WO2017043927A1 - 공기조화기의 실외기 - Google Patents
공기조화기의 실외기 Download PDFInfo
- Publication number
- WO2017043927A1 WO2017043927A1 PCT/KR2016/010194 KR2016010194W WO2017043927A1 WO 2017043927 A1 WO2017043927 A1 WO 2017043927A1 KR 2016010194 W KR2016010194 W KR 2016010194W WO 2017043927 A1 WO2017043927 A1 WO 2017043927A1
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- WIPO (PCT)
- Prior art keywords
- fixed
- angle
- fan
- inner circumferential
- discharge
- Prior art date
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Classifications
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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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D19/00—Axial-flow pumps
- F04D19/002—Axial flow fans
-
- 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
- F04D29/54—Fluid-guiding means, e.g. diffusers
-
- 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
- F04D29/54—Fluid-guiding means, e.g. diffusers
- F04D29/541—Specially adapted for elastic fluid pumps
-
- 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
- F04D29/54—Fluid-guiding means, e.g. diffusers
- F04D29/541—Specially adapted for elastic fluid pumps
- F04D29/542—Bladed diffusers
-
- 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
- F04D29/54—Fluid-guiding means, e.g. diffusers
- F04D29/541—Specially adapted for elastic fluid pumps
- F04D29/542—Bladed diffusers
- F04D29/544—Blade shapes
-
- 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
- F24F1/56—Casing or covers of separate outdoor units, e.g. fan guards
-
- 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
- F24F13/20—Casings or covers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2250/00—Geometry
- F05D2250/70—Shape
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
- F24F13/20—Casings or covers
- F24F2013/205—Mounting a ventilator fan therein
Definitions
- the present invention relates to an air conditioner, and more particularly, to a blower and an outdoor unit.
- the outdoor unit of the air conditioner provided with the rotating propeller fan and the some radial crosspiece provided downstream of the propeller fan is described.
- the radial crosspiece is formed to be inclined in a circular arc shape in the axial direction of the propeller fan, thereby converting and recovering the dynamic pressure energy of the swirl flow flowing from the propeller fan into static pressure energy. It has a function.
- the airflow generated by the rotation of a fan having a plurality of rotary vanes usually has a different blowing direction depending on the radial position of the fan. And depending on the difference of the shape of the fixed vane provided downstream of a fan, the dynamic pressure of the airflow which arises by rotation of a fan cannot be collect
- An object of the present invention is to improve static pressure efficiency in a blower provided with a fixed vane downstream of a fan.
- the present invention which achieves the above object is provided in a radial shape around the rotating shaft on a fan that rotates in a predetermined direction around the rotating shaft and in a traveling direction downstream of the airflow generated by the rotation of the fan, It has a plurality of fixed blades that are bent in the opposite direction to the rotation direction of the fan from the inner peripheral portion to the outer peripheral portion, wherein the fixed blade, the inlet angle formed by the inlet end and the rotary shaft in which the air flow flows, and the air flow is
- the tip angle formed by the discharge end and the inlet end connected to the discharge end and the rotating shaft are larger at the inner circumferential portion and the outer circumferential portion than the radial center portion, and the discharge angle formed by the discharge end and the rotating shaft is larger than 0 °.
- It is a blower which is 50 degrees or less.
- blade can be characterized in that the said discharge angle in an inner peripheral part and an outer peripheral part is larger than the said discharge angle in a radial center part.
- the fixed vane may be characterized in that the discharge angle is substantially constant from the inner circumference to the outer circumference.
- blade can be characterized in that the length of the said chord in an inner peripheral part and an outer peripheral part is longer than the length of the said chord in a radial center part.
- outer peripheral connection member for connecting the outer peripheral end of the fixed blade adjacent to the rotation direction of the fan may be further provided.
- this invention is installed radially centering on the said rotating shaft in the fan direction which rotates in a predetermined direction centering on a rotating shaft, and the advancing direction downstream of the airflow which arises by rotation of the said fan.
- a plurality of fixed vanes that are curved in an opposite direction to the rotation direction of the fan from an inner circumferential portion to an outer circumferential portion, wherein the fixed vanes have an inflow angle formed by an inflow end through which the airflow flows and the rotation shaft, and the The blades formed by the blades connecting the inlet end and the discharge end through which air flow is discharged are larger in the inner circumferential part and the outer circumferential part than the radial center part, and the discharge angle formed by the discharge end and the rotary shaft extends from the inner circumferential part to the outer circumferential part. It is a blower characterized by a substantially constant.
- this invention is equipped with the compressor which compresses a refrigerant
- the said blower The fan rotates in a predetermined direction about the rotational axis, and is provided radially around the rotational axis on the downstream side in the traveling direction of the airflow generated by the rotation of the fan, and is directed from the inner circumference to the outer circumference.
- the fixed vanes include an inflow angle formed by the inflow end through which the airflow flows in and the rotation shaft, a discharge end through which the airflow flows out, and the inflow end.
- the blade axis formed by the connected blade string and the rotating shaft is larger in the inner circumferential portion and the outer circumferential portion than the radial center portion,
- An outdoor unit characterized in that the discharge angle formed by the rotating shaft is greater than 0 ° and less than 50 °.
- this invention is equipped with the compressor which compresses a refrigerant
- the said blower The fan rotates in a predetermined direction about the rotational axis, and is provided radially around the rotational axis on the downstream side in the traveling direction of the airflow generated by the rotation of the fan, and is directed from the inner circumference to the outer circumference.
