WO2015045907A1 - 遠心送風機及びこれを備えた空気調和機 - Google Patents
遠心送風機及びこれを備えた空気調和機 Download PDFInfo
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- WO2015045907A1 WO2015045907A1 PCT/JP2014/074229 JP2014074229W WO2015045907A1 WO 2015045907 A1 WO2015045907 A1 WO 2015045907A1 JP 2014074229 W JP2014074229 W JP 2014074229W WO 2015045907 A1 WO2015045907 A1 WO 2015045907A1
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
- F04D25/088—Ceiling fans
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- 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
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- 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
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
- F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/663—Sound attenuation
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- 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
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
- F24F1/0022—Centrifugal or radial fans
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- 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
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
- F24F1/0047—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in the ceiling or at the ceiling
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- 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
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- 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
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- 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
- F05D2240/304—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 trailing edge of a rotor blade
-
- 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
- F05D2240/307—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 tip of a rotor blade
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2250/00—Geometry
- F05D2250/10—Two-dimensional
- F05D2250/18—Two-dimensional patterned
- F05D2250/182—Two-dimensional patterned crenellated, notched
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/02—Ducting arrangements
- F24F13/06—Outlets for directing or distributing air into rooms or spaces, e.g. ceiling air diffuser
- F24F2013/0616—Outlets that have intake openings
Definitions
- the present invention relates to a centrifugal blower and an air conditioner including the same.
- centrifugal blowers have been used as blowers for indoor units of air conditioners.
- this centrifugal blower when the impeller is rotated by the fan motor, air is sucked into the case of the indoor unit from the suction port of the indoor unit.
- the sucked air is guided to the air suction port of the shroud of the impeller by the inner peripheral surface of the bell mouth.
- main flow the flow of air guided to the air suction port by the inner peripheral surface of the bell mouth.
- This mainstream air is discharged from the impeller to the outside (in the direction away from the rotating shaft of the impeller) by a plurality of blades arranged along the circumferential direction between the hub and the shroud.
- Most of the air discharged from the impeller is blown into the room through the blowout port of the indoor unit.
- a part of the air discharged from the impeller circulates toward the bell mouth through the space between the outer peripheral surface of the shroud and the case in the case of the indoor unit.
- the recirculated air passes through the gap between the outer peripheral surface of the bell mouth and the inner peripheral surface of the shroud and joins the main flow.
- a circulation flow leakage flow
- the above circulation flow has a high wind speed. For this reason, when the circulating flow that has passed through the gap collides with the leading edge of the blade, noise increases. In addition, since the circulation flow has a large variation in wind speed (the wind speed is highly turbulent), the pressure generated on the surface of the blade near the circulation flow tends to become unstable. The pressure fluctuation on the blade surface becomes a sound source and causes an increase in noise.
- the flow path of the mainstream becomes narrow, while the airflow of the mainstream requires the same amount of air as the indoor unit that is not thinned.
- the amount of the circulation flow tends to increase, so that the ratio of the circulation flow to the main flow increases.
- the influence of the circulation flow on the mainstream is increased. Therefore, it is important to suppress the influence of the circulation flow.
- Patent Document 1 proposes a technique for reducing the circulating flow (leakage flow) to reduce noise.
- the centrifugal blower of Patent Document 1 includes a plurality of main blades provided between the hub and the shroud and a plurality of small blades provided on the outer peripheral surface of the shroud, and the camber line of the shroud side blade element of the main blade is provided. It is characterized in that it is concave on the pressure surface side, or the camber line leading edge side of the shroud blade element of the main blade is inclined in the rotational direction.
- Patent Document 1 since the pressure difference between the shroud back area and the bell mouth channel area is reduced by the pressure increase effect by the small blades, the flow rate of the circulating flow can be reduced, and the main blade leading edge shroud side The flow rate is also reduced.
- Patent Document 1 describes that the flow can be made to follow the main blade by making the shape of the main blade as described above. Patent Document 1 describes that the noise can be reduced by these actions.
- An object of the present invention is to provide a centrifugal blower that can reduce noise caused by a circulating flow while suppressing an increase in weight and cost.
- the centrifugal blower of the present invention includes an impeller that rotates around a rotation shaft, and a bell mouth that guides air to the impeller.
- the impeller is a shroud provided with a gap in the radial direction between the end portion of the bell mouth, a plurality of blades arranged along the circumferential direction of the shroud and attached to the shroud, It has.
- the angle formed by the tangent of the camber line at the intersection of the camber line and the arc centered on the rotation axis and the tangent of the arc at the intersection in the blade cross section passing through the leading edge and the trailing edge of the blade is the blade angle.
