EP2270338B1 - Gebläse und wärmepumpenvorrichtung damit - Google Patents

Gebläse und wärmepumpenvorrichtung damit Download PDF

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Publication number
EP2270338B1
EP2270338B1 EP09734028.5A EP09734028A EP2270338B1 EP 2270338 B1 EP2270338 B1 EP 2270338B1 EP 09734028 A EP09734028 A EP 09734028A EP 2270338 B1 EP2270338 B1 EP 2270338B1
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EP
European Patent Office
Prior art keywords
upstream
expanding portion
blade
bellmouth
blower
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
EP09734028.5A
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English (en)
French (fr)
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EP2270338A4 (de
EP2270338A1 (de
Inventor
Yasuaki Kato
Takahide Tadokoro
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication date
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Publication of EP2270338A1 publication Critical patent/EP2270338A1/de
Publication of EP2270338A4 publication Critical patent/EP2270338A4/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/38—Fan details of outdoor units, e.g. bell-mouth shaped inlets or fan mountings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/164—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of an axial flow wheel
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/522—Casings; Connections of working fluid for axial pumps especially adapted for elastic fluid pumps
    • F04D29/526—Details of the casing section radially opposing blade tips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/40—Vibration or noise prevention at outdoor units

Definitions

  • the present invention relates to a propeller fan type blower provided with a bellmouth and an impeller and to a heat pump apparatus using such a blower and, more particularly, to improvement of a bellmouth structure.
  • a bellmouth shape is proposed in such a way that, while keeping a front panel of the outdoor unit of an air conditioning apparatus rectangular, by changing the magnitude of a curvature of the upstream diameter expanding curved portion from the portion having the minimum bellmouth inner diameter in accordance with the distance between the top, bottom, left, and right peripheral side plates of a surrounding outdoor unit enclosure and the outer circumference of the impeller, an orifice shape can be set in accordance with a different inflow air flow angle in the vicinity of the impeller, separation of flow is reduced in the vicinity of the orifice, so that low noise is achieved.
  • Patent Document 3 For example, refer to Patent Document 3.
  • JP-A-2003 184797 discloses a blower reducing blowing noises and an air conditioner comprising this blower.
  • This blower has a bellmouth surrounding radial outside of a propeller fan and is formed comprising an extending part serially connecting the bellmouth with a straight part, a blow out side are part, a suction side org part and a large diameter end of the suction side are part and extending from these parts to the radial outside.
  • EP 1 357 337 A1 discloses a fan guard of a fan unit.
  • This fan guard comprises an outer frame, a plurality of radiating ribs and a plurality of annular ribs.
  • DE 19751042 A1 discloses a fan having a smaller downstream distance between the fan and the obstacles like a motor or the like.
  • WO 01/96746 A1 discloses an automotive assembly having a high efficiency and low noise. This is achieved by flaring the inlet to the shroud barrel and shaping the tips of the fan blades to conform to the shape of the inlet.
  • JP-A-360251914 discloses a propeller fan mounted in an air purifier main body.
  • This purifier main body has an air sucking port having a filter interposed thereto provided to the upstream side surface of that main body in the fan axial direction.
  • JP-B-2775796 further discloses a fan of an air conditioner placed within an air suction port.
  • a bellmouth having a radially outwardly extending straight section formed at the rim, or having its inlet side wall curved in an almost semi-circular shape toward a radially outward direction from the inner surface of an inlet opening so as to reduce separation of air flow on the bellmouth incoming from the outer circumferential edge of a blade such as air flow incoming from a region concealed by the bellmouth when seen from a blade of the blower, can fulfill its function only when the blower is used under an ideal air passage environment, that is, an environment where air passage is circumferentially uniform about its rotation shaft.
  • an ideal air passage environment is rare as an actual air passage where the blower is operated.
  • a blower having a bellmouth whose curvature changes according to un-uniformity resulting from a circumferential position of an inlet side air passage just reduces separation on the bellmouth, and is not effective in reducing the turbulence of incoming air flow, assuming that such a blower is mounted on an air conditioning apparatus.
  • An objective of the present invention is to reduce the turbulence of incoming air flow itself to obtain a low noise blower even if there is un-uniformity resulting from circumferential positions about the rotation shaft of the inlet side air passage.
  • a blower comprises; a blade having an outer circumferential edge having a recessed warp in a rotational direction, and a bellmouth covering the circumference of the blade at an air outlet side, wherein a surface of the bellmouth facing the blade has a first upstream expanding portion formed in a shape of a convex in an upstream direction of a rotation shaft, extending upstream from a minimum inner diameter position and a second upstream expanding portion formed in a shape of a concave in the upstream direction of the rotation shaft, being continuous with and extending upstream from the first upstream expanding portion.
  • a surface of the bellmouth facing the blade has a first upstream expanding portion formed in a shape of a convex in an upstream direction of a rotation shaft, extending upstream from a minimum inner diameter position and a second upstream expanding portion formed in a shape of a concave in the upstream direction of the rotation shaft, being continuous with and extending upstream from the first upstream expanding portion, whereby the outer circumferential edge of the blade is enclosed and a distance between the outer circumferential edge and the bellmouth becomes wider. This allows more air to be drawn in from around the outer circumferential edge, thereby preventing a pressure change on the bellmouth surface arising from turbulence by the blade tip vortex.
  • this allows air passage around the outer circumferential edge of a blade to be circumferentially uniform, which suppresses fluctuation of air flow coming into the blade, leading to the achievement of a low-noise blower. Furthermore, this allows a section from the second upstream expanding portion to the minimum inner diameter point to form a smoothly continuous shape, which suppresses the turbulence of the air flow itself and effectively reduces noise levels.
  • Embodiment 1 of the present invention is described below with reference to the accompanying drawings.
  • Fig. 1 is a front view of a blower according to Embodiment 1 of the present invention, as viewed from an outlet opening.
  • Fig. 2 is a cross-sectional view taken along the line A-A of Fig. 1 .
  • Fig. 3 is a cross-sectional view taken along the line B-B of Fig. 1 , whose outer circumferential edge is developed into a plane with lines indicating a position of each part in a bellmouth.
  • Fig. 4 is an enlarged partial view of Fig. 2 .
  • Fig. 5 is the same view as Fig. 3 , with the addition of a line illustrating the state of airflow in the vicinity of an outer circumferential edge of a blade.