- the fixed vanes include an inflow angle formed by the inflow end through which the airflow flows in and the rotation shaft, a discharge end through which the airflow flows out, and the inflow end.
- the blade axis formed by the connected blade string and the rotating shaft is larger in the inner circumferential portion and the outer circumferential portion than the radial center portion,
- the discharge angle formed by the rotating shaft is substantially constant from the inner circumference to the outer circumference.
- FIG. 1 is a schematic configuration diagram of an air conditioner to which this embodiment is applied.
- FIG. 2 is a schematic cross-sectional view showing the configuration of a blower to which the present embodiment is applied.
- FIG 3 is a schematic top view showing the configuration of a blower to which the present embodiment is applied.
- FIG. 5 is a diagram showing a radial distribution with respect to the speed of airflow generated by the rotation of the fan of Embodiment 1.
- FIG. 7A to 7C are cross-sectional views of fixed vanes to which Embodiment 1 is applied.
- 8A to 8C are cross-sectional views of fixed vanes to which Embodiment 1 is applied.
- FIG. 9 is a view showing a relationship between the fixing blade of Embodiment 1 and the inner wall surface in the second housing, and FIG. 3 is a view seen from the IX direction.
- 11A to 11B are views for explaining the configuration of a fixed blade to which Modification Example 2 of Embodiment 1 is applied.
- 13A to 13C are cross-sectional views of fixed vanes to which Embodiment 2 is applied.
- 14A to 14C are cross-sectional views of the stator blades to which the second embodiment is applied.
- Embodiment 1 is a schematic configuration diagram of an air conditioner 1 to which Embodiment 1 is applied.
- the air conditioner 1 includes, for example, an outdoor unit 10 installed on a rooftop of a building, a plurality of indoor units 20 installed in each part of a building, and an outdoor unit 10 and an indoor unit 20.
- the piping 30 which is connected and flows through the refrigerant
- the outdoor unit 10 includes a compressor 11 for compressing a refrigerant, a 4-way switching valve 12 for switching a refrigerant flow path, and an outdoor heat exchanger 13 which is a device for moving heat from a high temperature object to a low object. ), An outdoor expansion valve 14 which expands and vaporizes the condensed refrigerant liquid to a low pressure and low temperature, and an accumulator 15 that separates the refrigerant liquid remaining without evaporation.
- the outdoor unit 10 includes a blower 50 that injects air into the outdoor heat exchanger 13 to promote heat exchange between the refrigerant and the air.
- the four-way switching valve 12 is connected to the compressor 11, the outdoor heat exchanger 13, and the accumulator 15 by piping.
- the compressor 11 and the accumulator 15 are connected by piping, and the outdoor heat exchanger 13 and the outdoor expansion valve 14 are connected by piping.
- the state at the time of heating operation is shown as the switching connection state of the 4-way switching valve 12.
- FIG. 1 the state at the time of heating operation is shown as the switching connection state of the 4-way switching valve 12.
- the outdoor unit 10 is provided with the control apparatus 18 which controls operation
- the indoor unit 20 injects air into the indoor heat exchanger 21 and the indoor heat exchanger 21 which are apparatuses for moving heat from a high temperature object to a low object inside, and refrigerant
- coolant is carried out.
- the two indoor units 20 are connected with respect to one outdoor unit 10, 1 or 3 or more indoor units 20 may be sufficient, and even if there are multiple outdoor units 10, do.
- the pipe 30 has a liquid refrigerant pipe 31 through which the liquefied refrigerant flows and a gas refrigerant pipe 32 through which the gas refrigerant flows.
- the liquid refrigerant pipe 31 is disposed so that the refrigerant flows between the indoor expansion valve 24 and the outdoor expansion valve 14 of the indoor unit 20.
- the gas refrigerant pipe 32 is disposed so that the refrigerant passes between the switching valve 12 of the outdoor unit 10 and the gas side of the indoor heat exchanger 21 of the indoor unit 20.
- FIG. 2 is a schematic cross-sectional view showing the configuration of a blower 50 to which the first embodiment is applied.
- 3 is a schematic top view which shows the structure of the blower 50 to which Embodiment 1 is applied, and respond
- the blower 50 of this embodiment is a fan 51 which rotates in the direction of arrow X about the rotation axis P, and generates airflow for cooling the outdoor heat exchanger 13 (refer FIG. 1), An electric motor 52 for rotationally driving the fan 51, a first housing 53 as an example of the first accommodating member accommodating the fan 51 and the electric motor 52, and a fan with respect to the first housing 53.
- the 2nd housing 54 as an example of the 2nd accommodation member connected to the advancing direction downstream of the airflow by 51 is provided.
- the fan 51 has three rotary vanes 51a.
- the blower 50 of this embodiment is provided so that the rotation axis direction of the fan 51 may become a perpendicular direction.
- the outdoor heat exchanger 13 demonstrated above is provided below the 1st housing 53 of the blower 50 perpendicularly.
- the air is sucked in from the vicinity of the outdoor heat exchanger 13 by the rotation of the fan 51, and the vertical direction is vertically upward from the downward direction as indicated by the broken arrow Y. Air flow is supposed to flow.
- the first housing 53 of the present embodiment has a cylindrical inner wall surface 531, and inside the first housing 53, air flow generated by the fan 51 is caused by the inner wall surface 531. A passage passing through is formed.