- the blade has at least one of a reduced shape and a fixed shape.
- the decreasing shape is a shape in which the blade angle decreases as the intersection point shifts to the trailing edge side on the camber line in the front edge side portion of the blade section on the shroud side.
- the fixed shape is a shape in which the blade angle is constant even when the intersection point is shifted to the trailing edge side on the camber line in the front edge side portion of the blade cross section on the shroud side.
- (A) is sectional drawing which shows the blade
- (B) is sectional drawing which shows the blade
- (C) is this embodiment. It is sectional drawing which shows the blade
- (A) to (E) are graphs showing the relationship between the radial position of the blade and the blade angle in Modifications 1 to 5 of the present embodiment. It is a graph which shows the relationship between the radial position and blade
- (A) is sectional drawing which shows the blade
- (B) is sectional drawing which shows the blade
- (C) is conventional. It is sectional drawing which shows the blade
- centrifugal blower 51 according to an embodiment of the present invention and an indoor unit 31 of an air conditioner including the same will be described with reference to the drawings.
- the indoor unit 31 of the air conditioner of this embodiment shown in FIGS. 1 and 2 is a ceiling-embedded cassette indoor unit.
- the indoor unit 31 includes a substantially rectangular parallelepiped case 33 embedded in an opening provided in the ceiling 35, and a decorative panel 47 attached to the lower portion of the case 33.
- the decorative panel 47 is slightly larger in plan view than the case 33 and is exposed to the room in a state of covering the opening of the ceiling.
- the decorative panel 47 has a rectangular suction port 39 provided at the center thereof, and four elongated rectangular outlets 37 provided along each side of the suction port 39.
- the indoor unit 31 includes a centrifugal blower (turbo fan) 51, a fan motor 11, a heat exchanger 43, a drain pan 45, an air filter 41, and the like in a case 33.
- Centrifugal blower 51 includes an impeller 23 and a bell mouth 25.
- the fan motor 11 is fixed to the approximate center of the top plate of the case 33.
- the shaft 13 of the fan motor 11 extends in the vertical direction.
- the heat exchanger 43 has a flat shape with a small thickness.
- the heat exchanger 43 is disposed so as to surround the periphery of the impeller 23 in a state where it rises upward from a dish-shaped drain pan 45 extending along the lower end portion thereof.
- the drain pan 45 stores water droplets generated in the heat exchanger 43. The stored water is discharged through a drainage path (not shown).
- the air filter 41 has a size that covers the inlet of the bell mouth 25 and is provided between the bell mouth 25 and the inlet 39 along the inlet 39.
- the air filter 41 captures dust in the air when the air sucked into the case 33 from the suction port 39 passes through the air filter 41.
- the indoor unit 31 of the present embodiment is thinned, and the impeller 23 of the centrifugal blower 51 is also thinned in the direction of the rotation axis A along with it, so that noise due to the circulating flow C is likely to occur. is there. That is, the flow rate of the circulating flow C is considered to be proportional to the size of the gap G and the pressure difference (pressure loss of the indoor unit).
- the size of the gap G does not change, and the pressure difference tends to increase. This is because, even in the thinned indoor unit 31, in order to obtain the same air volume as the non-thinned indoor unit 31, the wind speed increases and the pressure loss increases. Therefore, in the thinned indoor unit 31, the circulation flow C increases.
- the impeller 23 includes a hub 15, a shroud 19, and a plurality of blades 21.
- the impeller 23 rotates about the rotation axis A.
- the hub 15 is fixed to the lower end portion of the shaft 13 of the fan motor 11.
- the hub 15 has a circular shape centered on the rotation axis A in plan view.
- the shroud 19 is arranged to face the front side F of the shaft 13 in the direction of the rotation axis A with respect to the hub 15.
- the shroud 19 has an air suction port 19a that opens in a circle around the rotation axis A.
- the outer diameter of the shroud 19 becomes larger toward the back side R in the direction of the rotation axis A.
- the bell mouth 25 is disposed so as to face the front side F in the direction of the rotation axis A with respect to the shroud 19.
- the bell mouth 25 has an opening 25a (suction port 25a) penetrating in the direction of the rotation axis A.
- a part of the rear side R of the bell mouth 25 is inserted into the shroud 19 from the air suction port 19a in a state where a predetermined gap is provided between the shroud 19 and the peripheral edge portion 19e of the air suction port 19a.
- the bell mouth 25 can guide the air sucked toward the back side R through the opening 25 a to the air suction port 19 a of the shroud 19.
- each blade 21 is a backward blade that is inclined in the direction opposite to the rotation direction DR (backward) with respect to the radial direction of the hub 15.