  • Fig. 6 is the same view as Fig. 2 , with the addition of lines indicating a conventional bellmouth for comparison.
  • a propeller fan 3 having a plurality of blades 1 around a hub 2 is driven by a fan motor 7.
  • the blade 1 is formed of a joining edge with the hub 2, a leading edge 1a facing a rotational direction, a trailing edge 1b opposed to the leading edge 1a, an outer circumferential edge 1c, which is opposed to the joining edge and connecting the leading edge 1a and the trailing edge 1b, and a curved surface surrounded by these joining edges, the leading edge 1a, the trailing edge 1b, and the outer circumferential edge 1c.
  • the blade 1 has a pressure surface 1d facing the rotational direction 10 formed at one side thereof and a negative-pressure surface 1e formed at the other side thereof.
  • Pf1 is a point at the intersection of the leading edge 1a with the outer circumferential edge 1c
  • Pf2 is a point at the intersection of the trailing edge 1b with the outer circumferential edge 1c.
  • the outer circumferential edge 1c has a concave warpage in the rotational direction, as shown in Fig. 3 .
  • Pf3 represents a maximum warpage position at which the distance between a chord 4 connecting Pf1 and Pf2 and the outer circumferential edge 1c is the largest.
  • FIGs. 2 and 4 lines of the blade 1 show a rotational trajectory of the leading edge 1a, the trailing edge 1b, and the outer circumferential edge 1c.
  • a shaft about which the fan motor 7 and the propeller 3 rotate is referred to as a rotational shaft.
  • a direction toward the air inlet side of the rotational shaft (the left side of Fig. 2 ) is set as an upstream direction of the rotation shaft, while a direction toward the air outlet side of the rotational shaft (the right side of Fig. 2 ) is set as a rotational downstream direction of the rotation shaft.
  • the outer periphery of the air outlet of the blade 1 is covered with a bellmouth 5.
  • the bellmouth 5 is located so as to cover the entire blade outer circumference or part of the trailing edge 1b.
  • a section between Pb2 and Pb3 is a minimum inner diameter portion 5b that is the closest to the outer circumferential edge 1c of the blade 1 so as to cover the trailing edge 1b of the outer circumference edge 1c of the blade 1.
  • a section from Pb2 to a Pb1 curves to form a downstream of expanding portion 5a for expanding an air passage toward the rotational downstream of the rotation shaft direction, and at Pb1 connects to a baffle plate 6 for separating an air outlet space ⁇ from an air inlet space ⁇ .
  • the bellmouth 5 has the following air passage expanding shape (contraction flow shape as seen from the air flow direction)in the inlet side direction.
  • the bellmouth 5 has a convex shaped first upstream expanding portion 5c between Pb3 and Pb4, Pb3 being an upstream end of the rotation shaft of the minimum inner diameter portion 5b of the bellmouth 5.
  • the bellmouth 5 has a concave shaped second upstream expanding portion 5d from Pb4 to Pb5, which follows the first upstream expanding portion 5c.
  • the second upstream expanding portion 5d has a large curvature in the vicinity of Pb4, while it has a small curvature in the vicinity of Pb5, and has a substantially conic section in the vicinity of Pb5.
  • the bellmouth 5 has a convex shaped third upstream expanding portion 5e from Pb5 to Pb6, which follows the second upstream expanding portion 5d.
  • Dashed lines Lb3, Lb4, Lb5, and Lb6 in Fig. 3 represent positions of Pb3, Pb4, Pb5, and Pb6 in the rotational shaft direction in the bellmouth 5, respectively.
  • a dashed line Lf3 represents a position in the rotational direction of the maximum warpage position Pf3 on the outer circumferential edge 1c of the blade 1.
  • Pb3, the upstream end of the rotation shaft of the minimum inner diameter portion 5b of the bellmouth 5, is located upstream of the rotation shaft direction of the trailing edge end Pb2 in the outer circumferential edge 1c of the blade 1.
  • Pb4 in the transition portion between the first upstream expanding portion 5c and the second upstream expanding portion 5d of the bellmouth 5 is located downstream of the rotation shaft direction of the maximum warpage position Pf3 on the outer circumferential edge 1c of the blade 1.
  • a position in the rotation shaft direction of the maximum warpage position Pf3 on the outer circumferential edge 1c of the blade 1 is included within the range covered by the second upstream expanding portion 5d.
  • the propeller fan 3 when driven by the fan motor 7, sends to the air outlet space ⁇ the air inside a region where the propeller fan 3 rotates and at the same time draws in the air in the air inlet space ⁇ to the region where the propeller 3 rotates.
  • Gases enter the propeller fan 3 from the face formed of a rotational trajectory of the leading edge 1a and the face formed of the rotational trajectory of the outer circumferential edge 1c. In this way an air flow from the inlet side space ⁇ to the outlet side space ⁇ takes place.
  • part of the gas entering the propeller fan 3 becomes a leak flow 8 to a negative pressure surface 1e from a pressure surface 1d via the outside of the outer circumferential edge 1c.
  • a flow having a vortex structure called a blade tip vortex 9 takes place at a position along the outer circumferential edge 1c of the negative pressure surface 1e, originating from the leak flow 8 occurring in the vicinity of the leading edge of the outer circumferential edge 1c.
  • the blade tip vortex 9 becomes larger as it moves toward the trailing edge side from the leading edge side, and moves away from the outer circumferential edge 1c in the vicinity of the maximum warpage position Pf3 at which a flow deflection becomes large.
  • the blade tip vortex 9 having moved away from the outer circumferential edge 1c is pushed by the entire flow from the inlet side space ⁇ to the outlet side space ⁇ to gradually proceed to the outlet side space ⁇ and is discharged out of the blower as the structure of the vortex weakens.
  • the positional relationship in the downstream side between the bellmouth 5 and the outer circumferential edge 1c is described below.
  • a pressure difference should be maintained between the inlet side space ⁇ and the outlet side space ⁇ depending upon the flow rate.
  • the portion at which the distance between the blade 1 and the bellmouth 5 is smallest is the gap between the minimum inner diameter portion 5b from Pb2 to Pb3 and the outer circumferential edge 1c.
  • such a gap is set at a position in the vicinity of the trailing edge 1b of the outer circumference edge 1c. If the gap is too large, the required pressure difference and flow rate cannot be attained when there is a greater air flow resistance before and after the blower.
