JP5460750B2 - Blower, outdoor unit and refrigeration cycle apparatus - Google Patents

Description

  The present invention relates to a blower or the like. In particular, it relates to the blade shape of a propeller fan.

  There is a blower (fan unit) that rotates a propeller fan having blades (propellers) to generate an air flow and blows air (cooling, exhaust heat, etc.). A blower having such a propeller fan is used in a wide range of fields such as an outdoor unit (outdoor unit) of an air conditioner, a refrigerator, a ventilation fan, a cooling device such as a computer.

  For example, in an outdoor unit of an air conditioner, an internal space is divided into a machine room in which a compressor or the like is installed, and a blower chamber through which air sucked into the blower flows by driving a propeller fan. For example, depending on the position where the machine room and the blower chamber are partitioned by increasing the size of the compressor and the like, the air flow in the blower chamber is directed toward the rotation center of the fan, and the outer side of the propeller fan May not be supplied with flow. Here, as the air passes through the outer periphery, the moment of the force that the propeller fan exerts on the air becomes stronger, increasing the amount of work, reducing the fan speed and reducing the noise on the outer periphery. It is better to let it pass.

  Therefore, in order to allow the air flowing into the rotation center side of the fan to pass through the outer peripheral side, the blade radius is increased from the front edge toward the bellmouth upstream end where the bellmouth and the propeller fan wrap (overlap). A blower has been proposed that gradually increases in size and secures the amount of suction from the side of the airflow toward the center of the fan (see, for example, Patent Document 1). On the other hand, a blower has also been proposed in which the blade radius of the front edge portion is reduced, a recess is provided in the rear edge, and the outermost peripheral portion is partially extended (see, for example, Patent Document 2).

Japanese Patent Laying-Open No. 2004-101154 (FIG. 1) Japanese Patent Laying-Open No. 2005-140081 (FIG. 1)

  For example, in the blower of Patent Document 1, if the fan diameter at the leading edge is reduced, it is possible to easily suck in the suction airflow that is biased toward the center, and the wing surface is not disposed outside the airflow, so the stagnant air is agitated. It will no longer induce turbulence. However, when the fan diameter is gradually increased to the upstream end where the lap where the propeller fan and bellmouth overlap in the axial direction is started, the wind speed changes rapidly due to the flow path reduction by the bell mouth and the flow path reduction by the fan diameter expansion. As a result, a vortex is generated and a turbulent flow is generated. When the turbulent flow collides with the wing and the bell mouth, the pressure fluctuation of the wall surface is generated, causing noise generation. Further, since the blade radius of the leading edge is reduced and the blade area is reduced, it is necessary to increase the number of rotations in order to obtain the required air blowing amount.

  Further, for example, in Patent Document 2, the rear edge of the outer peripheral part is partially extended, but the blade area is reduced by providing a recess in the rear edge of the inner peripheral side. For this reason, in order to obtain a required ventilation volume, the number of rotations must be increased, which may increase noise.

  Therefore, an object of the present invention is to obtain a blower or the like that can be driven with a reduced number of rotations with respect to the amount of blown air while preventing airflow disturbance.

  In order to solve the above problems, the present invention provides a propeller fan having a plurality of blades that rotate around a fan rotation shaft to generate a gas flow, and the outer periphery of the blades along the rotation direction of the propeller fan. A wall surface is formed outside the end so as to overlap a part of the blade as viewed from the direction perpendicular to the fan rotation axis direction, and a bell mouth for rectifying the gas is provided, and the air flow in the rotation direction of the propeller fan The uppermost flow point of the leading edge of the blade is at a position where the blade radius is shorter than the outermost blade diameter, which is the longest blade radius of the blade, and suction upstream of the gas flow in the fan rotation axis direction On the side, the position of the propeller fan and bell mouth is such that the edge of the wing is the outermost diameter of the wing at a position further upstream than the point where the propeller fan and bell mouth start to overlap. At the edge A portion having a blade radius longer than the trailing edge reference point corresponding to the blade radius of the most upstream point of the leading edge of the blade is retracted with respect to the rotation direction from the trailing edge reference point (becomes downstream of the air flow). ) Is in position.

