WO2017077576A1 - 空気調和機の室外機および冷凍サイクル装置 - Google Patents
空気調和機の室外機および冷凍サイクル装置 Download PDFInfo
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- WO2017077576A1 WO2017077576A1 PCT/JP2015/080937 JP2015080937W WO2017077576A1 WO 2017077576 A1 WO2017077576 A1 WO 2017077576A1 JP 2015080937 W JP2015080937 W JP 2015080937W WO 2017077576 A1 WO2017077576 A1 WO 2017077576A1
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- curved surface
- rotation center
- impeller
- outdoor unit
- axial direction
- Prior art date
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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
- F24F1/06—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
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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
- F24F1/06—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 an outdoor unit and a refrigeration cycle apparatus used for an air conditioner.
- Outdoor units of air conditioners may be installed in narrow spaces due to architectural reasons. In this case, sufficient space cannot be obtained between the blowout side of the outdoor unit and the wall surface of the building. Thereby, there is no sufficient blowing air path on the blowing side of the outdoor unit, and the ventilation resistance is increased. For this reason, the radial direction velocity component of the blowing flow from the outdoor unit increases, and the axial direction velocity component decreases.
- Patent Document 1 The configuration of the outdoor unit when the outdoor unit is installed in the narrow space as described above is disclosed in, for example, Japanese Patent Application Laid-Open No. 4-251138 (see Patent Document 1).
- a ring is attached to an orifice outlet.
- the ring has an inner diameter that is slightly larger than the outer diameter of the impeller and has a waterdrop-like cross-sectional shape.
- Patent Document 1 since the airflow blown obliquely from the impeller is blown out along the inner peripheral surface of the ring and the wall surface of the orifice outlet by the ring, the performance of the blower is reduced and the noise is increased. Absent.
- Patent Document 1 does not consider that the radial velocity component of the blown flow changes in the circumferential direction depending on the suction side conditions. Depending on the conditions on the suction side, the airflow blown out from the impeller does not sufficiently follow the wall surface of the orifice outlet, so the ventilation resistance increases and the noise increases.
- the present invention has been made in view of the above problems, and an object thereof is to provide an outdoor unit of an air conditioner having low ventilation resistance and low noise.
- An outdoor unit of an air conditioner includes a casing, an impeller, and a bell mouth.
- the housing has an air outlet.
- An impeller is arrange
- the bell mouth surrounds the outer periphery of the impeller.
- the bell mouth has a straight pipe part and a curved part.
- the straight pipe portion surrounds the outer periphery of the impeller.
- the curved portion is located between the straight pipe portion and the air outlet and expands from the straight pipe portion toward the air outlet.
- the housing When viewed from the axial direction of the rotation shaft, the housing has a wall portion surrounding the impeller.
- the wall portion includes a first portion and a second portion located farther from the rotation center of the rotation shaft than the first portion.
- the bending portion includes a first curved surface portion positioned on a line connecting the rotation center and the first portion, and a second curved surface portion positioned on a line connecting the rotation center and the second portion. The radius of curvature of the second curved surface portion is larger than the radius of curvature of the first curved surface portion.
- the other outdoor unit of the air conditioner of the present invention includes a casing, an impeller, and a bell mouth.
- the housing has an air outlet.
- An impeller is arrange
- the bell mouth surrounds the outer periphery of the impeller.
- the bell mouth has a straight pipe part and a flare part.
- the straight pipe portion surrounds the outer periphery of the impeller.
- a flare part is located between a straight pipe part and an air blower outlet, and is expanded toward an air blower outlet from an impeller.
- the housing When viewed from the axial direction of the rotation shaft, the housing has a wall portion surrounding the impeller.
- the wall portion includes a first portion and a second portion located farther from the rotation center of the rotation shaft than the first portion.
- the flare portion includes a first extension portion positioned on a line connecting the rotation center and the first portion, and a second extension portion positioned on a line connecting the rotation center and the second portion.
- the first extending portion has a first dimension along the axial direction.
- the second extending portion has a second dimension along the axial direction. The second dimension is larger than the first dimension.
- the curvature radius of the curved portion of the bell mouth is larger than the portion where the distance is small. It is set large. Thereby, the flow of air can be made to follow a curved part in the part where the said distance is large. Therefore, ventilation resistance and noise can be reduced.
- the axial dimension of the flare portion is larger in the portion where the distance from the rotation center of the impeller to the wall surface of the housing is larger than the portion where the distance is small. Is set. Thereby, the flow of air can be made to follow a curved part in the part where the said distance is large. Therefore, ventilation resistance and noise can be reduced.
- FIG. 2 is a partial cross-sectional view (A) of a portion where the distance from the rotation center of the impeller to the wall surface of the casing in the outdoor unit shown in FIG. 1 is L1, and a partial cross-sectional view (B) of the portion where the distance is L2.
- sectional drawing (A) which shows the structure which the blowing part of a bellmouth protrudes from a front panel
- sectional drawing (B) which shows the structure where the blowing part of a bellmouth does not protrude from a front panel.