  • the present embodiment makes the gap between the bellmouth 5 and the blade 1 in the vicinity of the trailing edge 1b of the outer circumferential edge 1c smaller.
  • the gap is about one to three percent of the blade outer diameter (diameter of a rotation circle of the outer circumferential edge 1c).
  • the face composed of the rotational trajectory of the outer circumferential edge 1c of the blade 1 is an air inlet face. Receiving incoming flow from a larger inlet area has an effect to reduce incoming flow speed at the same flow amount and reduce noise levels. Accordingly, it is preferable to make the distance between the outer circumferential edge 1c of the blade 1 and the bellmouth 5 sufficiently wide.
  • the outer circumferential edge 1c of the blade 1 is also a place where the blade tip vortex 9 originates, grows, and moves away.
  • the blade tip vortex 9 has large turbulence, and, if there is a wall such as a bellmouth 5 in the vicinity, a pressure change on the wall surface becomes so large that results in an increase in noise. To prevent these problems, it is preferable to make the distance between the bellmouth 5 and the outer circumferential edge 1c of the blade 1 in the upstream side sufficiently large.
  • a blower for practical use it is quite rare that there is a wide area around the blade 1 in the inlet space ⁇ and the blade has a circumferentially uniform shape. Air flow to the blade tends to become circumferentially nonuniform and varies in terms of time, as seen from the rotating blade 1, causing an increase in noise. Accordingly, in order to achieve a low-noise blower, it is preferable to provide a circumferentially uniform air passage shape. More preferably, the outer circumferential edge 1c of the blade 1 is covered with the bellmouth 5.
  • the second upstream expanding portion 5d has a large curvature close to the first upstream expanding portion 5c and a smaller curvature at more upstream position and has a substantially conic section at the upstream portion, which allows for a wider opening area upstream of the rotation shaft of the second upstream expanding portion 5d, thereby guiding a large amount of air flow to the space between the outer circumferential edge 1c and the bellmouth 5.
  • the blower has a convex-shaped third upstream expanding portion 5e upstream of the rotation shaft. The blower allows air entering from the end of the bellmouth to follow the third upstream expanding portion 5e for reduction in turbulence and guides it to the blade 1. As a result, a much lower-noise blower can be obtained.
  • the bellmouth 5 has the transition point Pb4 between the first upstream expanding portion 5c and the second upstream expanding portion 5d located downstream of the maximum warpage position Pf3 on the outer circumferential edge 1c of the blade 1, which results in a large distance between the outer circumferential edge 1c of the blade 1 and the bellmouth 5 in the vicinity of the maximum warpage point Pf3, thereby suppressing a pressure change on the bellmouth wall surface.
  • the location in the rotation shaft direction of the maximum warpage point Pf3 on the outer circumferential edge 1c of the blade 1 falls within the range covered by the second upstream expanding portion 5d, which reduces turbulent air flow around the blade tip vortex 9 when it moves away and also reduces the turbulence of the blade tip vortex 9, thereby suppressing the noise caused by the moving blade tip vortex 9.
  • Figs. 7 and 8 show a heat pump apparatus, namely an air conditioning apparatus according to Embodiment 2 of the present invention.
  • Fig. 7 (a) is a front view of a box-shaped outdoor unit of an air conditioning apparatus
  • Fig. 7 (b) is a cross-section taken along the line C-C of Fig. 7 (a) .
  • Fig. 8 is a view showing the direction of air passage, as seen from the rotation shaft.
  • the reference numerals and symbols in Fig. 7 refer to the same components as those with the same numerals and symbols in the above-described Embodiment 1. Reference is also made to Figs. 1 to 6 when describing a blower.
  • An air conditioning apparatus namely, a box-shaped outdoor unit 12 according to the present embodiment includes an air outlet face 13 formed in the front face, an air inlet face 14 formed at two faces including its opposite face (back face) and one face on the left-hand side, and a L-shaped heat exchanger 15 disposed so as to cover the air inlet face 14.
  • a blower is disposed close to the heat exchanger 15.
  • Such a blower includes a blower according to above described Embodiment 1.
  • the heat exchanger 15 includes a pipe having a multilayer fin for heat dissipation formed on an outer surface thereof, the pipe having a refrigerant circulating thereinside.
  • the heat exchanger 15 does not necessarily have an L-shaped form, and may be provided on a back face only. In such a case, the side surrounding the air outlet face 13 on the box-shaped unit is formed of a plurality of side plates.
  • a grill 16 is disposed downstream of the rotation shaft of the blower, which protects a propeller fan 3 or protects a person from the rotating propeller fan 3.
  • the air outlet face 13 and the bellmouth 5 are surrounded by the heat exchanger 15, top plate 17, bottom plate 18, and separating plate 22.
  • the separating plate 22 separates an inboard air passage chamber 19 housing the blower inside the outdoor unit 12 from a compressor chamber 21 housing a compressor 20.
  • a blade 1 of the propeller fan 3 has a concave-shaped warpage in the outer circumferential edge 1c in the rotational direction 10.
  • a minimum inner diameter portion 5b having the shortest distance with the outer circumferential edge 1c of the blade 1 in the section from Pb2 to Pb3, covers a trailing edge 1b of the outer circumferential edge 1c in any of directions (i) to (viii) shown in Fig. 8 .
  • a downstream expanding portion 5a is provided whose air passage bends at a section from Pb2 to Pb1 to expand in the rotation shaft downstream direction.
  • the air passage expanding shape (contraction flow shape as seen from the air flow direction) in the inlet direction includes a convex shaped first upstream expanding portion 5c between Pb3 and Pb4, Pb3 being an end point of upstream direction of the rotation shaft of the minimum inner diameter portion 5b.
  • the bellmouth 5 has a concave shaped second upstream expanding portion 5d from Pb4 to Pb5 upstream of the rotation shaft, which follows the first upstream expanding portion 5c.
  • the second upstream expanding portion 5d has a large curvature in the vicinity of Pb4, while it has a small curvature in the vicinity of Pb5, and has a substantially conic section in the vicinity of Pb5, which is an upstream portion.
  • the bellmouth 5 has a convex shaped third upstream expanding portion 5e in a section from Pb5 to Pb6, which follows the second upstream expanding portion 5d.
