファン
JP2000146214A (ja) * 1998-11-02 2000-05-26 Matsushita Refrig Co Ltd 空気調和機
EP2275689A1 (de) * 2008-05-14 2011-01-19 Daikin Industries, Ltd. Zentrifugalgebläse
JP5473497B2 (ja) * 2009-09-03 2014-04-16 三菱重工業株式会社 多翼遠心ファンおよびそれを用いた空気調和機
JP2013060916A (ja) * 2011-09-14 2013-04-04 Sanyo Electric Co Ltd 遠心ファン及びそれを用いた空気調和機
JP2014029149A (ja) * 2012-06-26 2014-02-13 Denso Corp 遠心式多翼送風機
CN103174672B (zh) * 2013-04-02 2016-01-13 宁波朗迪叶轮机械有限公司 后倾式斜流送风叶轮
US10036400B2 (en) * 2014-05-02 2018-07-31 Regal Beloit America, Inc. Centrifugal fan assembly and methods of assembling the same
DE102014006756A1 (de) * 2014-05-05 2015-11-05 Ziehl-Abegg Se Laufrad für Diagonal- oder Radialventilatoren, Spritzgusswerkzeug zur Herstellung eines solchen Laufrades sowie Gerät mit einem solchen Laufrad
WO2017060987A1 (ja) * 2015-10-07 2017-04-13 三菱電機株式会社 送風機、および、それを備えた空気調和装置
JP2017078386A (ja) * 2015-10-22 2017-04-27 パナソニックＩｐマネジメント株式会社 遠心ファン

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CN113439163A (zh) 2021-09-24
EP3922860A1 (de) 2021-12-15

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