- the flow path formed by the inner wall surface 531 is the air flow direction from the downstream direction (upper side in FIG. 2) of the air flow. It has a so-called bell-mouse shape in which the cross-sectional area becomes large as it goes upstream (downward in FIG. 2).
- the 2nd housing 54 of this embodiment has the cylindrical inner wall surface 541, The inner side of the 2nd housing 54 makes the 1st housing 53 the inner wall surface 541.
- FIG. A flow path (outlet duct) through which air flow after passing is formed.
- the flow path formed by the inner wall surface 541 is the flow direction of an airflow from the advancing direction upstream (downward in FIG. 2) of airflow. It has an expanded shape in which the cross-sectional area becomes large as it goes to the downstream side (upward in FIG. 2).
- the inner diameter of the inner wall surface 541 of the second housing 54 is the same diameter as or larger than the inner diameter of the downstream direction of the air flow in the inner wall surface 531 of the first housing 53. Formed. For this reason, for example, compared with the case where the inner diameter of the inner wall surface 541 of the 2nd housing 54 is smaller than the inner diameter of the flow direction downstream of the airflow in the inner wall surface 531 of the 1st housing 53, The airflow easily flows through the space surrounded by the inner wall surface 541 and the fixed vane 60 described later.
- a plurality of fixed blades 60 extending from the inner wall surface 541 toward the rotating shaft P and the plurality of fixed blades provided in the vicinity of the rotating shaft P are provided.
- An inner circumferential connecting member 65 to which the 60 is connected is formed.
- the some fixing vane 60 is provided radially toward the inner wall surface 541 from the inner peripheral connection member 65, have.
- each of the fixing blades 60 has a plate-like shape having a substantially uniform thickness from the inner circumferential connecting member 65 side to the inner wall surface 541 side.
- wing 60 has the same shape mutually.
- the surface facing the upstream side of the rotation direction X of the fan 51 among the plate-shaped fixed blades 60 is made into the surface on the opposite side to the 1st surface 60p and the 1st surface 60p. It is called 2nd surface 60q (refer FIG. 7A mentioned later).
- the 1st surface 60p and the 2nd surface 60q of the adjoining fixed blade 60 oppose each other through the space for airflow to pass.
- produces by the rotation of the fan 51, and blows out from the 1st housing 53, has the several some formed in the 2nd housing 54.
- FIG. It passes through the clearance gap between the fixed blade
- wing 60 opposite to the fan 51 flows in is located in the opposite side to the inflow end 601 and the inflow end 601.
- the edge of the side from which air flow is discharged is called the discharge end 602. That is, when the air flows along the fixed wing 60, the inlet edge through which the air flow 60 of the fixed wing flows is the inlet end 601 and the air flow is discharged from the fixed wing 60 along the fixed wing 60.
- the outlet edge is the discharge end 602.
- the edge of the outer peripheral side connected to the outer periphery 60a and the inner peripheral connection member 65 is taken out of the edge of the outer peripheral side connected to the inner wall surface 541 of the 2nd housing 54 among the fixing blades 60. It is called the periphery 60b.
- FIG. 4 is a figure for demonstrating the relationship between the fixed blade
- the fixed blade 60 and the fan 51 are rotating shaft direction downstream of the fan 51 side. Corresponds to the drawing from.
- each of the fixing vanes 60 is an inner wall surface 541 from an inner circumferential portion connected to the inner circumferential connecting member 65 so that the radial center portion becomes convex when viewed from the downstream side in the rotational axis direction. It is a shape curved to the opposite side to the rotation direction X of the fan 51 as it goes to the outer peripheral part connected to the edge. That is, as shown in FIG. 4, each fixed vane 60 passes through the rotation center (rotation shaft P) of the fan 51, and the connection part of the fixed vane 60 and the inner peripheral connection member 65. As shown in FIG. It is a shape curved more on the opposite side to the rotation direction X of the fan 51 than the straight line (one dashed-dotted line of FIG. 4) extended to the wall surface 541. As shown in FIG.
- each fixed vane 60 when each fixed vane 60 is viewed from the downstream side in the rotational axis direction, the discharge end 602 is provided to be shifted in the rotation direction X with respect to the inflow end 601. have. That is, each of the fixed vanes 60 has a shape inclined in the rotation direction X as it goes from the inflow end 601 to the discharge end 602.
- the direction which goes upward from the downward direction in FIG. 2 as a direction along the rotation axis P of the fan 51 may only be called a rotation axis direction.
- the direction toward the inner wall surface 531 or the inner wall surface 541 side from the rotating shaft P may be called a radial direction.
- the radially inner side (rotation shaft P side) such as the fan 51 and the fixed vane 60 is called an inner circumferential side (inner circumferential portion), and the radially outer side (inner wall surfaces 531, 541 side) is an outer circumferential side. Sometimes called (outer part).
- FIG. 5 is a diagram showing a radial distribution with respect to the speed of airflow generated by the rotation of the fan 51 of the first embodiment. Specifically, in the blower 50 of Embodiment 1, FIG. 5 shows the radial direction of the axial velocity and the circumferential velocity of the airflow generated by the rotation of the fan 51 and ejected from the first housing 53. The distribution is shown.
- the airflow generated by the rotation of the fan 51 is spouted spirally from the first housing 53. That is, the airflow generated by the rotation of the fan 51 has a circumferential component that faces the rotation direction X in addition to the axial component that faces the rotation axis direction downstream.