  In the propeller fan of the present invention, not only is it easy to suck a flow that is biased toward the center of the fan, but the flow path does not rapidly shrink at the place where the fan outer peripheral portion and the bell mouth overlap, and a turbulent flow is not generated in the gap. As a result, pressure fluctuations occurring on the fan and bell mouth surfaces can be suppressed. In addition, since the blade trailing edge is retracted with respect to the rotation direction, that is, the blade length is increased, the work amount for the reduced blade radius and area at the leading edge can be compensated. There is no need to increase the rotational speed in order to obtain From the above, noise generated from the blower can be reduced.

It is the figure which looked at the propeller fan 1 of the air blower concerning Embodiment 1 of this invention from the front side. It is the figure which looked at the air blower concerning Embodiment 1 of this invention from the front side. It is the figure which looked at the air blower concerning Embodiment 1 of this invention from the side surface side. It is a figure which shows the outdoor unit which has an air blower of this Embodiment. It is a figure for demonstrating the flow of the air which flows in into a ventilation chamber. It is a schematic diagram which shows the flow of the air in the air blower which concerns on Embodiment 1 of this invention. It is a schematic diagram which shows the flow of the air in the blade surface which concerns on Embodiment 1 of this invention. It is the figure seen from the front side of the air blower concerning Embodiment 2 of this invention. It is the figure which looked at the air blower concerning Embodiment 2 of this invention from the side surface side. It is the figure seen from the front side of the air blower concerning Embodiment 3 of this invention. It is the figure seen from the front side of the air blower concerning Embodiment 4 of this invention. It is the figure which looked at the air blower concerning Embodiment 4 of this invention from the side surface side. It is a figure which shows the outdoor unit which concerns on Embodiment 5 of this invention. It is a figure which shows the cross section of the outdoor unit containing the fan rotating shaft. It is a block diagram of the air conditioning apparatus which concerns on Embodiment 6 of this invention.

Embodiment 1 FIG.
FIG. 1 is a view of a propeller fan 1 of a blower according to Embodiment 1 of the present invention as viewed from the front side. With respect to the direction in which the air flows by the rotation of the propeller fan 1, the surface on the downstream side is the front. The propeller fan 1 according to the first embodiment is configured by attaching a plurality of blades 3 (three in the present embodiment) radially around a boss (column) 2.

  FIG. 2 is a view of the blower according to Embodiment 1 of the present invention as seen from the front side. Here, only the propeller fan 1 and the bell mouth 7 are shown in order to simply show the relationship between the propeller fan 1 and the bell mouth 7. The propeller fan 1 rotates in the rotation direction 13 around the fan rotation shaft 9. The rotation center 12 is a position where the fan rotation shaft 9 penetrates the propeller fan 1 (the center of the boss 2). The blades 3 are attached radially at the same interval around the fan rotation shaft 9. Here, the front edge 15 from the boss root 14 of the wing 3 to the end in the rotational direction is the rear edge 16, and the radially outer peripheral portion is the outer peripheral portion 17. In addition, a bell mouth 7 is disposed around the outer periphery of the wing 3 so as to cover a part of the propeller fan 1.

  The broken line shown in FIG. 2 shows the line on the concentric circle centering on the rotation center 12 of the propeller fan 1 as an auxiliary line. A broken line A is a line having the blade outermost diameter Ro as the blade radius. A broken line B is a line having Ri (<Ro) smaller than the blade outermost diameter as a blade radius. Here, at the leading edge 15, the blade radius (the distance between the leading edge most upstream point and the rotation center 12) of a point 18 (front edge most upstream point) located upstream from the air flow in the rotation direction 13 is the same. Let Ri be.