  • an upstream end of the minimum inner diameter portion 5b of the bellmouth 5 in the rotation shaft direction is located upstream of the rotation shaft direction of the trailing edge end Pb2 in the outer circumferential edge 1c of the blade 1.
  • Pb4 in the transition between the first upstream expanding portion 5c and the second upstream expanding portion 5d is located downstream of the rotation shaft of the maximum warpage position Pf3 on the outer circumferential edge 1c of the blade 1.
  • a position in the rotation shaft direction of the maximum warpage position Pf3 on the outer circumferential edge 1c of the blade 1 falls within the range covered by the second upstream expanding portion 5d.
  • An air conditioning apparatus namely an outdoor unit 12 according to the present embodiment is described with regard to operation.
  • the propeller fan 3 rotates to send the air inside the inboard air passage chamber 19, a region where the propeller fan 3 rotates, from the air outlet face 13 to the air outlet space ⁇ , and at the same time draws in the air in the air inlet space ⁇ from the air inlet face 14 through the fin of the heat exchanger 15, which enters the inboard air passage chamber 19 where the propeller fan 3 rotates.
  • the heat exchanger 15 include a refrigerant having higher or lower temperature than the gas outside the exchanger circulating thereinside, providing heat exchange when the air outside the exchanger 15 passes therethrough. The air, which becomes warmer or colder after undergoing heat exchange by the heat exchanger 15 when entering the inboard air passage chamber 19, is blown out to the outside with the rotating propeller fan 3.
  • Air flow around the blade of the propeller fan 3 behaves in the same manner as that in Embodiment 1. That is, as shown in Fig. 5 , part of the air entering the propeller fan 3 becomes a leak flow 8 to the negative pressure surface 1e from the pressure surface 1d via the outside of the outer circumferential edge 1c. A blade tip vortex 9 takes place at a position along the outer circumferential edge 1c of the negative pressure surface 1e, originating from the leak flow 8 occurring in the vicinity of the leading edge of the outer circumferential surface 1c.
  • the blade tip vortex 9 grows as it transits to the trailing edge side from the leading edge side, and moves away from the outer circumferential edge 1c of the blade in the vicinity of the maximum warpage position Pf3 at which a flow deflection becomes large.
  • the blade tip vortex 9 that left the outer circumferential edge 1c is pushed by an entire flow from the inboard air passage chamber 19 to the outside of the unit and is discharged out of the blower through the air outlet face 13, while weakening its vortex structure.
  • an air conditioning apparatus employs the blower described above in Embodiment 1 as a blower for promoting heat exchanger by the heat exchanger 15 in the outdoor unit 12, it is characterized by the shape of the bellmouth 15 around the propeller fan 3 and the positional relationship between the propeller fan 3 and the bellmouth 5. Accordingly, in the same way as with the above described Embodiment 1, a great amount of air can be drawn in from the outer circumferential edge 1c of the blade 1 of the blower, which suppresses a pressure change on the surface of the bellmouth 5 arising from turbulence of the blade tip vortex 9. In addition, air passage around the outer circumferential edge 1c of the blade 1 can be circumferentially homogenized, which helps to suppress fluctuation of air entering the blade 1, leading to the achievement of a lower-noise blower.
  • a section between the upstream side of the rotation shaft of the second upstream expanding portion 5d and the minimum inner diameter point Pb3 can be constructed into a smoothly continued shape, which effectively suppresses turbulent of air flow and efficiently reduces noise.
  • the distance to the end of air passage except the bellmouth 5 seen from the blade 1 is small, for example, in the direction of (i), (iii), (v), or (vii) in Fig. 8 and large in the direction of (ii), (iv), (vi), or (viii).
  • the outdoor unit 12 employing a blower according to the present embodiment having a sufficient distance between the bellmouth 5 and the maximum warpage position Pf3 on the outer circumferential edge 1c of the blade 1 is capable of preventing fluctuation of incoming flow of the air passage distance resulting from the rotation position of the blade 1, leading to a significant reduction in noise.
  • a change in air flow at the rotational position of the blade 1 can be reduced, which results in reduction of a change of force exerted by the propeller fan 3 on the fan motor 7, leading to reduction of bearing wear or shaft deflection of the fan motor 7. This prolongs the durability of the outdoor unit 12 and helps to achieve the outdoor unit 12 that provides a stable quality during a long period of service.
  • an air conditioning apparatus as a heat pump which has a bellmouth 5 around a propeller fan 3, the bellmouth 5 having a second upstream expanding portion 5d formed at the circumferential surface thereof and a third upstream expanding portion 5e formed upstream of the second upstream expanding portion 5d.
  • An objective of the present invention can also be achieved by forming the second upstream expanding portion 5d and the third upstream expanding portion 5e only at a portion where the distance to the end of an air flow passage other than the bellmouth 5 seen from the blade 1 rapidly changes in the circumferential direction, for example, a portion (having a long distance to the end of the air flow passage) corresponding to a corner of a box-shaped outdoor unit 12.
  • An outdoor unit 12 of a heat pump apparatus namely an air conditioning apparatus having an upstream portion including the second upstream expanding portion 5d formed only in some portions of the circumferential direction of the bellmouth 5 is described below with reference to Figs. 9 to 11 .
  • Fig. 9(a) is a front view of an outdoor unit of an air conditioning apparatus according to Embodiment 3 of the present invention.
  • Fig. 9(b) is a cross-sectional view taken along the line D-D including its rotation shaft.
  • Fig. 9(c) is a cross-sectional view taken along the line E-E.
  • Fig. 10 is a view showing the direction of an air passage, as seen from the rotational shaft.
  • Fig. 11 is a partially enlarged cross-sectional view of a main section of a bellmouth and a propeller fan, as seen from an inlet side.
  • Figs. 1 to 6 Reference is also made to Figs. 1 to 6 to describe below a blower.
  • An air conditioning apparatus namely a box-shaped outdoor unit 12 according to the present embodiment includes a blade 1 of a propeller fan 3 of its blower having a concave-shaped warpage (see Fig. 3 ) formed at the circumferential edge 1c thereof so as to warp in a rotational direction 10.
  • the bellmouth 5 surrounding the entire periphery or the trailing edge of the propeller fan 3 has its upstream portion terminated at a first upstream expanding portion 5c (see Fig. 4 ) in a portion extending in any of directions (i), (iii), (v), and (vii) as shown in Fig. 10 , namely in a portion having a smaller distance to an air flow passage other than the bellmouth 5.