- an outdoor unit 10 for an air conditioner according to Embodiment 1 of the present invention includes a housing 1, an impeller 3, a bell mouth 4, a drive source 5, and a rotation. It mainly has a shaft 6 and an outdoor heat exchanger 7.
- the housing 1 includes a front panel 1a, a pair of left and right side panels 1b, a back panel 1c, a top panel 1d, a bottom panel 1e, and a separator 1f.
- the housing 1 has a box shape.
- a separator 1f is arranged in this internal space.
- the internal space of the housing 1 is partitioned into a machine room 11 and a blower room 12.
- a compressor (not shown) and the like are arranged in the machine room 11.
- an impeller 3 In the blower chamber 12, an impeller 3, a bell mouth 4, a drive source 5, a rotating shaft 6, an outdoor heat exchanger 7, and the like are arranged in the blower chamber 12.
- the outdoor heat exchanger 7 has, for example, an L shape in a plan view of FIG.
- the outdoor heat exchanger 7 is disposed along the side panel 1b and the back panel 1c of the housing 1.
- the planar view means a viewpoint viewed from above along a direction orthogonal to the upper surface of the top panel 1d.
- the housing 1 is provided with air inlets 1ba and 1ca on at least two surfaces.
- the air suction port 1ba is provided in the side panel 1b, and the air suction port 1ca is provided in the back panel 1c. Air can be sucked into the housing 1 from the outside of the housing 1 through each of the air suction ports 1ba and 1ca. The air sucked into the housing 1 from the air suction ports 1ba and 1ca can exchange heat with the outdoor heat exchanger 7.
- the housing 1 is provided with an air outlet 1aa.
- the air outlet 1aa is provided on the front panel 1a. It is possible to blow air from the inside of the housing 1 to the outside of the housing 1 through the air outlet 1aa. Thereby, the air heat-exchanged between the outdoor heat exchangers 7 is blown out of the housing 1 from the air outlet 1aa.
- the drive source 5 is, for example, a fan motor.
- the drive source 5 is disposed in front of the outdoor heat exchanger 7.
- the drive source 5 is attached to the housing 1 via a drive source support plate (not shown).
- the impeller 3 is attached to a drive source 5 with a rotating shaft 6 interposed.
- the impeller 3 is disposed in front of the drive source 5.
- the impeller 3 is for generating an air circulation for efficiently performing heat exchange in the outdoor heat exchanger 7.
- the impeller 3 is rotatable about the axis CL of the rotating shaft 6 by being given a driving force from a driving source.
- the impeller 3 has a function of introducing outside air into the blower chamber 12 through each of the air inlets 1ba and 1ca by the rotation and then discharging the outside through the air outlet 1aa.
- the bell mouth 4 is attached to the rear surface (rear surface) of the front panel 1a.
- the bell mouth 4 is disposed so as to surround the outer periphery of the impeller 3.
- the bell mouth 4 has a straight pipe portion 4a, a reduced diameter portion 4b, a curved portion 4c, and a flare portion 4d.
- the straight pipe portion 4a, the reduced diameter portion 4b, the curved portion 4c, and the flare portion 4d are integrally formed and constitute one component.
- the straight pipe portion 4 a surrounds the outer periphery of the impeller 3.
- the straight pipe portion 4a has a cylindrical shape and extends from the front to the rear while maintaining the diameter of the cylinder.
- the reduced diameter portion 4b is connected to the rear end of the straight pipe portion 4a.
- the reduced diameter portion 4b has a cylindrical shape, and is configured such that the opening diameter of the cylindrical shape decreases from the rear end toward the front end.
- the reduced diameter portion 4b has the smallest opening diameter at the joint portion with the straight pipe portion 4a.
- the curved portion 4c is connected to the front end of the straight pipe portion 4a.
- the curved portion 4c is located between the straight pipe portion 4a and the air outlet 1aa.
- the curved portion 4c is expanded in diameter from the straight pipe portion 4a toward the air outlet 1aa. Thereby, opening diameter OD (FIG. 2) of the curved part 4c is large toward the air blower outlet 1aa from the straight pipe part 4a.
- opening diameter OD (FIG. 2) of the curved part 4c is large toward the air blower outlet 1aa from the straight pipe part 4a.
- At least the inner peripheral surface of the curved portion 4c is configured to be curved in the cross section shown in FIG.
- the cross section shown in FIG. 2 is a cross section that includes the axis line CL of the rotating shaft 6 and is parallel to the axis line CL along the plane.
- the flare portion 4d is connected to the front end of the curved portion 4c.
- the flare portion 4d is located between the curved portion 4c and the air outlet 1aa.
- the flare portion 4d is enlarged in diameter from the curved portion 4c toward the air outlet 1aa.
- the opening diameter of the bell mouth 4 is increased from the curved part 4c toward the air outlet 1aa.
- At least the inner peripheral surface of the flare portion 4d is configured to be a straight line in the cross section shown in FIG.
- the front end (end on the front panel side) of the flare portion 4d is connected to the rear side surface of the front panel.
- the housing 1 has a wall portion that surrounds the impeller 3 when viewed from the axial direction of the rotating shaft 6 (in the direction of the axis CL in FIG. 2).