- Each blade 21 in the present embodiment has a three-dimensional shape extending in the direction of the rotation axis A while being twisted between the hub 15 and the shroud 19.
- wing 21 may not have the above twist.
- a plurality of irregularities 72 are provided on the trailing edge 62 of each blade 21, but these irregularities 72 can be omitted.
- each blade 21 includes a negative pressure surface 21 ⁇ / b> A (blade inner surface 21 ⁇ / b> A) facing radially inward in the impeller 23 and a positive facing radially outward. It has a pressure surface 21B (blade outer surface 21B), a front edge 61 that is a front edge when the impeller 23 rotates, and a rear edge 62 that is a rear edge. Further, the edge 21 ⁇ / b> F on the front side F of each blade 21 is joined to the inner surface of the shroud 19. An edge 21 ⁇ / b> R on the rear side R of each blade 21 is joined to the inner surface of the hub 15.
- the front edge 61 of the blade 21 includes a front side region 61F and a back side region 61R. Further, the front edge 61 has one end portion 61a on the front side F, the other end portion 61c on the back side R, and a bent portion 61b provided therebetween.
- the front side region 61F is a region from one end 61a to the bent portion 61b
- the back side region 61R is a region from the other end 61c to the bent portion 61b.
- One end 61a of the front edge 61 is connected to the end of the end edge 21F.
- the other end 61c of the front edge 61 is connected to the end of the end edge 21R.
- the front edge 61 has a bent shape at the bent portion 61b.
- the inclination angle of the front side region 61F with respect to the rotation axis A is larger than the inclination angle of the rear side region 61R with respect to the rotation axis A.
- the front side region 61F is inclined with respect to the rotation axis A in a direction away from the rotation axis A as it goes from the bent portion 61b to the one end portion 61a.
- all the blades 21 have the same shape. That is, each blade 21 has a feature of a blade angle ⁇ described later in order to reduce noise caused by the circulation flow C.
- all the blades 21 do not necessarily have the feature of the blade angle ⁇ , and at least one of the blades 21 may have only the feature of the blade angle ⁇ . .
- FIG. 4 is a cross-sectional view for explaining the main flow and the circulation flow.
- the impeller 23 When the impeller 23 is rotated by the fan motor 11, air is sucked into the case 33 of the indoor unit 31 from the suction port 39 of the indoor unit 31.
- the sucked air is guided to the air suction port 19 a of the shroud 19 of the impeller 23 by the inner peripheral surface of the bell mouth 25.
- the air of the mainstream M guided to the air suction port 19a by the inner peripheral surface of the bell mouth 25 is outside the impeller 23 by a plurality of blades 21 arranged along the circumferential direction between the hub 15 and the shroud 19. It is discharged in the direction away from the rotation axis A.
- Most of the air discharged from the impeller 23 is blown into the room through the air outlet 37 of the indoor unit 31.
- FIG. 6 is a graph showing the relationship between the radial position r of the blade 21 and the blade angle ⁇ in the present embodiment.
- FIG. 7A is a cross-sectional view showing a blade cross section S1 on the shroud 19 side in the present embodiment
- FIG. 7C is a cross-sectional view showing the blade cross-section S3 on the hub side in the present embodiment.
- the horizontal axis of the graph in FIG. 6 indicates the radial position r of the arc centered on the rotation axis A, and the origin O side of the horizontal axis is the front edge 61 side of the blade 21, and the origin O of the horizontal axis
- the leaving side is the trailing edge 62 side of the blade 21.
- An arc centered on the rotation axis A is indicated by a two-dot chain line in FIGS. 7A to 7C, for example.
- An angle formed with the tangent line L2 is defined as a blade angle ⁇ .
- the camber line CL is indicated by a broken line in each of FIGS.
- the broken line indicating the blade angle ⁇ on the shroud 19 side in FIG. 6 is when the intersection P is shifted from the front edge 61 to the rear edge 62 on the camber line CL in the blade cross section S1 on the shroud 19 side shown in FIG.
- the change in the blade angle ⁇ is shown.
- five intersection points P1 to P5 are shown as the intersection points P, but the broken lines shown in FIG. 6 are not only at the intersection points P1 to P5 but also at a larger number of intersection points P.
- the blade angle ⁇ is plotted.
- the blade cross section S1 on the shroud 19 side shown in FIG. 7A is a blade cross section in the boundary portion B1 (joint portion B1 between the shroud 19 and the blade 21) between the shroud 19 and the blade 21 shown in FIG. Specifically, it is a blade cross section at a boundary portion B1 between the inner peripheral surface of the shroud 19 and the edge 21F on the front side F of the blade 21.