  In the blade 3 of the propeller fan 1 in the present embodiment, when the shape of the outer peripheral portion 17 is traced back in the rotational direction 13 from the leading edge most upstream point 18, the blade radius gradually increases from the broken line B toward the broken line A. It gets bigger. And it continues to the trailing edge 16 while maintaining the blade radius (blade outermost diameter) of the broken line A. In FIG. 2, the trailing edge (the trailing edge outer periphery) of the outer peripheral side of the intersection 19 of the trailing edge 16 and the broken line B (the point at which the distance from the rotation center 12 at the trailing edge 16 is Ri. Part) 20 a and the rear edge (rear edge inner peripheral part) 20 b on the inner peripheral side are retracted with respect to the rotation direction 13. Here, in the line segment connecting the rotation center 12 and a certain position of the blade surface, another line segment to be compared with respect to a certain line segment is located on the rotation direction 13 (direction in which the blade 3 advances). Sometimes the position related to another line segment is said to be moving forward, and the case of the direction opposite to the rotation direction 13 is expressed as moving backward. In the trailing edge 16, a line segment connecting the rotation center 12 and the points on the trailing edge outer peripheral portion 20a and the trailing edge inner peripheral portion 20b is more than a line segment connecting the rotation center 12 and the trailing edge reference point 19. Retreating. For this reason, the trailing edge reference point 19 is the most upstream point located in the most upstream with respect to the air flow in the rotation direction 13.

  FIG. 3 is a view of the blower according to Embodiment 1 of the present invention as viewed from the side. FIG. 3 is a diagram obtained when the blade 3 is projected on a section parallel to the axis including the fan rotation shaft 9 and is projected, and in order to grasp the position in the direction of the fan rotation shaft 9, a three-dimensional blade surface is obtained. It is a meridional view that represents as a two-dimensional section. The airflow 10 represents the air flowing by the rotation of the propeller fan 1.

  As described above, the distance between the leading edge most upstream point 18 of the leading edge 15 and the rotation center 12 is the blade radius Ri, and the blade radius increases to the blade outermost diameter Ro as it goes downstream. In FIG. 3, the bell mouth 7 is represented by a cross-sectional shape. A wrap start point 22 is an upstream side of the wrap region 21 where the propeller fan 1 and the bell mouth 7 wrap (overlap) when viewed from the side surface with respect to the direction of the fan rotation axis 9. In the propeller fan 1 of the present embodiment, the end point 23 whose blade radius is the blade outermost diameter Ro is located upstream of the wrap start point 22 with respect to the air flow in the direction of the fan rotation axis 9.

  FIG. 4 is a diagram showing an outdoor unit having the blower of the present embodiment. In the present embodiment, for example, an outdoor unit 100 of an air conditioner will be described. FIG. 4A is a diagram illustrating an appearance of the outdoor unit 100. FIGS. 4B and 4C are diagrams for explaining the internal configuration viewed from the front side and the back side, respectively. The space inside the outdoor unit 100 is divided into a blower chamber for allowing air to pass through the outdoor heat exchanger 4 having fins and pipes (heat transfer tubes), and a refrigerant to the outdoor heat exchanger 4 by a separator (partition plate) 6. It is divided into a machine room in which the compressor 5 to be sent is placed. For example, as shown in FIG. 4C, the blowout side opening portion of the bell mouth 7 and the opening portion of the outer panel 8 arranged so as to surround the outer periphery of the propeller fan 1 are continuous, and the bell mouth 7 and the outer panel are continuous. There is also an outdoor unit in which 8 is integrally formed. As described above, the propeller fan 1 and the bell mouth 7 overlap with each other in the lap region 21, and the propeller fan 1 on the inner peripheral side of the bell mouth 7 is located inside and outside the outdoor unit 100 (outside the blower room, outside the fan, Partitioning between the blowout side).