- the wall portion surrounding the impeller 3 includes, for example, a left side panel 1b, a top panel 1d, a bottom panel 1e, and a separator 1f in the drawing.
- the wall portions 1b, 1d, 1e, and 1f surrounding the impeller 3 have a substantially rectangular shape when viewed from the axial direction of the rotating shaft 6.
- the walls 1b, 1d, 1e, and 1f surrounding the impeller 3 are portions having different distances from the rotation center C of the impeller 3 (points on the axis CL in FIG. 2) when viewed from the axial direction of the rotary shaft 6. Have.
- the distances from the rotation center C of the impeller 3 are L1, L2, and L3, respectively. Yes.
- the part S1 is a part on the side panel 1b
- the part S2 is a part (corner part) where the side panel 1b and the top panel 1d intersect
- the part S3 is on the top panel 1d. Part.
- the distance L2 between the S2 and the rotation center C is larger than the distance L1 between the S1 and the rotation center C and the distance L3 between the S3 and the rotation center C. That is, the part S2 is located farther from the rotation center C than the parts S1 and S3.
- the curved portion 4c has, for example, a curved surface portion (first curved surface portion) P1, a curved surface portion (second curved surface portion) P2, and a curved surface portion (third curved surface portion) P3.
- the curved surface portion P1 is a portion located on a straight line SL1 (first line) connecting the rotation center C and the portion S1 when viewed from the axial direction of the rotation shaft 6 as shown in FIG.
- the curved surface portion P2 is a portion located on a straight line SL2 (second line) connecting the rotation center C and the portion S2 when viewed from the axial direction of the rotation shaft 6.
- the curved surface portion P3 is a portion located on a straight line SL3 (third line) connecting the rotation center C and the portion S3 when viewed from the axial direction of the rotation shaft 6.
- FIG. 3A The cross section of the outdoor unit 10 along the straight line SL1 is shown in FIG. 3A, and the cross section of the outdoor unit 10 along the straight line SL2 is shown in FIG. 3B.
- the curvature radius R2 of the curved surface portion P2 shown in FIG. 3 (B) is set to be larger than the curvature radius R1 of the inner peripheral surface of the curved surface portion P1 shown in FIG. 3 (A). Further, the curvature radius R2 of the inner peripheral surface of the curved surface portion P2 is set to be larger than the curvature radius of the curved surface portion P3 in FIG.
- the walls 1b, 1d, 1e, and 1f surrounding the impeller 3 and the rotation center C are viewed from the axial direction of the rotary shaft 6.
- the radius of curvature of the portion of the curved portion 4c (for example, the curved surface portion P2) having a large distance to is set larger than the radius of curvature of the portion of the curved portion 4c (for example, the curved surface portions P1 and P3) having a small distance.
- the curvature radius of the curved part 4c may change continuously in the circumferential direction centering on the rotation center C. As shown in FIG. 1 shows, the curvature radius of the curved part 4c may change continuously in the circumferential direction centering on the rotation center C. As shown in FIG. 1 shows, the curvature radius of the curved part 4c may change continuously in the circumferential direction centering on the rotation center C. As shown in FIG. 1 shows, the curvature radius of the curved part 4c may change continuously in the circumferential direction centering on the rotation center C.
- the front end 4e of the bell mouth 4 may protrude forward from the front panel 1a as long as the front end 4e is located behind the blowing grill 8. However, as shown in FIG. 4B, it is preferable that the front end 4e of the bell mouth 4 does not protrude forward from the front panel 1a.
- the radius of curvature of the curved portion 4c is constant in the circumferential direction around the rotation center C. For this reason, in the conventional bell mouth, it is not taken into consideration that the flow path of the blowout flow changes depending on the suction condition for each position in the circumferential direction of the bell mouth. Therefore, the air flow cannot sufficiently follow the curved portion 4c and the flare portion 4d of the bell mouth 4.
- the angle ⁇ 1 formed by the suction flow F1 and the straight pipe portion 4a of the bell mouth 4 is small in the cross section of the portion at the distance L1. For this reason, even if the curvature radius R1 of the curved portion 4c of the bell mouth 4 is relatively small, the flow can be along the small curvature radius R1.
- the wall portion of the housing 1 and the rotation center C are viewed from the axial direction of the rotation shaft 6.
- the curvature radius R2 of the curved surface portion P2 of the curved portion 4c having a large distance is set larger than the curvature radius R1 of the curved surface portion P1 of the curved portion 4c having a small distance.
- the radius of curvature R2 of the curved portion 4c is set to be large in the cross section where the distance L2 from the rotation center C is large, the flow can be greatly attracted to the outer peripheral side in the radial direction. Thereby, since a flow can be made to follow the curved part 4c and the flare part 4d, peeling is suppressed and ventilation resistance reduces.
- the front end 4e of the bell mouth 4 is not connected to the front panel 1a of the housing 1 and protrudes forward from the front panel 1a.
- the configuration in which the curved portion 4c and the flare portion 4d are provided on the front end side of the straight tube portion 4a of the bell mouth 4 has been described, but the flare portion 4d may not be provided.
- the curved portion 4 c is located from the front end of the straight tube portion 4 a to the entire front end 4 e of the bell mouth 4.