- the blade cross section S1 shown in FIG. 7A is a projection of the blade cross section at the boundary portion B1 curved along the inner peripheral surface of the shroud 19 on the plane orthogonal to the rotation axis A in the direction of the rotation axis A.
- the blade cross section S3 on the hub 15 side shown in FIG. 7C is a blade cross section at the boundary B2 between the hub 15 and the blade 21 (joint portion B2 between the hub 15 and the blade 21) shown in FIG. Specifically, it is a blade cross section at the boundary B2 between the inner surface of the hub 15 and the edge 21R on the rear side R of the blade 21.
- the edge 21 ⁇ / b> R on the rear side R of the blade 21 and the inner surface of the hub 15 to which the blade 21 is joined are planes orthogonal to the rotation axis A.
- the blade cross section at the boundary portion B2 curved along the edge 21R is rotated on a plane orthogonal to the rotation axis A.
- the blade cross section S3 shown in FIG. 7C can be obtained.
- a blade section S2 at the center of the span shown in FIG. 7B is a blade section at the center of the blade height in the direction of the rotation axis A, and specifically, for example, the blade height of the trailing edge 62 of the blade 21. It is a blade
- region of the front edge 61 side is located in the blade
- a portion PL on the leading edge 61 side is referred to as a portion PL, and a region closer to the trailing edge 62 than a middle point (center) of the length of the camber line CL in the blade section S1 is referred to as a portion PT on the trailing edge 62 side in the blade section S1.
- the blade 21 has a blade angle ⁇ that decreases as the intersection point P shifts to the rear edge 62 side on the camber line CL in the portion PL on the front edge 61 side in the blade cross section S1 on the shroud 19 side. Has a reduced shape.
- the blade 21 Since the blade 21 has the above-described reduced shape in the portion PL on the front edge 61 side in the blade cross section S1 on the shroud 19 side, a region having a strong negative pressure on the shroud 19 side on the suction surface 21A of the blade 21 is provided. It can be moved from the leading edge to the trailing edge.
- FIG. 8 is a cross-sectional view for explaining that the negative pressure region N is moved away from the front edge to the rear edge side.
- a solid circle drawn on the suction surface 21A is a region N where the negative pressure is strong in the present embodiment, and a broken circle drawn on the suction surface 21A is a blade of a conventional centrifugal blower described later.
- the region N has a strong negative pressure.
- the blade 21 has the reduced shape as described above in the portion PL on the front edge 61 side in the blade cross section S ⁇ b> 1 on the shroud 19 side.
- the region N having a strong negative pressure at 21A can be moved away from the front edge 61 toward the rear edge 62 as compared with the conventional case.
- sucks the circulation flow C can be weakened.
- the flow rate of the circulation flow C is reduced, so that noise (interference sound between the main flow and the circulation flow) caused by the circulation flow C can be reduced.
- wing 21 has illustrated the case where it corresponds with the area
- the blade 21 has a shape in which the blade angle ⁇ continues to decrease from the front edge 61 to the rear edge 62 in the blade cross section S1 on the shroud 19 side.
- the blade angle ⁇ in the blade 21 continues to decrease, for example, the airflow at the suction surface reaches the trailing edge 62 as compared with the case where the blade angle ⁇ increases in the portion on the trailing edge 62 side. It becomes easy to follow. Thereby, it is possible to suppress the separation of the airflow in the vicinity of the trailing edge 62.
- the blade angle as the intersection point P shifts from the front edge 61 to the rear edge 62 side on the camber line CL.
- a region where the degree of decrease in ⁇ is small is provided.
- the broken line indicating the blade angle ⁇ includes a curved portion that protrudes to the lower left.
- the downward slope in the first half region (region closer to the origin O) of the portion PL on the front edge 61 side is the latter half region (region far from the origin O) of the portion PL on the front edge 61 side. ) Is greater than the downward slope of As described above, in the blade 21 according to the present embodiment, among the portion PL on the front edge 61 side, the gradient of the decrease in the blade angle ⁇ in the region closer to the front edge 61 is relatively large, while the portion on the front edge 61 side. In PL, an area is provided in which the gradient of decrease in the blade angle ⁇ decreases toward the trailing edge 62 side.
- the effect of moving the region having a strong negative pressure from the front edge 61 toward the rear edge 62 can be enhanced.
- the blade load on the shroud 19 side is suppressed from becoming extremely small on the suction surface by providing a region in which the blade angle ⁇ decreases gradually toward the trailing edge 62 side. As a result, the blade load on the shroud 19 side is maintained at a certain level on the suction surface.