- the speed of the axial component is set to the axial speed
- the speed of the circumferential component is set to the circumferential speed among the air flows generated by the rotation of the fan 51.
- occur
- the axial speed of is slowed down.
- the circumferential speed of the airflow generated by rotation of the fan 51 is faster than the radial center part.
- the airflow blown out from the inner peripheral part and the outer peripheral part of the 1st housing 53 compared with the airflow blown out from the radial center part of the 1st housing 53, there are many circumferential components.
- the airflow blown out from the inner peripheral part and the outer peripheral part of the 1st housing 53 is compared with the airflow blown out from the radial center part of the 1st housing 53 of the fan 51 It is in the state inclined in the rotation direction X (circumferential direction).
- FIG. 6 is a figure which shows the change according to the radial position of the inflow angle (theta) 1 and the discharge angle (theta) 2 in the fixed blade 60 to which Embodiment 1 is applied.
- 7A to 8C are cross-sectional views of the fixing vanes 60 to which the first embodiment is applied, and show cross-sectional shapes of the fixing vanes 60 along the rotational direction X of the fan 51.
- 7A and 8A correspond to the A-A cross-sectional view in FIG. 4, and show cross-sectional shapes in the outer peripheral portion of the fixed blade 60.
- 7B and 8B correspond to the B-B cross-sectional view in FIG. 4, and show cross-sectional shapes at the radially center portion of the fixed blade 60.
- 7C and 8C respond
- the inflow angle (theta) 1 of the fixed blade 60 refers to the angle which the inflow end 601 and the rotating shaft P of the fan 51 in the fixed blade 60 make
- the discharge angle ⁇ 2 of 60 refers to an angle formed by the discharge end 602 of the fixed vane 60 and the rotation shaft P of the fan 51.
- the center line L1 passing through the thickness center of the fixed wing 60 from the inlet end 601 to the discharge end 602. Draw.
- the fixing blade 60 has a plate shape with a substantially uniform thickness, and has a curved shape from the inflow end 601 to the discharge end 602.
- the center line L1 is a curved curve as shown in Fig. 7A.
- the angle which the tangent T1 of the center line L1 and the rotating shaft P in the inflow end 601 make is the inflow angle (theta) 1.
- the angle which the tangent T2 of the center line L1 and the rotating shaft P in the discharge end 602 make is discharge angle (theta) 2.
- discharge angle (theta) 2 is small compared with inflow angle (theta) 1, and becomes an angle close to the rotation axis direction.
- the airflow generated by the rotation of the fan 51 flows in from the inlet end 601 side of the fixed vane 60 and is discharged.
- the moving direction of airflow is changed to the rotation axis direction side, and dynamic pressure is collect
- the inflow angle (theta) 1 of the fixed blade 60 is the speed distribution (the distribution of axial velocity and circumferential velocity of the airflow which the fan 51 produces); Are continuously changed according to the radial position.
- the outer circumferential portion and the inner circumferential portion of the airflow generated by the fan 51 have a low axial velocity and the airflow ejection direction is inclined in the rotational direction X (circumferential direction), compared with the radial center portion.
- the inflow angle ⁇ 1 of the blade 60 is large.
- the inflow angle ( ⁇ 1) of the fixed blade 60 is larger in the axial velocity of the air flow generated by the fan 51 and the radial direction of the airflow is closer to the rotation axis direction than the outer peripheral portion and the inner peripheral portion. ) Is small.
- the inflow angle (theta) 1a in the outer peripheral part of the fixed blade 60, and the inflow angle (theta) 1c in the inner peripheral part of the fixed blade 60 are fixed blades. It is larger than the inflow angle (theta) 1b in the radial center part of (60) ((theta) 1a> (theta) 1b, (theta) 1c> (theta) 1b). In addition, the inflow angle (theta) 1 in the fixed blade 60 of this embodiment is larger than 0 degree.
- the fan 51 has a corresponding relationship between the inflow angle ⁇ 1 of the fixed vane 60 and the ejection direction of the airflow generated by the rotation of the fan 51.
- the airflow generated by the rotation of) is easily introduced from the inlet end 601 along the fixed blade 60.
- produced by the rotation of the fan 51 flows into the fixed blade 60 is reduced, and it becomes easy to change the direction of airflow by the fixed blade 60. .
- the innermost peripheral part (inner peripheral edge 60b) connected to the inner peripheral connection member 65 among the fixed vanes 60 is 0, and the outermost peripheral part (outer peripheral edge 60a) connected to the inner wall surface 541.
- the inflow angle (theta) 1 is a part where the radial position (relative value) is 50-60. The minimum value is to be taken.
- the inflow angle (theta) 1 of the fixed blade 60 is not limited to the example shown in FIG. 6,
- the fixed blade 60 of the present embodiment has a discharge angle such that the discharge angle ⁇ 2 of the inner circumferential portion and the outer circumferential portion becomes larger than the discharge angle ⁇ 2 of the radial center portion. ( ⁇ 2) is continuously changing.
- the discharge angle (theta) 2a in the outer peripheral part of the fixed blade 60, and the discharge in the inner peripheral part of the fixed blade 60 are shown.
- the angle ⁇ 2c is larger than the discharge angle ⁇ 2b at the radial center portion of the fixed blade 60 ( ⁇ 2a> ⁇ 2b, ⁇ 2c> ⁇ 2b).
- discharge angle (theta) 2 is larger than 0 degree and 50 degrees or less from the inner peripheral part to an outer peripheral part.