  • the bellmouth 5 has a minimum inner diameter portion 5b being face-to-face with the trailing edge 1b of the outer circumferential edge 1c in a portion defined by lines extending in the directions of (ii) and (iv) in a section consisting of a separating plate 22, a top plate 17, and a bottom plate 18 and in a portion defined by lines extending in the directions of (vi) and (viii) in a section consisting of a heat exchanger 15, the bottom plate 18, and the top plate 17, the minimum inner diameter portion 5b being the closest to the outer circumferential edge 1c of the blade 1 in a section from Pb2 to Pb3, as described in Embodiment 1 with reference to, for example, Fig. 4 .
  • the bellmouth 5 has a downstream expanding portion 5a formed at a section from Pb2 to Pb1 so as to expand the air passage in the rotational shaft upstream direction.
  • the air passage expanding shape (contraction flow shape as seen from the air flow direction) in the air inlet direction includes a convex shaped first upstream expanding portion 5c upstream of the rotation shaft between Pb3 and Pb4, Pb3 being an upstream end of the minimum inner diameter portion 5b.
  • the bellmouth 5 has a concave shaped second upstream expanding portion 5d from Pb4 to Pb5, which follows the first upstream expanding portion 5c.
  • the second upstream expanding portion 5d has a large curvature in the vicinity of Pb4, while it has a small curvature in the vicinity of Pb5, and has a substantially conic section in the vicinity of Pb5. Furthermore, the bellmouth 5 has a convex shaped third upstream expanding portion 5e in a section from Pb5 to Pb6, which follows the second upstream expanding portion 5d.
  • an upstream end of the minimum inner diameter portion 5b is located upstream of the trailing edge end Pb2 in the outer circumferential edge 1c in any of directions of (ii), (iv), (vi), and (viii).
  • Pb4 in the transition between the first upstream expanding portion 5c and the second upstream expanding portion 5d is located downstream of the rotation shaft direction of the maximum warpage position Pf3 on the outer circumferential edge 1c of the blade 1.
  • a position in the rotation shaft direction of the maximum warpage position Pf3 on the outer circumferential edge 1c of the blade 1 falls within the range covered by the second upstream expanding portion 5d.
  • An air conditioning apparatus that is an outdoor unit 12 is also characterized by the shape of the bellmouth 15 around the propeller fan 3 and the positional relationship between the propeller fan 3 and the bellmouth 5. Accordingly, as with the above described Embodiments 1 and 2, a great amount of air can be drawn in from the outer circumferential edge 1c of a blade 1 of a blower, which suppresses a pressure change on the surface of the bellmouth 5 arising from turbulence of the blade tip vortex 9.
  • a section between the upstream side of the second upstream expanding portion 5d and the minimum inner diameter point Pb3 can be constructed with a smoothly continued surface, which effectively suppresses turbulent air flow and efficiently reduces noise.
  • the second upstream expanding portion 5d and the third upstream expanding portion 5e cover the periphery of the blade in any of directions (ii), (iv), (vi), and (viii) as shown in Fig. 8 where a distance to an air flow passage other than the bellmouth 5 rapidly changes in the circumferential direction, thereby efficiently suppressing the fluctuation of incoming air flow and the blade tip vortex 9 as well as attaining reduction in noise.
  • a change in air flow at the rotational position of the blade 1 can be reduced, which results in reduction of a change of force exerted by the propeller fan 3 on the fan motor 7, leading to reduction of bearing wear or shaft deflection of the fan motor 7. This prolongs the durability of the outdoor unit 12 and helps to achieve the outdoor unit 12 that provides a stable quality during a long period of service.
  • an upstream portion of the bellmouth 5 including the second upstream expanding portion 5d exists only at a part of the periphery direction of the outer circumferential edge 1c, the effect of suppressing fluctuation of incoming air flow or the blade tip vortex 9 is reduced compared with above-described Embodiment 2 where such a upstream portion is provided around the entire periphery.
  • the diameter of the propeller fan 3 can be large.
  • a propeller fan 3 having an increased diameter reduces the revolution of the fan for a required amount of air, leading to reduced noise.
  • an increased-diameter fan reduces the velocity of air flow blown out by the propeller fan 3 and passing through the grill 16, leading to a reduction in noise emissions caused by the grill 16. So that low noise outdoor unit 12 can be obtained
  • the bellmouth 5 has a convex-shaped end warpage 23 formed at both circumferential ends of the second upstream expanding portion 5d in the rotation shaft direction.
  • This makes continuously smooth a transitional section between the second upstream expanding portion 5d and a portion where no such portion is found, for example, between the direction of (vii) and that of (viii), or between the direction of (viii) and that of (i), thereby suppressing the fluctuation due to separation of the air flow coming into the bellmouth 5 in these transitional section, so that low noise effect can be easily obtained.
  • Fig. 12(a) is a front view of a rectangular box-shaped outdoor unit of a heat pump water heater according to Embodiment 4 of the present invention.
  • Fig. 12(b) is a horizontal cross-sectional view including a rotation shaft taken along the line F-F.
  • Fig. 12(c) is a cross-sectional view including a rotation shaft taken along the line G-G.
  • the reference numerals and symbols in Fig. 12 refer to the same components as those in Embodiments 1 and 3. Reference is also made to Figs. 1 to 6 to provide descriptions on the blower.
  • the heat pump water heater In a heat pump water heater, namely a rectangular box-shaped outdoor unit 25 according to the present embodiment, its blower has the same structure as in Embodiment 3. Accordingly, descriptions on the blower are omitted, and differences in structure from those in Embodiment 3 are described below.
  • the heat pump water heater according to the present embodiment has an outlet face 13 provided in the front of the outdoor unit 25, an external air inlet face 14 provided in two faces, that is, its opposing face (back face) and a face of the left-hand side of the figure, and an L-shaped heat exchanger 15 is disposed so as to cover the air inlet face 14.
  • a water heat exchanger 24 for performing heat exchange between a refrigerant and water is provided at the bottom of the inboard air passage chamber 19.
  • the water heat exchanger 24 occupies the bottom of the inboard air passage chamber 19.