- the region where the degree of decrease in the blade angle ⁇ is small in the portion PL on the front edge 61 side is provided in the entire region of the portion PL on the front edge 61 side. Instead, it is provided in the first half region of the portion PL on the front edge 61 side, and is not provided in the second half region of the portion PL on the front edge 61 side. In the latter half region of the portion PL on the front edge 61 side, the blade angle ⁇ is not small even when the intersection point P is shifted to the rear edge 62 side on the camber line CL, and is constant.
- the blade angle ⁇ decreases as the intersection point P shifts to the trailing edge 62 side on the camber line CL.
- a region where the degree is increased is provided.
- the broken line indicating the blade angle ⁇ is a convex curve on the upper right. That is, the downward slope in the latter half region (region far from the origin O) of the portion PT on the trailing edge 62 side is the first half region (region on the side close to the origin O) of the portion PT on the trailing edge 62 side.
- the blade angle ⁇ increases as the intersection point P shifts to the trailing edge 62 side on the camber line CL.
- the degree of reduction increases.
- the region where the blade angle ⁇ decreases is not necessarily provided in the entire region of the portion PT on the trailing edge 62 side, and is provided only in a partial region of the portion PT on the trailing edge 62 side. It may be.
- the region where the blade angle ⁇ decreases is provided in the entire region of the portion PT on the trailing edge 62 side. Instead, it is provided in the latter half region of the portion PT on the rear edge 62 side, and is not provided in the first half region of the portion PT on the rear edge 62 side. In the first half region of the portion PT on the trailing edge 62 side, the blade angle ⁇ is not small even when the intersection point P is shifted to the trailing edge 62 side on the camber line CL, and is constant.
- the blade cross section S1 on the shroud 19 side shown in FIG. 7A does not necessarily have to be a blade cross section at the boundary B1 between the shroud 19 and the blade 21.
- the blade cross section S ⁇ b> 1 may be a blade cross section on the shroud 19 side of the blade 21.
- wing 21 can be made into the following ranges, for example. That is, the shroud 19 side of the blade 21 is a region B3 having a predetermined width W in a direction away from the shroud 19 from the boundary B1 between the shroud 19 and the blade 21 as shown in FIG. Good.
- the predetermined width W is the same as the distance D between the end 25e of the bell mouth 25 and the shroud 19. Then, a blade cross section along the boundary B1 between the shroud 19 and the blade 21 through the front edge 61 and the rear edge 62 is selected within the range of the region B3, and the selected blade cross section is a plane orthogonal to the rotation axis A.
- the blade cross section S ⁇ b> 1 may be the one projected above in the direction of the rotation axis A.
- the force for sucking the circulating flow C can be effectively reduced. Specifically, it is as follows.
- the width of the circulating flow C immediately after passing through the gap G between the outer peripheral surface of the bell mouth 25 and the inner peripheral surface of the shroud 19 is the distance D between the end 25e of the bell mouth 25 and the inner peripheral surface of the shroud 19. It is about the same.
- This circulating flow C reaches the blades 21 shortly after passing through the gap G. Therefore, the region where the circulating flow C affects the blades 21 is related to the width of the circulating flow C.
- the blade is a projection of the selected blade cross section on the plane orthogonal to the rotation axis A in the direction of the rotation axis A.
- the cross section S1 preferably has the characteristics of the blade angle ⁇ as described above.
- the solid line indicating the blade angle ⁇ on the hub 15 side in FIG. 6 indicates that the intersection P is on the camber line CL from the front edge 61 in the blade cross section S3 on the hub 15 side shown in FIG.
- wing angle (beta) when shifting to the trailing edge 62 is shown.
- the blade angle ⁇ on the hub 15 side is a line that rises to the right (curved line) and increases from the front edge 61 toward the rear edge 62, but is not limited thereto.
- the alternate long and short dash line indicating the blade angle ⁇ at the center of the span in FIG. 6 indicates that the intersection P is on the camber line CL from the front edge 61 in the blade cross section S2 at the center of the span shown in FIG.
- wing angle (beta) when shifting to the edge 62 is shown.
- the blade angle ⁇ at the center of the span is a line (curved line) that rises to the right and increases from the front edge 61 toward the rear edge 62, but is not limited thereto.
- FIG. 11 is a graph showing the relationship between the radial position r of the blade 121 and the blade angle ⁇ in a conventional centrifugal blower.
- 12A is a cross-sectional view showing a blade cross section S11 on the shroud side in a conventional centrifugal blower
- FIG. 12B is a cross-sectional view showing a blade cross section S12 at the center of the span in the conventional centrifugal blower
- FIG. 12C is a cross-sectional view showing a blade cross section S13 on the hub side in a conventional centrifugal blower.