- the dimension along the axial direction of the straight pipe portion 4a in the cross section of the portion where the distance from the rotation center C to the wall portion of the housing 1 is a large distance L2 is shown in FIG. ),
- the distance L1 from the rotation center C may be smaller than the dimension along the axial direction of the straight pipe portion 4a in the cross section.
- the dimension along the axial direction of the flare portion 4d in the cross section where the distance L2 from the rotation center C is large is the distance L1 from the rotation center C as shown in FIG. May be larger than the dimension along the axial direction of the flare part 4d in a small cross section.
- Embodiment 2 The configuration of the present embodiment is different from the configuration of the first embodiment shown in FIGS. 1 to 5 in the configuration of the curved portion 4c of the bell mouth 4.
- the curvature radius of at least one curved surface portion of the curved surface portion having a large curvature radius and the curved surface portion having a small curvature radius is maintained in the circumferential direction around the rotation center C.
- the radius of curvature of the curved portion 4c within the range of the angle ⁇ 1 with the rotation center C as the center is constant in the circumferential direction. Further, the radius of curvature of the curved portion 4c within the range of the angle ⁇ 2 with the rotation center C as the center is constant in the circumferential direction.
- the range of the angle ⁇ 2 is a range in which the distance between the wall portion of the housing 1 and the rotation center C is relatively larger than the range of the angle ⁇ 1.
- the curvature radius of the curved portion 4c within the range of the angle ⁇ 1 has, for example, a curvature radius R1 shown in FIG.
- the curvature radius of the curved portion 4c within the range of the angle ⁇ 2 has a curvature radius R2 shown in FIG. 3B, for example.
- the radius of curvature of the curved portion 4c within the range of the angle ⁇ 2 is set to be relatively larger than the radius of curvature of the curved portion 4c within the range of the angle ⁇ 1.
- a boundary surface 4f is provided at the boundary of the curved portions 4c having different radii of curvature.
- the boundary surface 4f extends so as to intersect (for example, orthogonally cross) the circumferential direction.
- a boundary surface 4f is provided at the boundary between a portion with a large curvature radius and a portion with a small curvature radius of the curved portion 4c. For this reason, as shown in FIG. 6, since the swirling component Fc having the swirl component flowing through the curved portion 4c having a large curvature radius collides with the boundary surface 4f, the swirl component is suppressed, and the air volume increases. .
- Embodiment 3 The configuration of the present embodiment is different from that of the first embodiment shown in FIGS. 1 to 4 in the configuration of the bell mouth 4.
- the bending portion is omitted and the flare portion 4d is directly connected to the straight pipe portion 4a.
- the flare part 4d is located between the straight pipe part 4a and the air outlet 1aa.
- the flare portion 4d is enlarged in diameter from the impeller 3 toward the air outlet 1aa. Further, the joint portion between the straight pipe portion 4a and the flare portion 4d is angular.
- the flare portion 4d includes a portion (first extending portion) Q1 located on the cross section of the distance L1 having a relatively small distance from the rotation center C (axis CL), and FIG. As shown in (B), it has the part (2nd extension part) Q2 located in the cross section of the distance L2 whose distance from the rotation center C (axis line CL) is relatively large.
- the cross section at distance L1 in the present embodiment corresponds to the cross section of the portion at distance L1 in FIG. 1, for example, and the cross section at distance L2 in the present embodiment corresponds to the cross section at the portion of distance L2 in FIG. To do.
- the dimension Lb2 along the axial direction of the second extending portion Q2 is larger than the dimension Lb1 along the axial direction of the first extending portion Q1 as shown in FIG. 8 (A). It is getting bigger. 8B, the dimension along the axial direction of the straight pipe portion 4a in the cross section where the distance L2 from the rotation center C is large is the distance from the rotation center C as shown in FIG. L1 is smaller than the dimension along the axial direction of the straight pipe portion 4a in a cross section with a small cross section.
- the inclination angle of the first extending portion Q1 shown in FIG. 8A with respect to the straight pipe portion 4a is the same as the inclination angle of the second extending portion Q2 shown in FIG. 8B with respect to the straight pipe portion 4a.
- the inclination angle of the first extension portion Q1 shown in FIG. 8A with respect to the straight pipe portion 4a is different from the inclination angle of the second extension portion Q2 shown in FIG. 8B with respect to the straight pipe portion 4a. It may be.
- the dimension along the axial direction of the flare part 4d may be continuously changing in the circumferential direction centering on the rotation center C.
- the dimension Lb2 along the axial direction of the second extending portion Q2 of the flare portion 4d is the first extension. It is set to be larger than the dimension Lb1 along the axial direction of the existing portion Q1.
- the dimension Lb2 of the second extending portion Q2 is set to be large, so that the flow can be greatly attracted to the radially outer peripheral side. it can.
- peeling is suppressed and ventilation resistance reduces.
- the occurrence of turbulent flow is suppressed and the turbulent sound can be reduced by suppressing the separation, noise is reduced.
- Embodiment 4 The configuration of the present embodiment differs from that of the third embodiment shown in FIGS. 8A and 8B in the configuration of the bell mouth 4.