  • the top plate 24a of the water heat exchanger 24 is replaced by the bottom plate 18 in Embodiment 3. Therefore, the outdoor unit 25 of a heat pump water heater according to the present embodiment also provides the same advantages and effects as the blower described in Embodiment 3, leading to the implementation of the outdoor unit 25 which provides low-noise and preserves quality for a long period of time.
  • a blower according to the present embodiment is characterized in that a circumferential edge of the blade 1 is warped toward an inlet side ( ⁇ ) from an outlet side ( ⁇ ).
  • the shape of such a circumferential edge is described below in terms of the warpage toward the inlet side from the outlet side.
  • a bellmouth 5 except the shape of the blade, the relative position of a propeller fan 3 and bellmouth 5, and the structure with a fan motor 7 are the same as Embodiment 1. Accordingly, reference is also made to Figs. 1 to 6 to provide a description on the blower.
  • Fig. 13 is an enlarged view, equivalent to Fig. 4 , of a main section of a blower according to Embodiment 5 of the present invention, where dashed lines Ld1 to Ld11 are dividing meridians obtained by equally dividing a radial section of a blade with the rotation shaft being the center and rotating lines that connect divided points from hub side to an outer circumference side about the rotational shaft to project the dividing points to a plane containing the rotation shaft. The outer circumference side is shown.
  • Fig. 13 shows 12 divisions ranging from the leading edge to the trailing edge.
  • the dividing meridian is warped in front and at the back of a line Lf4 drawn in the outer circumferential edge of a blade in such a manner that the outer circumferential edge curves toward an inlet side (inlet space a) from an outlet side (outlet space ⁇ ).
  • Such a warpage shown in Fig. 13 is becoming greater at in the middle between the leading edge and the trailing edge, Ld5 to Ld7, and is gradually becoming smaller toward the leading edge or the trailing edge, while no warpage is found at a leading edge 1a and a trailing edge 1b (represented as meridian in Fig. 13 ) that are ends of the dividing meridian.
  • a blower provided with a propeller fan 3 according to the present embodiment having a blade outer circumferential edge warped toward the inlet side is described below in terms of its operation.
  • the propeller fan 3 when driven by the fan motor 7, sends to the air outlet space ⁇ the air inside a region where the propeller fan 3 rotates and at the same time draws in the air in the air inlet space ⁇ to the region where the propeller 3 rotates through surfaces defined by a leading edge 1a or an outer circumferential edge 1c when a blade is rotating.
  • Fig. 14 is a view of an outer circumferential edge of a blade, with the addition of leader lines indicating the state of air flow in the vicinity of the outer circumferential edge of the blade.
  • part of the air entering the propeller fan 3 becomes a leak flow 8 to the negative pressure surface 1e from the pressure surface 1d via the outside of the outer circumferential edge 1c.
  • the outer circumferential edge of a blade is warped toward an inlet side, which reduces the pressure difference between the pressure surface 1d and the negative pressure surface 1e in the outer circumferential edge 1c as well as makes smooth the leak flow 8 coming into the negative pressure surface 1e from the pressure surface 1d.
  • a blade tip vortex 9 occurring at a position along the outer circumferential edge 1c on the negative pressure surface 1e, originating from the leak flow 8 occurring in the vicinity of the leading edge of the outer circumferential surface 1c, has a higher central pressure than those with no warped outer circumferential edge made toward an inlet side, which causes the vortex to be weaker.
  • the blade tip vortex 9 grows as it transits to the trailing edge side 1b from the leading edge side 1a, and moves away from the outer circumferential edge 1c of the blade 1 at the maximum warpage position Pf3 at which a flow deflection becomes large.
  • the blade tip vortex 9 that left the outer circumferential edge 1c is pushed by an entire flow from the inlet space ⁇ to the outlet space ⁇ and is discharged out of the blower, while it is weakening in vortex structure.
  • the vortex that left the outer circumferential edge 1c interferes with the bellmouth 5 and an adjacent blade causing noise emissions and impedes air flow from the inlet space ⁇ to the outlet space ⁇ . For this reasons, fan rotating speeds is increased to obtain a required amount of air volume and pressure, increasing in noise emissions.
  • the blade outer circumferential edge is warped toward an upstream side, thereby weakening the blade tip vortex 9 and suppressing increased noise level caused by the blade tip vortex 9.
  • the blade tip vortex 9 becomes unstable such that its position and vortex diameter are easily changed although it is weak as a vortex due to its relatively high central when the outer circumferential edge of the blade is warped toward the inlet side.
  • a conventional bellmouth 25 having only a first upstream expanding portion as shown in Fig. 15 cannot sufficiently obtain effects.
  • actual blowers rarely have a wide area around the blade 1 in the air inlet space ⁇ and a circumferentially uniform shape.
  • a bellmouth 24 having a small first expanding portion indicated by a solid line is susceptible to fluctuation in the periphery, causing the weak, unstable blade tip vortex 9 to further become unstable, which disturbs a flowing path and induces noise emissions.
  • the bellmouth 5 covers area of the outer circumferential edge 1c of the blade 1 and provides a greater distance to the outer circumferential edge 1c of the blade 1 than a conventional bellmouth indicated by solid lines or dashed-dotted lines.
  • the warpage of the outer circumferential edge made toward the inlet side from the outlet side is becoming greater in the middle between the leading edge 1a and the trailing edge 1b and is gradually becoming smaller toward the trailing edge 1b, while no warpage is found at the trailing edge 1b, an end of the dividing meridian.
  • the bellmouth 5 causes less air flow to come from the outer circumferential edge 1c of the blade 1, and the less warped outer circumferential edge at the trailing edge 1b where there is less leak flow 8 where the blade tip vortex 9 originates and grows results in a greater turning angle at an outer circumferential edge having a high circumferential velocity, thereby effectively heightening blade boosting.
  • a heat pump apparatus for example, an air conditioning apparatus is described with reference to Figs. 7 and 8 provided with a blower, with a blade outer circumferential edge of a propeller fan 3 being warped toward an inlet side from an outlet side, having a second upstream expanding portion 5d along the entire circumference in the circumference direction continuously upstream of the first upstream expanding portion of the bellmouth 5.
  • Figs. 1 to 6 is made to describe the blower.
  • An air conditioning apparatus to which a blower according to the present embodiment is applied has the same structure and operation as those described in Embodiment 2, and provides the same advantages and effects as those in Embodiment 2. Accordingly, descriptions provided below are mainly regarding warped outer circumferential edge of a blade 1 of the propeller fan 3.