  FIG. 5 is a view for explaining the flow of air flowing into the blower chamber. Next, the flow of air will be described with reference to a horizontal sectional view including the fan rotation shaft 9 when the outdoor unit 100 is viewed from the upper surface side. Here, attention is paid to the airflow 10 passing through the side closer to the machine room among the airflow upstream (suction side) of the air flow in the direction of the fan rotation shaft 9 with respect to the propeller fan 1. The airflow 10 passes through the outdoor heat exchanger 4 on the upstream side in the direction of the fan rotation shaft 9 with respect to the propeller fan 1, and flows into the propeller fan 1 along the separator 6. For example, when the capacity of the equipment is high and the compressor 5 is large, the volume of the machine room increases, and the corner 11 of the separator 6 becomes steep on the air blowing chamber side. Then, at the corner portion 11, air may be separated (peeled) without being able to follow the wall surface of the separator 6. The separated air flow is directed toward the center (rotary axis) of the propeller fan 1. For this reason, the air flowing into the propeller fan 1 is biased toward the center side, and no flow is supplied to the outer peripheral side of the propeller fan 1.

  Here, the work that the propeller fan 1 imparts to the air increases as the air passing through the outer peripheral side has a stronger moment of force. For this reason, considering the necessary energy given to the air to overcome the resistance of a certain outdoor unit air passage, the rotation speed of the propeller fan 1 can be reduced by passing the outer peripheral side. Further, when the number of rotations is reduced, the number of interferences that the blades 3 cut off air is reduced, and noise can be suppressed. Therefore, when the airflow 10 flows into the center side of the propeller fan 1, the work amount that the propeller fan gives to the air decreases. As a result, the required number of revolutions increases, which may increase noise.

  In the blower of the present embodiment, air whose main flow is biased toward the center side due to the separation generated in the separator 6 of the air conditioner flows in from the front edge 15 side. The most upstream point 18 of the leading edge of the blade 3 is located on the inner peripheral side with respect to the outermost diameter of the blade in accordance with the flow field where the suction airflow approaches the center side. The airflow 10 passing over the blade surface gradually spreads toward the outer periphery due to centrifugal force. Since propeller fan 1 of the present embodiment has a shape in which the outer diameter of the blade is increased toward the downstream direction, airflow 10 toward the outer peripheral portion due to centrifugal force does not leak from blade 3, and the work given to airflow 10 from blade 3 The amount can be secured.

  FIG. 6 is a schematic diagram showing the air flow in the blower according to Embodiment 1 of the present invention. Here, FIG. 6A shows the positional relationship between the propeller fan 1 and the bell mouth 7 in the present embodiment. FIG. 6B shows the positional relationship between a conventional propeller fan and a bell mouth for comparison. Here, the air flow 24 near the outer periphery is considered. For example, at the wrap start point where the propeller fan 1 and the bell mouth 7 wrap, a reduced air passage that narrows the air flow path is formed. As shown in FIG. 6B, at the lap start point 22, the propeller fan 1 and the bell mouth are positioned so that the outer diameter of the blade increases (fluctuates) to the outermost diameter of the blade. Since the gap between the mouse 7 is reduced from both sides of the propeller fan and the bell mouth, the air path is rapidly reduced. The airflow increases in the rapidly reduced wind path, and a vortex 25 is generated due to the speed difference from the low-speed airflow on the bellmouth surface. When the vortex 25 is generated, the turbulence of the airflow is increased on the blade surface and the bell mouth surface, and a strong pressure fluctuation is generated, thereby increasing noise.

  In the blower of the present embodiment, the end point 23 where the blade radius is the blade outermost diameter Ro is upstream of the air flow in the direction of the fan rotation shaft 9 from the wrap start point 22 with the bell mouth 7. To position. For this reason, the blade radius does not fluctuate at the wrap start point 22, and the flow path reduction of the gap is only on one side (only from the bell mouth 7 side). Therefore, the rate of change of the channel width is smaller than that of a conventional blower. As a result, by suppressing the vortex generated at the time of reduction, the pressure fluctuation generated on the surface of the blade 3 or the bell mouth 7 can be suppressed, and noise can be reduced.