- the flare portion 4d is configured to maintain at least one of a small size and a large size along the axial direction of the flare portion 4d in the circumferential direction around the rotation center C. ing.
- the dimension along the axial direction of the flare portion 4d within the range of the angle ⁇ 1 with the rotation center C as the center is constant in the circumferential direction, and the rotation center C is the center.
- the dimension along the axial direction of the flare portion 4d within the range of the angle ⁇ 2 is constant in the circumferential direction.
- the range of the angle ⁇ 2 is a range in which the distance between the wall portion of the housing 1 and the rotation center C is relatively larger than the range of the angle ⁇ 1.
- the dimension along the axial direction of the flare part 4d within the range of the angle ⁇ 2 is set larger than the dimension along the axial direction of the flare part 4d within the range of the angle ⁇ 1.
- the bell mouth 4 of the present embodiment has a flare portion in which the dimension along the axial direction of the flare portion 4d is constant in the circumferential direction within a predetermined angular range and has different axial dimensions.
- the boundary surface 4f is provided at the boundary 4d.
- a boundary surface 4f is provided at the boundary between the large portion and the small portion along the axial direction of the flare portion 4d. For this reason, as shown in FIG. 9, since the swirling component Fc having the swirling component flowing through the flare portion 4d having a large dimension along the axial direction collides with the boundary surface 4f, the swirling component is suppressed. Will increase.
- Embodiment 5 The configuration of the present embodiment is different from the configurations of the third and fourth embodiments in the configuration of the connecting portion between the straight pipe portion 4a and the flare portion 4d.
- the connecting portion between the straight pipe portion 4a and the flare portion 4d has a rounded shape.
- the connecting portion between the straight pipe portion 4a and the flare portion 4d is configured by a curved portion 4c having a circular shape along a predetermined radius of curvature Ra in a cross section along the axis.
- the same effects as in the third and fourth embodiments can be obtained.
- the straight pipe portion 4a and the flare portion 4d are connected by the curved portion 4c having a circular shape. For this reason, an abrupt angle change is suppressed between the straight pipe part 4a and the flare part 4d, and as shown by an arrow Fd in FIG. 11, peeling that occurs at the connecting part between the straight pipe part 4a and the flare part 4d is suppressed. can do.
- Embodiment 6 The configuration of the present embodiment is different from the configurations of the third to fifth embodiments in the configuration of the connecting portion between the straight pipe portion 4a and the flare portion 4d.
- a curved portion having a rounded shape is provided at the connecting portion between the straight pipe portion 4a and the flare portion 4d. Further, the radius of curvature of the curved portion in the cross section of the portion where the distance from the rotation center C to the wall surface of the housing 1 is large is set larger than the radius of curvature of the curved portion in the cross section of the portion where the distance is small.
- FIG. 8A the connecting portion between the straight pipe portion 4a and the flare portion 4d in the cross section of the portion where the distance from the rotation center C to the wall surface of the housing 1 is small is shown in FIG.
- a curved portion 4c having a small radius of curvature Ra is disposed.
- FIG. 8B the connecting portion between the straight pipe portion 4a and the flare portion 4d in the cross section of the portion where the distance from the rotation center C to the wall surface of the housing 1 is large is shown in FIG. In this way, the curved portion 4c having a large curvature radius Ra is arranged.
- the curved portion in the cross section of the portion where the distance from the rotation center C to the wall surface of the housing 1 is small is, for example, the curved portion of the curved portion located on the straight line SL1 in FIG.
- the curved portion in the cross section of the portion where the distance from the rotation center C to the wall surface of the housing 1 is large is, for example, the curved portion of the curved portion located on the straight line SL2 in FIG.
- the same effects as those in the third to fifth embodiments can be obtained.
- the curvature radius Ra of the curved portion 4c changes according to the distance from the rotation center C to the wall surface of the housing 1, the flow of the curved portion 4c and the flare portion 4d as shown by the arrow Fd in FIG. Separation can be further suppressed, and noise can be further reduced.
- Embodiment 7 Next, the configuration of the seventh embodiment of the present invention will be described with reference to FIG.
- FIG. 13 shows an air conditioner 500 having the air conditioner (outdoor unit) described in the first embodiment as the refrigeration cycle apparatus.
- the air conditioning apparatus 500 of the present embodiment includes the outdoor unit 10, the indoor unit 200, and the refrigerant pipes 300 and 400 described in the first to sixth embodiments.
- the outdoor unit 10 and the indoor unit 200 are connected to each other by refrigerant pipes 300 and 400.
- a refrigerant circuit is configured, and the refrigerant circulates through the outdoor unit 10 and the indoor unit 200.
- the refrigerant pipe 300 is a gas pipe through which a gaseous refrigerant (gas refrigerant) flows.
- the refrigerant pipe 400 is a liquid pipe through which a liquid refrigerant (which may be a liquid refrigerant or a gas-liquid two-phase refrigerant) flows.
- the outdoor unit 10 includes, for example, a compressor 101, a four-way valve 102, an outdoor heat exchanger 7, an impeller 3, and a throttle device (expansion valve) 105.