- the difference (theta) 1- (theta) 2 of inflow angle (theta) 1 and discharge angle (theta) 2 is compared with the radial center part of the fixed blade 60 in the outer peripheral part and the inner peripheral part of the fixed blade 60.
- the difference Da in the outer circumferential portion of the fixed blade 60 and the difference Dc in the inner circumferential portion are made larger than 20 °, and the radial center portion of the fixed blade 60 is increased.
- the difference Db in can be made into less than 20 degrees.
- the difference Da in the outer peripheral part of the fixed blade 60 is larger than the difference Dc in the inner peripheral part of the fixed blade 60 (Da> Dc) .
- the air-foil angle ⁇ 3 formed by the blade string S and the rotation shaft P is generated by the inflow angle ⁇ 1 of the fixed blade 60 and the fan 51.
- it is continuously changing according to the radial position. Specifically, as shown in FIGS.
- the blade angle ⁇ 3a in the outer circumferential portion of the fixed blade 60, and the blade angle in the inner circumferential portion of the fixed blade 60 ( (theta) 3c is large compared with the blade angle (theta) 3b in the radial center part of the fixed blade 60 ((theta) 3a> (theta) 3b, (theta) 3c> (theta) 3b).
- the blade angle ⁇ 3 in the fixed blade 60 of the present embodiment is larger than 0 °.
- the radius of the chord S is a radius so that the inflow angle (theta) 1 of the fixed blade 60 and the speed distribution of the airflow which generate
- the length La of the blade string Sa in the outer peripheral portion of the fixed blade 60 and the blade string Sc in the inner peripheral portion of the fixed blade 60 are shown.
- the length Lc is longer than the length Lb of the blade string Sb in the radially center portion of the fixed blade 60 (La> Lb, Lc> Lb).
- blade 60 rapidly spreads from the inflow end 601 to the discharge end 602.
- the fixed vane 60 has a sharply curved shape, in the process of moving the airflow flowing from the inlet end 601 side of the fixed vane 60 to the discharge end 602 side, the airflow is fixed stationary vane. It becomes easy to peel from the surface of 60.
- the fixed blade 60 makes it difficult to change the blowing direction of the air stream, and it becomes difficult to effectively recover the dynamic pressure of the air stream.
- the discharge angle ⁇ 2 is smaller than the inflow angle ⁇ 1 in order to change the ejection direction of the airflow flowing from the inflow end 601 side.
- the inflow angle (theta) 1 is made large in the inner peripheral part and outer peripheral part of the fixed blade 60 compared with the radial center part of the fixed blade 60. .
- the inflow angle ⁇ 1 is compared with the radial center portion.
- the lengths of the discharge angle ⁇ 2, the chord angle ⁇ 3, and the chord S are applied to the inflow angle ⁇ 1 and the fan 51. It changes according to the radial position so as to correspond to the velocity distribution of the airflow which arises.
- the discharge angle (theta) 2 and the chord angle (theta) 3 in the inner peripheral part and outer peripheral part of the fixed blade 60 are discharge angle in the radial center part of the fixed blade 60. It is larger than (theta) 2 and the blade
- the fixed blade 60 has such a structure, in the blower 50 of this embodiment, also in the inner peripheral part and outer peripheral part of the fixed blade 60 with a large inflow angle (theta) 1, the fixed blade 60 flows in. Sudden bending from the stage 601 to the discharge stage 602 is suppressed.
- the fixed wing 60 can collect
- discharge angle (theta) 2 is made into the range larger than 0 degree and 50 degrees or less from an inner peripheral part to an outer peripheral part (0 degree ⁇ (theta) 2). ⁇ 50 °).
- produced by rotation of the fan 51 changes with the shape of the fan 51 etc., it is about 60 degrees-70 degrees normally. Therefore, when the ejection angle ⁇ 2 is larger than 50 °, the difference between the ejection angle of the airflow generated by the rotation of the fan 51 and the ejection angle ⁇ 2 is small, so that it is difficult to deflect the airflow sufficiently toward the rotation axis direction. Lose.
- the discharge angle (theta) 2 of the stator blade 60 when the discharge angle (theta) 2 of the stator blade 60 is less than 0 degree, the blowing angle and the discharge angle (theta) 2 of the airflow generated by rotation of the fan 51 will face in the opposite direction to an axial direction. For this reason, when discharge angle (theta) 2 is less than 0 degree, the airflow generated by the rotation of the fan 51 collides with the fixed blade
- wing S in the outer peripheral part and an inner peripheral part is formed long compared with a radial center part, and is fixed in the outer peripheral part and inner peripheral part of the fixed blade 60.
- the length from the inflow end 601 to the discharge end 602 on the first surface 60p of the blade 60 is long. That is, in the outer peripheral part and the inner peripheral part of the fixed blade 60, compared with the radial center part of the fixed blade 60, the path
- the inflow angle ⁇ 1 is smaller than the inner peripheral portion and the outer peripheral portion.
- the discharge angle (theta) 2 and the chord angle (theta) 3 are made small compared with the inner peripheral part and the outer peripheral part. For this reason, even when the length of the blade string S is shortened, it is difficult for the fixed blade 60 to curve rapidly from the inlet end 601 to the discharge end 602, so that the fixed wing 60 curves rapidly. The problem by is hard to arise.
- the ratio of the axial component in the air flow generated by the rotation of the fan 51 is higher than the inner peripheral portion and the outer peripheral portion.