  • a conventional bellmouth structure cannot provide sufficient effect even if the blade 1 of the propeller fan 3 has a warped outer circumferential edge toward the inlet side.
  • a conventional bellmouth structure when installed in a heat pump apparatus such as an air conditioning apparatus, a conventional bellmouth structure has difficulties in providing noise reduction effect resulting from a blade having a warped outer circumferential edge, due to low circumferential uniformity in air passages at the periphery of the blade circumferential edge.
  • An air conditioning apparatus includes a bellmouth that has a first upstream expanding portion and a second upstream expanding portion provided at the entire circumference thereof and a propeller fan 3 that has an outer circumferential edge of its blade 1 warped toward an air inlet side, which suppresses the effect of non-uniform air passage around the outer circumferential edge and ensures the entry of air from the outer circumferential edge 1c as well as weakens a blade tip vortex 9 and achieves noise reduction effects, leading to the achievement of a low-noise heat pump apparatus.
  • a heat pump apparatus for example, an air conditioning apparatus provided with a propeller fan 3 having a outer circumferential edge of its blade warped toward an inlet side from an outlet side and a second upstream expanding portion 5d formed along part of the circumference continuously upstream side of the first upstream expanding portion 5c.
  • a propeller fan 3 having a outer circumferential edge of its blade warped toward an inlet side from an outlet side and a second upstream expanding portion 5d formed along part of the circumference continuously upstream side of the first upstream expanding portion 5c.
  • Figs. 1 to 6 is made to describe the blower.
  • An air conditioning apparatus to which a blower according to the present embodiment is applied has the same structure and operation as those described in Embodiment 3 using Figs. 10 and 11 , and provides the same advantages and effects of Embodiment 3. Accordingly, descriptions provided below are mainly regarding warping outer circumferential edge of a blade 1 of the propeller fan 3 toward the inlet side.
  • a conventional bellmouth structure cannot achieve sufficient effects even if a blade 1 of a propeller fan 3 has a warped outer circumferential edge toward the inlet side.
  • uniformity is low in the air passage around the outer circumferential edge of the blade.
  • the distance between ambient faces and the blade becomes small, so that it is difficult to obtain low noise effect in the case of warping the outer circumferential edge of the blade toward the inlet side.
  • An air conditioning apparatus includes a bellmouth that has a first upstream expanding portion and a second upstream expanding portion provided at a location in which there is a significant change in distance between the blade and the surface of the apparatus, as viewed from the rotating blade, which effectively suppresses the effect of un-uniform air passage of the outer circumferential edge and ensures the entry of air from the outer circumferential edge 1c as well as weakens a blade tip vortex 9 and achieves noise reduction effects, leading to the achievement of a low-noise heat pump apparatus.
  • Figs. 16 and 17 are graphs showing the relationship of air volume and aerodynamic noise level by combining cases of an outdoor unit of an air conditioning apparatus having a blade 1 of a propeller fan 3 with and without a warped outer circumferential edge, second upstream expanding portion upstream of the bellmouth first upstream expanding portion in a corner consisting of a separation plate, a top plate, and a bottom plate of the outdoor unit, and those having a conventional bellmouth.
  • the outer circumferential edge of a blade 1 has a different shape between Fig. 16 and Fig. 17 .
  • Blade shapes in Figs. 16 and 17 are hereinafter referred to as propeller fan A and propeller fan B, respectively.
  • Fig. 18 shows dividing meridians, like those in Fig. 13 .
  • a ⁇ being an angular difference between before and after the inclination of the dividing meridian changes
  • ⁇ at a dividing meridian in the middle of the leading edge 1a and the trailing edge 1b, that is, a dividing meridian Ld6 in Fig. 18 is set at a maximum of about 14 degrees
  • ⁇ at a dividing meridian closer to the leading edge 1a that is, a dividing meridian Ld4 in Fig. 18 is set at a maximum of about 14 degrees.
  • Radius position which is a base point where the gradient of the dividing meridian changes is specified as 85 % radius of the outer circumferential diameter for both fans.
  • the maximum ⁇ value (about 14 degrees) is obtained after various tests are conducted and preferably approximately 14 degrees.
  • Fig. 19 is a development view of the outer circumferential edge of a blade 1.
  • Warpage ratio is defined as D divided by L, where D is a maximum distance between the blade chord and the blade and L is the length of the chord. Warpage ratio is set to 5.8 percent at a position 85 percent of the radius and to 8.7 percent at a position of the outer diameter.
  • a bellmouth having a second upstream expanding portion provides more noise reduction than a conventional bellmouth in the case where no warpage is formed in the outer circumferential edge of a blade.
  • the conventional bellmouth provides nearly no noise reduction for an outdoor unit, while a bellmouth having a second upstream expanding portion provides a significant noise reduction.
  • An outdoor unit 12 of an air conditioning apparatus and an outdoor unit 25 of a heat pump water heater are described above as an example of applications of a blower according to the present invention.
  • the blower according to the present invention can be widely used in other various types of apparatuses (for example, a ventilating fan) and facilities which are provided with a blower.

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

Claims (12)

  1. Gebläse, umfassend:
    einen Flügel (1), aufweisend eine außen umlaufende Kante (1c) mit einer vertieften Wölbung in einer Rotationsrichtung, und
    eine ringförmigen Einströmdüse (5), die den Umfang des Flügels (1) an einer Luftauslassseite bedeckt,
    wobei ein Oberflächenabschnitt der Einströmdüse (5), der einer Fläche zugewandt ist, die aus einer Rotationstrajektorie der außen umlaufenden Kante (1c) gebildet ist, einen in einer konvexen Form ausgebildeten ersten stromaufwärtigen Expansionsabschnitt (5c) aufweist, der einer stromaufwärtigen Richtung einer Rotationswelle zugewandt ist und sich von einer Position am minimalen Innendurchmesser (Pb3) stromaufwärts erstreckt, und einen in einer konkaven Form ausgebildeten zweiten stromaufwärtigen Expansionsabschnitt (5d) aufweist, der der stromaufwärtigen Richtung der Rotationswelle zugewandt ist, und der zusammenhängend mit und sich erstreckend von dem ersten stromaufwärtigen Expansionsabschnitt (5c) ist, und
    dadurch gekennzeichnet, dass
    ein Übergangsabschnitt zwischen dem ersten stromaufwärtigen Expansionsabschnitt (5c) und dem zweiten stromaufwärtigen Expansionsabschnitt (5d) stromabwärtig von einer Position mit maximaler Wölbung (Pf3) auf der außen umlaufenden Kante (1c) des Flügels (1) angeordnet ist.