- Compressor 101 compresses and discharges the sucked refrigerant.
- the compressor 101 has an inverter device or the like, and can arbitrarily change the capacity of the compressor 101 (the amount of refrigerant sent out per unit time) by arbitrarily changing the operation frequency.
- the four-way valve 102 switches the refrigerant flow between the cooling operation and the heating operation based on an instruction from a control device (not shown).
- the outdoor heat exchanger 7 performs heat exchange between the refrigerant and air (outdoor air).
- the outdoor heat exchanger 7 functions as a condenser during cooling operation, for example.
- the outdoor heat exchanger 7 performs heat exchange between the refrigerant compressed by the compressor 101 and air, and condenses and liquefies the refrigerant.
- the outdoor heat exchanger 7 functions as an evaporator, for example, during heating operation. At this time, the outdoor heat exchanger 7 performs heat exchange between the low-pressure refrigerant decompressed by the expansion device 105 and the air, and evaporates and vaporizes the refrigerant.
- An impeller 3 is provided in the vicinity of the outdoor heat exchanger 7 in order to efficiently exchange heat between the refrigerant and air.
- the rotational speed of the impeller 3 may be finely changed by arbitrarily changing the operating frequency of the drive source (fan motor) 5 by an inverter device.
- the expansion device 105 is provided to adjust the pressure of the refrigerant and the like by changing its opening. By the expansion device 105, the refrigerant condensed by the condenser is decompressed and expanded.
- the indoor unit 200 includes a load side heat exchanger 201 and a load side blower 202.
- the load side heat exchanger 201 functions as a condenser during heating operation, for example.
- the load-side heat exchanger 201 performs heat exchange between the refrigerant compressed by the compressor 101 and the air, condenses the refrigerant, and liquefies (or gas-liquid two-phase).
- the load side heat exchanger 201 functions as an evaporator, for example, during cooling operation. At this time, the load-side heat exchanger 201 performs heat exchange between the low-pressure refrigerant decompressed by the expansion device 105 and the air, and evaporates and vaporizes the refrigerant.
- the load side blower 202 is provided to adjust the flow of air that performs heat exchange in the load side heat exchanger 201.
- the operating speed of the load-side blower 202 is determined by, for example, user settings.
- the four-way valve 102 is switched so as to have a connection relationship indicated by a solid line.
- the high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 101 passes through the four-way valve 102 and flows into the outdoor heat exchanger 7.
- the refrigerant that has flowed into the outdoor heat exchanger 7 is condensed and liquefied by exchanging heat with the outdoor air sent by the impeller 3 and becomes liquid refrigerant.
- the liquid refrigerant flows into the expansion device 105, is decompressed by the expansion device 105, enters a gas-liquid two-phase state, and then flows out of the outdoor unit 10.
- the gas-liquid two-phase refrigerant that has flowed out of the outdoor unit 10 passes through the liquid pipe 400 and flows into the load-side heat exchanger 201 in the indoor unit 200.
- the refrigerant flowing into the load-side heat exchanger 201 is evaporated and gasified by exchanging heat with the indoor air sent by the load-side blower 202 to become a gas refrigerant. This gas refrigerant flows out of the indoor unit 200.
- the gas refrigerant that has flowed out of the indoor unit 200 passes through the gas pipe 300 and flows into the outdoor unit 10. Thereafter, the gas refrigerant passes through the four-way valve 102 and is sucked into the compressor 101 again. As described above, the refrigerant of the refrigeration cycle apparatus 500 circulates and air conditioning (cooling) is performed.
- the four-way valve 102 is switched so as to have a connection relationship indicated by a dotted line.
- the high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 101 passes through the four-way valve 102 and flows out of the outdoor unit 10.
- the gas refrigerant flowing out of the outdoor unit 10 passes through the gas pipe 300 and flows into the load side heat exchanger 201 in the indoor unit 200.
- the gas refrigerant that has flowed into the load-side heat exchanger 201 is condensed and liquefied by exchanging heat with the indoor air sent by the load-side blower 202, becomes liquid refrigerant, and flows out of the indoor unit 200.