- the discharge angle (theta) 2 and the chord angle (theta) 3 of the radial center part of the fixed blade 60 are made small, and the length of the chord S is made into small.
- FIG. 9 is a figure which showed the relationship between the fixed blade 60 of Embodiment 1, and the inner wall surface 541 in the 2nd housing 54
- FIG. 3 is the figure seen from the IX direction.
- each fixed vane 60 is in contact with the inner wall surface 541 of the 2nd housing 54 inward. More specifically, as shown in FIG. 9, the outer circumferential edge 60a of the fixed blade 60 extends from the inflow end 601 side to the discharge end 602 side of the inner wall surface of the second housing 54. 541 is inward contacted.
- each fixed vane 60 is in the state supported by the inner wall surface 541 of the 2nd housing 54. As shown in FIG.
- the 2nd housing 54 in which the fixed blade 60 is supported is attached to the 1st housing 53.
- the inner wall surface 541 of the second housing 54 on which the fixed blade 60 is supported is the downstream direction of the air flow in the bell mouth-shaped inner wall surface 531 of the first housing 53. Is connected to.
- the inner diameter of the inner wall surface 541 of the second housing 54 is the same diameter as or larger than the inner diameter of the downstream direction of the air flow in the inner wall surface 531.
- the blower 50 of this embodiment is configured to support the plurality of fixed blades 60 by the inner wall surface 541 of the second housing 54, so that, for example, the force is applied to the fixed blades 60 from the outside. Even in the case of being applied, deformation or breakage of the fixed blade 60 is suppressed. And even if the fixed blade 60 is manufactured using an inexpensive manufacturing method such as resin molding, for example, since the deformation and breakage of the fixed blade 60 can be suppressed, the cost of the blower 50 can be reduced. have.
- the outer periphery 60a of the fixed blade 60 is in contact with the inner wall surface 541 of the 2nd housing 54, and the inner wall surface 541 is 1st.
- produced by the rotation of the fan 51 leaks to the outer peripheral side of the fixed blade 60 is suppressed.
- the blowing direction of the airflow generated by rotation of the fan 51 can be effectively changed by the fixed blade 60, and the static pressure efficiency of the blower 50 can be improved compared with the case where this structure is not employ
- the inflow angle (theta) 1 of the fixed blade 60 is changed continuously according to a radial position.
- the magnitude of the inflow angle ⁇ 1 is You may change stepwise according to the radial position of the stator blade 60.
- the discharge angle ⁇ 2, the blade angle ⁇ 3, the length L of the blade S, and the like of the fixed blade 60 may be changed stepwise according to the radial position of the fixed blade 60.
- FIG. 10 is a figure for demonstrating the structure of the fixed blade 60 to which the modification 1 of Embodiment 1 is applied, and is a figure which looked at the fixed blade 60 from the rotation axis direction.
- the some fixed blade 60 is connected to the radial center part, and has the annular support member 68 which supports the some fixed blade 60.
- the fixed blade 60 includes a plurality of inner circumferential fixed blades 61 extending from the inner circumferential connecting member 65 to the supporting member 68 by the supporting member 68, and the supporting member 68. ) Is divided into a plurality of outer circumferential fixing vanes 62 extending from the inner wall surface 541.
- each inner circumferential fixing blade 61 has the same shape
- each outer circumferential fixing blade 62 has the same shape mutually.
- the strength of the fixed blade 60 improves compared with the case where this structure is not employ
- the fixed blade 60 of this embodiment also has the inner circumferential fixed blade 61 so as to correspond to the radial distribution with respect to the speed of the airflow generated by the rotation of the fan 51, similarly to the example shown in FIG. 4 and the like.
- the shape of the outer circumferential fixed blade 62 is continuously changed in the radial direction. That is, in this embodiment, the shape which connected the inner circumferential fixed blade 61 and the outer circumferential fixed blade 62 becomes the same shape as the fixed blade 60 shown in FIG.
- the inner circumferential fixing blade 61 has an inflow angle ⁇ 1 (see FIG. 5) and a discharge angle ⁇ 2 (see FIG. 5) on the inner circumferential connecting member 65 side as compared with the support member 68 side.
- the chord angle ⁇ 3 (see FIG. 8A) is large, and the chord S is long.
- the outer circumferential fixing blade 62 has a larger inflow angle ⁇ 1, a discharge angle ⁇ 2, and a blade angle ⁇ 3 on the inner wall surface 541 side than the support member 68 side, and the blade side S. This is long.
- the number of the outer circumferential fixed blades 62 is provided more than the inner circumferential fixed blade 61. As shown in FIG. 10 for this reason, compared with the case where the number of the inner circumferential fixing blades 61 and the outer circumferential fixing blades 62 is the same, for example, it becomes suppressed that the space
- the fixed blade 60 was divided into two area
- the example is shown.
- a plurality of supporting members 68 may be provided in the radial direction to divide the fixed blade 60 into three or more regions. In this case, in each of three or more areas, you may change the number of the fixed blades 60, and the space
- FIG. 11A and 11B are views for explaining the configuration of the fixed blade 60 to which the second modified example of the first embodiment is applied.
- FIG. 11A is the figure which looked at the fixed blade 60 from the inclination direction with respect to the rotating shaft direction
- FIG. 11B is XIB-XIB sectional surface in FIG. 11A.
- the outer periphery 60a of the some fixed blade 60 has the structure connected by the ring-shaped outer peripheral connection member 66.