- the broken line indicating the shroud side blade angle ⁇ in FIG. 11 indicates the blade when the intersection P is shifted from the front edge 161 to the rear edge 162 on the camber line CL in the shroud side blade cross section S11 shown in FIG.
- the change of the angle ⁇ is shown.
- the one-dot chain line indicating the blade angle ⁇ at the center of the span in FIG. 11 is obtained when the intersection P is shifted on the camber line CL from the front edge 161 to the rear edge 162 in the blade center blade cross section S12 shown in FIG.
- a change in the blade angle ⁇ is shown.
- the blade cross sections S11 to S13 are blade cross sections at the same positions as the blade cross sections S1 to S3 in the present embodiment described above.
- the blade angle ⁇ is increased to the right (curved line) in any of the blade cross section S11 on the shroud side, the blade cross section S12 at the center of the span, and the blade cross section on the hub side.
- the region N where the negative pressure is strong is located near the front edge 161 on the negative pressure surface 21A of the blade 121, so that the circulating flow is sucked with a larger force than in the present embodiment.
- the flow rate of the circulating flow is increased as compared with the present embodiment, and the noise caused by the circulating flow is increased.
- the blade 21 has a shape in which the blade angle ⁇ continues to decrease from the front edge 61 to the rear edge 62 in the blade cross-section S1 on the shroud 19 side.
- 21 may have a shape as shown in Modifications 1 to 5 shown in FIGS. 10 (A) to 10 (E).
- 10 (A) to 10 (E) only the blade angle ⁇ in the blade cross section S1 on the shroud 19 side is shown, and the blade angle ⁇ in the blade cross section S2 in the center of the span and the blade on the hub 15 side are shown.
- the blade angle ⁇ in the cross section S3 is not shown.
- the blade 21 of Modification 1 shown in FIG. 10A has a blade angle ⁇ as the intersection point P shifts to the rear edge 62 side on the camber line CL in the portion PL on the front edge 61 side in the blade cross section S1 on the shroud 19 side.
- the blade 21 of the modified example 2 shown in FIG. 10B has a shape obtained by combining the reduced shape and a fixed shape in the portion PL on the front edge 61 side in the blade cross section S1 on the shroud 19 side.
- the blade angle ⁇ is constant even when the intersection point P is shifted toward the trailing edge 62 on the camber line CL in the portion PL on the front edge 61 side in the blade cross section S1 on the shroud 19 side.
- the fixed shape and the decreasing shape are arranged in this order toward the trailing edge 62 side.
- the intersection point P on the camber line CL is on the rear edge 62 side in the portion PL on the front edge 61 side in the blade cross section S1 on the shroud 19 side. Even if it is shifted, the blade angle ⁇ remains constant.
- the blade 21 of Modification 3 shown in FIG. 10C has a blade angle as the intersection point P shifts toward the trailing edge 62 on the camber line CL in the portion PT on the trailing edge 62 side in the blade cross section S1 on the shroud 19 side. It has a region where ⁇ decreases.
- the blade 21 of Modification 4 shown in FIG. 10D has a blade angle as the intersection point P shifts toward the trailing edge 62 on the camber line CL in the portion PT on the trailing edge 62 side in the blade cross section S1 on the shroud 19 side. It has a region where ⁇ increases.
- the blade 21 of Modification 5 shown in FIG. 10 (E) has a blade angle as the intersection point P shifts toward the trailing edge 62 on the camber line CL in the portion PT on the trailing edge 62 side in the blade cross section S1 on the shroud 19 side. It has a region where ⁇ decreases and a region where the blade angle ⁇ increases.
- the centrifugal blower 51 is applied to a ceiling-embedded indoor unit, but the present invention is not limited to this.
- the centrifugal blower of the present invention can also be applied to other types of indoor units such as a ceiling-mounted indoor unit, an air handling unit, a rooftop indoor unit such as a rooftop, and a floor-standing indoor unit.
- the centrifugal blower of the embodiment includes an impeller that rotates around a rotation shaft, and a bell mouth that guides air to the impeller.
- the impeller is a shroud provided with a gap in the radial direction between the end portion of the bell mouth, a plurality of blades arranged along the circumferential direction of the shroud and attached to the shroud, It has.
- the angle formed by the tangent of the camber line at the intersection of the camber line and the arc centered on the rotation axis and the tangent of the arc at the intersection in the blade cross section passing through the leading edge and the trailing edge of the blade is the blade angle.
- the blade has a reduced shape in which the blade angle decreases as the intersection point shifts to the trailing edge side on the camber line in the front edge side portion of the blade cross section on the shroud side, and the shroud side
- the blade section has at least one of the fixed shapes in which the blade angle is constant even when the intersection point is shifted to the trailing edge side on the camber line in the front edge side portion of the blade cross section.