- the liquid refrigerant flowing out from the indoor unit 200 passes through the liquid pipe 400 and flows into the outdoor unit 10. Thereafter, the liquid refrigerant is decompressed by the expansion device 105 to be in a gas-liquid two-phase state, and then flows into the outdoor heat exchanger 7. And the refrigerant
Abstract
Description
なお、参照符号については、図1~図12において同一の符号を付した要素は同一またはこれに相当するものであり、このことは明細書の全文において共通することである。
図1および図2に示されるように、本発明の実施の形態1に係る空気調和機の室外機10は、筐体1と、羽根車3と、ベルマウス4と、駆動源5と、回転軸6と、室外側熱交換器7とを主に有している。
図2に示されるように、羽根車3が回転することにより、室外側熱交換器7側から吸込み流れが発生する。この吸込み流れには動翼の効果が付与されるため、吸込み流れは径方向の速度成分が増大されつつ吹き出される。そのため、ベルマウス4の湾曲部4cの曲率半径の大小を調整することにより、径方向の速度成分が増大した流れをベルマウス4に沿わすことができる。これにより、ベルマウス4における流れの剥離が抑制され、通風抵抗を低減することができる。
本実施の形態の構成は、図1~図5に示す実施の形態1の構成と比較して、ベルマウス4の湾曲部4cの構成において異なっている。
本実施の形態の構成は、図1~図4に示す実施の形態1の構成と比較して、ベルマウス4の構成において異なっている。
実施の形態1で説明したように、図8(A)に示されるように回転中心Cからの距離が小さい断面では、吸い込み流れF3と直管部4aとが成す角度α1は小さくなる。一方、図8(B)に示されるように回転中心Cからの距離が大きい断面では、吸い込み流れF4と直管部4aとが成す角度α2は大きくなる。このように角度α2が大きくなる場合、吸い込み流れF4には羽根車3の中心に向かう方向の慣性が作用する。このため、フレア部4dの軸方向の寸法が一定である場合、径方向外周側への誘引が充分でなく、剥離が発生する。
本実施の形態の構成は、図8(A)および図8(B)に示す実施の形態3の構成と比較して、ベルマウス4の構成において異なっている。
本実施の形態の構成は、実施の形態3、4の構成と比較して、直管部4aとフレア部4dとの連接部の構成において異なっている。
本実施の形態の構成は、実施の形態3~5の構成と比較して、直管部4aとフレア部4dとの連接部の構成において異なっている。
次に、本発明の実施の形態7の構成について図13を用いて説明する。
Claims (8)
- 空気吹出口を有する筐体と、
前記筐体内に配置され、かつ回転軸を中心に回転可能な羽根車と、
前記羽根車の外周を取り囲むベルマウスとを備え、
前記ベルマウスは、
前記羽根車の外周を取り囲む直管部と、
前記直管部と前記空気吹出口との間に位置し、かつ前記直管部から前記空気吹出口に向かって拡径する湾曲部とを有し、
前記回転軸の軸方向から見て、前記筐体は、前記羽根車の外周を取り囲む壁部を有し、
前記軸方向から見て、前記壁部は、第1部分と、前記第1部分よりも前記回転軸の回転中心から離れて位置する第2部分とを有し、
前記軸方向から見て、前記湾曲部は、前記回転中心と前記第1部分とを繋ぐ線上に位置する第1曲面部と、前記回転中心と前記第2部分とを繋ぐ線上に位置する第2曲面部とを有し、
前記第2曲面部の曲率半径は前記第1曲面部の曲率半径よりも大きい、空気調和機の室外機。 - 前記湾曲部は、前記回転中心を中心とした周方向に、前記第1曲面部および前記第2曲面部の少なくとも一方の曲面部の曲率半径を維持するように構成されている、請求項1記載の空気調和機の室外機。
- 空気吹出口を有する筐体と、
前記筐体内に配置され、かつ回転軸を中心に回転可能な羽根車と、
前記羽根車の外周を取り囲むベルマウスとを備え、
前記ベルマウスは、
前記羽根車の外周を取り囲む直管部と、
前記直管部と前記空気吹出口との間に位置し、かつ前記羽根車から前記空気吹出口へ向かって拡径するフレア部とを有し、
前記回転軸の軸方向から見て、前記筐体は、前記羽根車を取り囲む壁部を有し、
前記軸方向から見て、前記壁部は、第1部分と、前記第1部分よりも前記回転軸の回転中心から離れて位置する第2部分とを有し、
前記軸方向から見て、前記フレア部は、前記回転中心と前記第1部分とを繋ぐ線上に位置する第1延在部と、前記回転中心と前記第2部分とを繋ぐ線上に位置する第2延在部とを有し、
前記第1延在部は前記軸方向に沿う第1寸法を有し、前記第2延在部は前記軸方向に沿う第2寸法を有し、前記第2寸法は前記第1寸法よりも大きい、空気調和機の室外機。 - 前記フレア部は、前記回転中心を中心とした周方向に前記第1寸法および前記第2寸法の少なくとも一方の寸法を維持するように構成されている、請求項3記載の空気調和機の室外機。
- 前記ベルマウスは、前記直管部と前記フレア部との間に位置する湾曲部をさらに有し、
前記湾曲部は曲面を有し、前記曲面は前記直管部の壁面と前記フレア部の壁面とを繋いでいる、請求項3または4記載の空気調和機の室外機。 - 前記軸方向から見て、前記湾曲部は、前記回転中心と前記第1部分とを繋ぐ線上に位置する第1曲面部と、前記回転中心と前記第2部分とを繋ぐ線上に位置する第2曲面部とを有し、
前記第2曲面部の曲率半径は前記第1曲面部の曲率半径よりも大きい、請求項5記載の空気調和機の室外機。 - 前記筐体は、前記空気吹出口を有するフロントパネルを有し、
前記ベルマウスの端部は前記フロントパネルに接続されている、請求項1~6のいずれか1項記載の空気調和機の室外機。 - 吸入した冷媒を圧縮して吐出する圧縮機と、前記圧縮機により圧縮された冷媒を凝縮する凝縮器と、前記凝縮器により凝縮された冷媒を減圧する絞り装置と、前記絞り装置により減圧された冷媒を蒸発させる蒸発器とを含む冷凍サイクル装置であって、
請求項1~7のいずれか1項記載の空気調和機の室外機は、前記凝縮器および前記蒸発器の一方を含む、冷凍サイクル装置。
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US15/749,826 US10495328B2 (en) | 2015-11-02 | 2015-11-02 | Outdoor unit of air conditioner and refrigeration cycle device |
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Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3739271A4 (en) * | 2018-02-19 | 2021-03-17 | Daikin Industries, Ltd. | FAN UNIT AND OUTDOOR UNIT OF AIR CONDITIONING WITH FAN UNIT |