  2. Gebläse nach Anspruch 1, wobei ein stromaufwärtiger Abschnitt des zweiten stromaufwärtigen Expansionsabschnitts (Sd) im Wesentlichen in Form eines Kegels ausgebildet ist.
  3. Gebläse nach Anspruch 1 oder 2, wobei ein dritter stromaufwärtiger Expansionsabschnitt (5e) in einer konvexen Form in der stromaufwärtigen Richtung der Rotationswelle ausgebildet ist, wobei der dritte stromaufwärtige Expansionsabschnitt (5e) zusammenhängend mit und sich stromaufwärtig erstreckend von dem zweiten stromaufwärtigen Expansionsabschnitt (5d) ist.
  4. Gebläse nach Anspruch 3, wobei der zweite stromaufwärtige Expansionsabschnitt (5d) oder der dritte stromaufwärtige Expansionsabschnitt (5e) den Abschnitt mit der maximalen Wölbung (Pf3) auf der außen umlaufenden Kante (1c) des Flügel (1) bedeckt.
  5. Gebläse nach einem der Ansprüche 1 bis 4,
    wobei eine außen umlaufende Kantenseite des Flügels (1) eines Propellerlüfters (3) von einer Auslassseite zu einer Einlassseite gewölbt ist.
  6. Gebläse nach Anspruch 5, wobei bezüglich einer Wölbung, die von der Auslassseite zu der Einlassseite in der außen umlaufenden Kantenseite des Flügels (1) des Propellerlüfters (3) ausgebildet ist, ein Wölbungsgrad von einem mittleren Punkt zwischen einer Vorderkante (1a) und einer Hinterkante (1b) zur Hinterkante (1b) allmählich kleiner wird.
  7. Wärmepumpenvorrichtung, umfassend:
    eine Luftauslassfläche (13), die auf einer oberen Fläche oder einer seitlichen Fläche eines Gehäuses vorgesehen ist und ein Gebläse nach einem der Ansprüche 1 bis 6 darauf angeordnet ist,
    eine Lufteinlassfläche (14), die auf zumindest einer Fläche mit Ausnahme der Luftauslassfläche (13) vorgesehen ist,
    einen Wärmetauscher (15), der angeordnet ist, um die Lufteinlassfläche (14) abzudecken; und
    eine Vielzahl von Seitenplatten, um die anderen Flächen mit Ausnahme der Luftauslassfläche (13) und der Lufteinlassfläche (14) auszubilden,
    wobei der erste stromaufwärtige Expansionsabschnitt (5c) des Gebläses von einer Position mit minimalem Innendurchmesser (Pb3) an einem gesamten Abschnitt einer Umfangsrichtung der Einströmdüse ausgebildet ist, und
    der zweite stromaufwärtige Expansionsabschnitt (5d) des Gebläses zusammenhängend mit dem ersten stromaufwärtigen Expansionsabschnitt (5c) an einem gesamten Abschnitt der Umfangsrichtung der Einströmdüse ausgebildet ist.
  8. Wärmepumpenvorrichtung, umfassend:
    eine Luftauslassfläche (13), die auf einer oberen Fläche oder einer seitlichen Fläche eines Gehäuses vorgesehen ist und die ein Gebläse nach einem der Ansprüche 1 bis 6 darauf anordnet,
    eine Lufteinlassfläche (14), die auf zumindest einer Fläche mit Ausnahme der Luftauslassfläche (13) vorgesehen ist,
    einen Wärmetauscher (15), der angeordnet ist, um die Lufteinlassfläche (14) zu bedecken; und
    eine Vielzahl von Seitenplatten, um die anderen Flächen mit Ausnahme der Luftauslassfläche (13) und der Lufteinlassfläche (14) auszubilden,
    wobei ein erster stromaufwärtiger Expansionsabschnitt (5c) des Gebläse von einer Position mit minimalem Innendurchmesser (Pb3) an einem gesamten Abschnitt einer Umfangsrichtung der Einströmdüse ausgebildet ist, und
    der zweite stromaufwärtige Expansionsabschnitt (5d) des Gebläses zusammenhängend mit dem ersten stromaufwärtigen Expansionsschnitt (5c) an einigen Abschnitten der Umfangsrichtung der Einströmdüse ausgebildet ist.
  9. Wärmepumpenvorrichtung nach Anspruch 8, wobei der zweite stromaufwärtige Expansionsabschnitt (5d) der Einströmdüse (5) eine gekrümmte Oberfläche (23) an beiden Umfangsenden davon aufweist, wobei die gekrümmte Oberfläche (23) in einer konvexen Form in Richtung einer Rotationsachse ausgebildet ist.
  10. Wärmepumpenvorrichtung nach Anspruch 8 oder 9, wobei eine Umfangsposition der Einströmdüse (5), wo sich der zweite stromaufwärtige Expansionsabschnitt (5d) vom ersten stromaufwärtigen Expansionsabschnitt (5c) teilweise nach oben erstreckt, einer Ecke zwischen seitlichen Flächen entspricht, die die Luftauslassfläche (13) des Gehäuses umgeben.
  11. Wärmepumpenvorrichtung nach Anspruch 10, wobei die die Luftauslassfläche (13) des Gehäuses umgebenden seitlichen Flächen aus der Vielzahl von Seitenplatten gebildet sind.
  12. Wärmepumpenvorrichtung nach Anspruch 10, wobei die die Luftauslassfläche (13) des Gehäuses umgebenden seitlichen Flächen aus der Vielzahl von Seitenplatten und dem Wärmetauscher (15) gebildet sind.
EP09734028.5A 2008-04-22 2009-03-11 Gebläse und wärmepumpenvorrichtung damit Active EP2270338B1 (de)

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CN102016327A (zh) 2011-04-13
JP5213953B2 (ja) 2013-06-19
EP2270338A4 (de) 2014-10-01
ES2702364T3 (es) 2019-02-28
EP2270338A1 (de) 2011-01-05
US20110017427A1 (en) 2011-01-27
WO2009130954A1 (ja) 2009-10-29

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