- the blade has at least one of the reduced shape and the fixed shape in the front edge side portion of the blade section on the shroud side.
- the camber line which is an element that defines the blade angle, is a line connecting positions at equal distances from the pressure surface and the suction surface in the blade cross section.
- the blade has at least one of the reduced shape and the constant shape as described above in the front edge side portion in the blade cross section on the shroud side, so that the shroud side and the front edge side portion of the blade suction surface The wing load can be reduced.
- noise due to the circulation flow can be reduced without adding small blades as in the prior art, so that an increase in weight and an increase in cost can be suppressed.
- the front edge side portion in the blade cross section is the front edge side from the intermediate point of the camber line
- the rear edge side portion in the blade cross section is the rear edge side from the intermediate point of the camber line
- the blade may have a shape obtained by combining the reduced shape and the fixed shape in a portion on the front edge side in the blade cross section on the shroud side.
- the blade has a shape in which the blade angle continuously decreases from the front edge to the rear edge in the blade cross section on the shroud side.
- a region in which the degree of decrease in the blade angle becomes smaller as the intersection point on the camber line shifts from the front edge to the rear edge side is preferably provided.
- the gradient of the blade angle decrease in the region closer to the leading edge is relatively large, while in the portion on the leading edge side, the gradient of the blade angle decrease becomes smaller toward the trailing edge side.
- the part which becomes becomes that is, by locally increasing the degree of decrease in the blade angle in the region closer to the front edge, the effect of moving the region having a strong negative pressure from the front edge to the rear edge side can be enhanced.
- the blade load on the shroud side is suppressed from becoming extremely small on the suction surface. Thereby, the blade load on the shroud side is maintained at a certain level on the suction surface.
- a region on the rear edge side in the blade cross section on the shroud side is provided with a region in which the degree of decrease in the blade angle increases as the intersection on the camber line shifts to the rear edge side. It is preferable.
- the shroud side of the blades may be in the following range. That is, the shroud side of the blade is a region having a predetermined width in a direction away from the shroud from the boundary between the shroud and the blade, and the predetermined width is an end of the bell mouth. It may be the same size as the distance between the portion and the shroud.
- the force for sucking the circulating flow can be effectively weakened. Specifically, it is as follows.
- the width of the circulation flow immediately after passing through the gap between the outer peripheral surface of the bell mouth and the inner peripheral surface of the shroud is approximately the same as the distance between the end of the bell mouth and the inner peripheral surface of the shroud.
- This circulating flow reaches the blades shortly after passing through the gap.
- the region where the circulating flow affects the vanes is related to the width of the circulating flow. Therefore, the force of attracting the circulation flow is effectively obtained by adding the above-described blade angle characteristics to a region having a predetermined width which is the same as the distance between the end portion of the bell mouth and the shroud. Can be weakened.