WO2021255882A1 (ja) * | 2020-06-18 | 2021-12-23 | 三菱電機株式会社 | 空気調和機の室外機 |
EP4166859A4 (en) * | 2020-06-12 | 2023-07-12 | Mitsubishi Electric Corporation | AIR CONDITIONING SYSTEM OUTDOOR UNIT |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2017145370A1 (ja) * | 2016-02-26 | 2017-08-31 | 三菱電機株式会社 | 送風装置 |
JP2018084232A (ja) * | 2016-11-15 | 2018-05-31 | 三星電子株式会社Samsung Electronics Co.,Ltd. | 送風装置及びこれを用いた空気調和機用室外機 |
JP6879458B2 (ja) * | 2017-03-15 | 2021-06-02 | 株式会社富士通ゼネラル | 空気調和機の室外機 |
US10982863B2 (en) | 2018-04-10 | 2021-04-20 | Carrier Corporation | HVAC fan inlet |
WO2020070825A1 (ja) * | 2018-10-03 | 2020-04-09 | 三菱電機株式会社 | 室外機、及び冷凍サイクル装置 |
GB2599949B (en) * | 2020-10-16 | 2023-04-26 | Mosen Ltd | Aerodynamic spoiler for jetfan bellmouth |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11337126A (ja) * | 1998-05-29 | 1999-12-10 | Matsushita Refrig Co Ltd | 空気調和機の室外機 |
JP2013096622A (ja) * | 2011-10-31 | 2013-05-20 | Daikin Industries Ltd | 空気調和装置の室外ユニット |
JP2015129504A (ja) * | 2013-12-02 | 2015-07-16 | 三星電子株式会社Samsung Electronics Co.,Ltd. | 送風装置及び空気調和装置用室外機 |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH04251138A (ja) | 1991-01-07 | 1992-09-07 | Matsushita Refrig Co Ltd | セパレート形空気調和機の室外機 |
JPH0571768A (ja) | 1991-07-12 | 1993-03-23 | Mitsubishi Electric Corp | 空気調和機の室外ユニツト |
JP3757481B2 (ja) | 1996-08-27 | 2006-03-22 | ダイキン工業株式会社 | 空気調和機用室外機ユニット |
JP4380744B2 (ja) * | 2007-07-12 | 2009-12-09 | ダイキン工業株式会社 | 送風ユニット |
JP4823294B2 (ja) * | 2008-11-04 | 2011-11-24 | 三菱電機株式会社 | 送風機及びこの送風機を用いたヒートポンプ装置 |
CN103097821B (zh) * | 2010-09-14 | 2015-08-19 | 三菱电机株式会社 | 室外单元的送风机、室外单元及冷冻循环装置 |
US10145601B2 (en) * | 2011-12-19 | 2018-12-04 | Mitsubishi Electric Corporation | Outdoor unit and refrigeration cycle apparatus including the outdoor unit |
-
2015
- 2015-11-02 WO PCT/JP2015/080937 patent/WO2017077576A1/ja active Application Filing
- 2015-11-02 US US15/749,826 patent/US10495328B2/en active Active
- 2015-11-02 GB GB1803372.0A patent/GB2557130C/en active Active
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Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11337126A (ja) * | 1998-05-29 | 1999-12-10 | Matsushita Refrig Co Ltd | 空気調和機の室外機 |
JP2013096622A (ja) * | 2011-10-31 | 2013-05-20 | Daikin Industries Ltd | 空気調和装置の室外ユニット |
JP2015129504A (ja) * | 2013-12-02 | 2015-07-16 | 三星電子株式会社Samsung Electronics Co.,Ltd. | 送風装置及び空気調和装置用室外機 |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3739271A4 (en) * | 2018-02-19 | 2021-03-17 | Daikin Industries, Ltd. | FAN UNIT AND OUTDOOR UNIT OF AIR CONDITIONING WITH FAN UNIT |
US11162693B2 (en) | 2018-02-19 | 2021-11-02 | Daikin Industries, Ltd. | Fan unit, and outdoor unit of air conditioner comprising fan unit |
EP4166859A4 (en) * | 2020-06-12 | 2023-07-12 | Mitsubishi Electric Corporation | AIR CONDITIONING SYSTEM OUTDOOR UNIT |
WO2021255882A1 (ja) * | 2020-06-18 | 2021-12-23 | 三菱電機株式会社 | 空気調和機の室外機 |
JP7370466B2 (ja) | 2020-06-18 | 2023-10-27 | 三菱電機株式会社 | 空気調和機の室外機 |
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