- the outer circumferential edge 60a on the second surface 60q of the plate-shaped fixed blade 60, and the rotational direction of the fixed blade 60 and the fan 51 is connected by the outer circumferential connecting member 66.
- the outer peripheral connecting member 66 which connects the several fixed blade 60 is a 1st housing. It is attached in the advancing direction downstream of the air flow in 53 (refer FIG. 2).
- Embodiment 2 of this invention is described.
- symbol is used and the detailed description is abbreviate
- FIG. 12 is a figure which showed the change according to the radial position of the inflow angle (theta) 1 and the discharge angle (theta) 2 in the fixed blade 60 to which Embodiment 2 is applied.
- 13A to 14C are cross-sectional views of the fixing vanes 60 to which the second embodiment is applied, and show cross-sectional shapes of the fixing vanes 60 along the rotational direction X of the fan 51.
- 13A and 14A correspond to sectional views in the outer circumferential portion (radial position 100) of the fixed blade 60
- FIGS. 13B and 14B show a radial center portion (radial direction) of the fixed blade 60.
- 13C and 14C correspond to sectional views of the inner circumferential portion (radial position 0) of the fixed blade 60.
- the fixed vane 60 to which Embodiment 2 is applied differs from the fixed vane 60 to which Embodiment 1 is applied in the magnitude
- size of discharge angle (theta) 2 is substantially constant from an inner peripheral part to an outer peripheral part.
- the discharge angle (theta) 2a in the outer peripheral part of the fixed blade 60, the discharge angle (theta) 2b in the radial center part of the fixed blade 60, and the inner peripheral part of the fixed blade 60 are shown.
- the discharge angle [theta] 2c in is approximately the same magnitude
- size of discharge angle (theta) 2 is “constantly constant"
- the difference between the maximum value and minimum value of the discharge angle (theta) 2 from the inner peripheral part of the fixed blade 60 to the outer peripheral part is less than 10 degrees. Means that.
- size of the discharge angle (theta) 2 is larger than 0 degrees, and is 50 degrees or less from the inner peripheral part to the outer peripheral part, (0 ° ⁇ 2 ⁇ 50 °).
- size of the discharge angle (theta) 2 is smaller than the inflow angle (theta) 1 from the inner peripheral part to the radial center part and the outer peripheral part.
- Embodiment 2 by making the discharge angle (theta) 2 of the fixed blade 60 substantially constant from the inner peripheral part to the outer peripheral part, the blowing direction of the airflow deflected and discharged from the fixed wing 60 is the It becomes substantially constant from an inner peripheral part to an outer peripheral part. For this reason, compared with the case where the discharge angle (theta) 2 changes according to a radial position, for example, the confusion of the airflow discharged from the fixed blade 60 is suppressed. As a result, in the blower 50 which applied the fixed vane 60 of this embodiment, generation
- the inflow angle (theta) 1a in the outer peripheral part of the fixed blade 60, and the inflow angle (theta) 1c in the inner peripheral part of the fixed blade 60 are fixed blades. It is larger than the inflow angle (theta) 1b in the radial center part of (60) ((theta) 1a> (theta) 1b, (theta) 1c> (theta) 1b).
- the inflow angle (theta) 1 of the fixed blade 60 has the relationship corresponding to the jet direction of the airflow which generate
- Embodiment 2 similar to Embodiment 1, the blade angle ⁇ 3a at the outer circumferential portion of the fixed blade 60 and the blade angle ⁇ 3c at the inner circumferential portion of the fixed blade 60 are fixed blades. Larger than the chord angle ⁇ 3b at the radial center portion of (60) ( ⁇ 3a> ⁇ 3b, ⁇ 3c> ⁇ 3b).
- Embodiment 2 similarly to Embodiment 1, the length La of the blade
- the length Lc is longer than the length Lb of the blade string Sb in the radially center portion of the fixed blade 60 (La> Lb, Lc> Lb).
- Embodiment 2 similarly to Embodiment 1, in the outer periphery part and inner periphery part with a high circumferential component in the airflow generate
- the support member 68 shown in FIG. 10 and the outer periphery connection member 66 shown in FIG. 11 can be applied also to the fixing blade 60 of Embodiment 2 similarly to Embodiment 1.
- the plurality of fixed vanes 60 are changed in the radial position so as to correspond to the blowing direction of the airflow generated by the rotation of the fan 51.
- the circumferential velocity energy (dynamic pressure) of the airflow generated by the rotation of the fan 51 can be effectively recovered by the plurality of fixed blades 60.
- the static pressure efficiency in the blower 50 can be improved compared with the case where this structure is not employ
- the noise produced by airflow in the blower 50 can be reduced.
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Abstract
Description
도 11A 내지 도 11B는, 실시형태 1의 변형예 2가 적용되는 고정 날개의 구성을 설명하기 위한 도면이다.
Claims (15)
- 회전축을 중심으로 회전하는 송풍팬;상기 송풍팬을 커버하는 송풍팬 하우징;상기 회전축 측에서 상기 송풍팬 하우징의 내주면 측으로 연장되고, 상기송풍팬의 반경 방향을 따라 만곡한 형상을 포함하는 고정 날개;를 포함하고,상기 고정 날개는 상기 송풍팬에 의해 형성되는 기류가 유입되는 측에 배치되는 유입단과 상기 회전축 측에 배치되는 내주부와 상기 송풍팬 하우징의 내주면 측에 배치되는 외주부 및 상기 내주부와 상기 외주부 사이에 배치되는 중앙부를 포함하고,상기 내주부 및 상기 외주부에서 상기 유입단과 상기 회전축이 이루는 제 1유입각은 상기 중앙부에서 상기 유입단과 접선과 상기 회전축이 이루는 제 2유입각보다 큰 공기조화기의 실외기.