- the plurality of blades preferably have the same shape.
- the air conditioner of the embodiment includes the centrifugal blower, noise can be reduced.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
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- Combustion & Propulsion (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
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Abstract
Description
図1及び図2に示す本実施形態の空気調和機の室内機31は、天井埋込型のカセット室内機である。この室内機31は、天井35に設けられた開口に埋め込まれる略直方体のケース33と、ケース33の下部に取り付けられた化粧パネル47とを備えている。化粧パネル47は、平面視の形状がケース33よりも一回り大きく、天井の開口を覆った状態で室内に露出している。化粧パネル47は、その中央部に設けられた矩形状の吸込口39と、この吸込口39の各辺に沿って設けられた細長い矩形状の4つの吹出口37とを有している。
図1~図3に示すように、羽根車23は、ハブ15と、シュラウド19と、複数の羽根21とを含む。羽根車23は、回転軸Aを中心に回転する。ハブ15は、ファンモータ11のシャフト13の下端部に固定されている。ハブ15は、平面視で回転軸Aを中心とする円形状を有している。
図4は、主流と循環流れについて説明するための断面図である。ファンモータ11によって羽根車23が回転すると、室内機31の吸込口39から室内機31のケース33内に空気が吸い込まれる。吸い込まれた空気は、ベルマウス25の内周面によって羽根車23のシュラウド19の空気吸込口19aに案内される。ベルマウス25の内周面によって空気吸込口19aに案内された主流Mの空気は、ハブ15とシュラウド19との間に周方向に沿って配列された複数の羽根21によって羽根車23からその外側(回転軸Aから離れる方向)に吐出される。羽根車23から吐出された空気の大半は、室内機31の吹出口37を通じて室内に吹き出される。
図6は、本実施形態における羽根21の半径位置rと羽根角度βとの関係を示すグラフである。図7(A)は、本実施形態におけるシュラウド19側の羽根断面S1を示す断面図であり、図7(B)は、本実施形態におけるスパン中央(回転軸A方向の羽根高さの中央)の羽根断面S2を示す断面図であり、図7(C)は、本実施形態におけるハブ側の羽根断面S3を示す断面図である。図6におけるグラフの横軸は、回転軸Aを中心とする円弧の半径位置rを示しており、横軸の原点O側は、羽根21における前縁61側であり、横軸の原点Oから離れる側は、羽根21における後縁62側である。回転軸Aを中心とする円弧は、例えば図7(A)~(C)において二点鎖線で示されている。
以上、本発明の実施形態について説明したが、本発明はこれらの実施形態に限定されるものではなく、その趣旨を逸脱しない範囲で種々変更、改良等が可能である。
Claims (8)
- 回転軸を中心に回転する羽根車と、
前記羽根車に空気を案内するベルマウスと、を備え、
前記羽根車は、前記ベルマウスの端部との間に径方向に隙間をあけて設けられたシュラウドと、前記シュラウドの周方向に沿って配列され、前記シュラウドに取り付けられた複数の羽根と、を備え、
前記羽根の前縁と後縁を通る羽根断面においてキャンバラインと前記回転軸を中心とする円弧との交点における前記キャンバラインの接線と、前記交点における前記円弧の接線とのなす角度を羽根角度とする場合において、
前記羽根は、
前記シュラウド側の羽根断面における前記前縁側の部分において前記キャンバライン上を前記交点が前記後縁側にシフトするにつれて前記羽根角度が減少する減少形状、及び
前記シュラウド側の前記羽根断面における前記前縁側の部分において前記キャンバライン上を前記交点が前記後縁側にシフトしても前記羽根角度が一定である一定形状の少なくとも一方の形状を有する遠心送風機。 - 前記羽根は、前記シュラウド側の前記羽根断面における前記前縁側の部分において、前記減少形状と前記一定形状を組み合わせた形状を有する、請求項1に記載の遠心送風機。
- 前記羽根は、前記シュラウド側の前記羽根断面において前記前縁から前記後縁まで前記羽根角度が減少し続ける形状を有する、請求項1に記載の遠心送風機。
- 前記シュラウド側の前記羽根断面における前記前縁側の部分において、前記キャンバライン上を前記交点が前記前縁から前記後縁側にシフトするにつれて前記羽根角度の減少の度合いが小さくなる領域が設けられている、請求項1~3の何れか1項に記載の遠心送風機。
- 前記シュラウド側の前記羽根断面における前記後縁側の部分において、前記キャンバライン上を前記交点が前記後縁側にシフトするにつれて前記羽根角度の減少の度合いが大きくなる領域が設けられている、請求項1~4の何れか1項に記載の遠心送風機。
- 前記羽根における前記シュラウド側とは、前記シュラウドと前記羽根との境界部から前記シュラウドに対して遠ざかる方向に所定の幅をもった領域であり、
前記所定の幅は、前記ベルマウスの端部と前記シュラウドとの距離と同じ大きさである、請求項1~5の何れか1項に記載の遠心送風機。 - 前記複数の羽根は同じ形状を有する、請求項1~6の何れか1項に記載の遠心送風機。
- 請求項1~7の何れか1項に記載の遠心送風機を備えた空気調和機。
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AU2014325384A AU2014325384B2 (en) | 2013-09-30 | 2014-09-12 | Centrifugal fan and air conditioner provided with the same |
EP14847547.8A EP3034885B1 (en) | 2013-09-30 | 2014-09-12 | Centrifugal fan and air conditioner provided with the same |
ES14847547T ES2784221T3 (es) | 2013-09-30 | 2014-09-12 | Ventilador centrífugo y aire acondicionado provisto del mismo |
CN201480052053.6A CN105579712B (zh) | 2013-09-30 | 2014-09-12 | 离心送风机以及具备该离心送风机的空调机 |
US15/025,711 US10024332B2 (en) | 2013-09-30 | 2014-09-12 | Centrifugal fan and air conditioner provided with the same |
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JP2013205128A JP5783214B2 (ja) | 2013-09-30 | 2013-09-30 | 遠心送風機及びこれを備えた空気調和機 |
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EP3034885A4 (en) | 2016-09-21 |
US10024332B2 (en) | 2018-07-17 |
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EP3034885B1 (en) | 2020-01-15 |
EP3034885A1 (en) | 2016-06-22 |
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US20160245298A1 (en) | 2016-08-25 |
AU2014325384A1 (en) | 2016-04-07 |
AU2014325384B2 (en) | 2018-02-01 |
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