- 제 1 항에 있어서,상기 고정 날개는 상기 기류가 상기 고정 날개를 따라 토출되는 측에 배치되는 토출단을 더 포함하고,상기 내주부 및 상기 외주부에서 상기 유입단과 상기 토출단을 연결한 제 1익현과 상기 회전축이 이루는 제 1익현각은 상기 중앙부에서 상기 유입단과 상기 토출단을 연결한 제 2익현과 상기 회전축이 이루는 제 2익현각보다 큰 공기조화기의 실외기.
- 제 2 항에 있어서,상기 토출단과 상기 회전축이 이루는 토출각은 0° 에서 50° 사이인 공기조화기의 실외기.
- 제 2 항에 있어서,상기 내주부 및 상기 외주부에서 상기 토출단과 상기 회전축이 이루는 제 1토출각은 상기 중앙부에서 상기 토출단과 상기 회전축이 이루는 제 2토출각보다 큰 공기조화기의 실외기.
- 제 2 항에 있어서,상기 토출단과 상기 회전축이 이루는 토출각은 상기 내주부로부터 상기 외주부를 따라 일정한 각도를 유지하는 공기조화기의 실외기.
- 제 2 항에 있어서,상기 토출단과 상기 회전축이 이루는 토출각은 상기 제 1유입각 및 상기 제 2유입각보다 작은 공기조화기의 실외기.
- 제 2 항에 있어서,상기 제 1익현의 길이는 제 2익현의 길이보다 긴 공기조화기의 실외기.
- 제 1 항에 있어서,상기 만곡한 형상은 상기 송풍팬의 반경 방향을 따라 상기 송풍팬의 회전방향과 반대 방향을 향해 만곡하게 형성되는 공기조화기의 실외기.
- 제 1 항에 있어서,상기 회전축 상에 배치되고 상기 고정 날개의 내주부와 접하게 마련되는 내주 연결 부재와, 상기 내주 연결 부재와 상기 송풍팬 하우징의 내주면 사이에 배치되고 환형 형상으로 마련되는 지지 부재를 더 포함하는 공기조화기의 실외기.
- 제 9 항에 있어서,상기 고정 날개는 복수로 마련되고,상기 복수의 고정 날개는 상기 내주 연결 부재와 상기 외주 연결 부재 사이에서 방사형으로 연장되는 제 1복수의 고정 날개와, 상기 지지 부재와 상기 송풍팬 하우징의 내주면 사이에서 방사형으로 연장되는 제 2복수의 고정 날개를 포함하고,상기 제 2복수의 고정 날개의 개수가 상기 제 1복수의 고정 날개의 개수보다 많은 공기조화기의 실외기.
- 회전축을 중심으로 회전하는 송풍팬;상기 송풍팬을 커버하는 송풍팬 하우징;상기 회전축 측에서 상기 송풍팬 하우징의 내주면 측으로 연장되고, 상기송풍팬의 반경 방향을 따라 만곡한 형상을 포함하는 고정 날개;를 포함하고,상기 고정 날개는 상기 송풍팬에 의해 형성되는 기류가 유입되는 측에 배치되는 유입단과 상기 기류가 토출되는 측에 배치되는 토출단을 포함하고,상기 유입단과 상기 회전축이 이루는 유입각은 상기 유입단과 상기 토출단을 연결한 익현과 상기 회전축이 이루는 익현각보다 크게 마련되고,상기 유입각은 상기 토출단과 상기 회전축이 이루는 토출각보다 크게 마련되는 공기조화기의 실외기.
- 제 11 항에 있어서,상기 고정 날개는 상기 회전축 측에 배치되는 내주부와 상기 송풍팬 하우징의 내주면 측에 배치되는 외주부 및 상기 내주부와 상기 외주부 사이에 배치되는 중앙부를 더 포함하고상기 내주부 및 상기 외주부에서의 유입각은 상기 중앙부에서의 유입각 보다 크게 마련되는 공기조화기의 실외기.
- 제 12 항에 있어서,상기 내주부 및 상기 외주부에서의 익현각은 상기 중앙부에서의 익현각보다 크게 마련되는 공기조화기의 실외기.
- 제 13항에 있어서,상기 내주부 및 상기 외주부에서의 토출각은 상기 중앙부에서의 토출각보다 크게 마련되는 공기조화기의 실외기.
- 제 14항에 있어서,상기 토출각은 0° 에서 50° 사이인 공기조화기의 실외기.
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KR1020177035358A KR102553475B1 (ko) | 2015-09-11 | 2016-09-09 | 공기조화기의 실외기 |
US15/759,180 US10578322B2 (en) | 2015-09-11 | 2016-09-09 | Outdoor unit of air conditioner |
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JP2015179119A JP2017053295A (ja) | 2015-09-11 | 2015-09-11 | 送風機および室外機 |
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Also Published As
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US20180259201A1 (en) | 2018-09-13 |
KR20180068901A (ko) | 2018-06-22 |
US10578322B2 (en) | 2020-03-03 |
KR102553475B1 (ko) | 2023-07-11 |
JP2017053295A (ja) | 2017-03-16 |
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