  FIG. 7 is a schematic diagram showing the air flow on the blade surface according to the first embodiment of the present invention. As shown in FIG. 7, the airflow 26 passing through the blades 3 of the propeller fan 1 flows so as to move to the outer peripheral side with a large moment and a large amount of work given to the airflow due to the influence of centrifugal force. For example, the airflow 26 that flows in at the most upstream point 18 of the leading edge of the blade 3 flows out from the outer peripheral portion 20a of the trailing edge. In the blower of the present embodiment, the trailing edge 16 side of the propeller fan 1 is retracted in the rotational direction 13 from the trailing edge reference point 19. For this reason, a path with a large moment can be passed through the airflow 26 for a long time. Even when the diameter is small, the work amount that is insufficient can be compensated. The trailing edge inner peripheral portion 20b is also moved backward from the trailing edge reference point 19 in the rotational direction 13 so as to keep the blade area.

  As described above, according to the blower of the present embodiment, in the propeller fan 1, the leading edge most upstream point 18 has an inner circumference that is larger than the outermost diameter of the blade in accordance with the air flow field where the suction airflow approaches the center side. Since it is located on the side, it is possible to make it easier to suck the flow that is biased toward the center of the fan. Further, since the blade 3 has a positional relationship such that the blade 3 has the outermost diameter on the upstream side with respect to the air flow in the direction of the fan rotation axis 9 than the wrap region 21 between the part of the propeller fan 1 and the bell mouth 7. The flow path between the propeller fan 1 and the bell mouth 7 is reduced only from the bell mouth 7 side, and the vortex 25 generated at the time of reduction can be suppressed, and the pressure fluctuation generated on the surface of the blade 3 or the bell mouth 7 can be reduced. Can be suppressed. Further, a portion of the trailing edge 16 of the blade 3 having a blade radius larger than the trailing edge reference point 19 is retracted with respect to the rotation direction so that the trailing edge 16 extends downstream, so that the blade radius of the leading edge 15 is The amount of work for the smaller and smaller area can be supplemented, and the amount of blown air can be secured. For this reason, it is not necessary to increase the rotational speed in order to obtain the required work. From the above, the number of rotations can be suppressed with respect to the blowing amount, and energy saving can be achieved. And the noise which generate | occur | produces from an air blower can be reduced, and the noise which generate | occur | produces from the outdoor unit 100 can be reduced.

Embodiment 2. FIG.
FIG. 8 is a view of the propeller fan 1 according to the second embodiment of the present invention as viewed from the front side. In FIG. 8, one blade 3 is shown enlarged. As for the radius of the blade 3, an arbitrary radius Ri2 between the radius Ri of the leading edge most upstream point 18 of the leading edge 15 and the blade outermost diameter Ro is defined, the section between Ri and Ri2, the radius Ri2 and the blade maximum A position on the front edge 15 serving as a boundary is defined as a front edge inflection point 15a. Here, when the blade tip is rounded in the vicinity of the blade outermost diameter Ro, it is determined that the position at the most retracted position with respect to the rotational direction 13 is the position of the blade outermost diameter Ro, and the blade outermost diameter starts. Point 27.

  In the present embodiment, attention is paid to the increase rate of the blade radius at the leading edge 15 (defined as the ratio (ratio) ΔR / Δθ of the radius change ΔR when the unit angle Δθ moves backward in the rotation direction 13). The shape of the blade 3 in the propeller fan 1 shown in FIG. 8 is such that the radius increase rate from Ri2 to the blade outermost diameter Ro (ΔR2) is larger than the radius increase rate from Ri to Ri2 (ΔR1 / Δθ1; ΔR = Ri2−Ri). / Δθ2; ΔR = Ro−Ri2) is small. Here, Δθ1 is an angle formed by the leading edge most upstream point 18, the rotation center 12, and the leading edge inflection point 15a. Δθ2 is an angle formed by the leading edge inflection point 15a, the rotation center 12, and the blade outermost diameter starting point 27.

  FIG. 9 is a view of the blower according to Embodiment 2 of the present invention as viewed from the side. FIG. 9 is a meridional view showing a three-dimensional blade surface as a two-dimensional cross section. As shown in FIG. 9, the reduction degree of the gap between the propeller fan 1 and the bell mouth with respect to the direction of the fan rotation shaft 9 is between the blade radius Ri2 and the blade outermost diameter Ro, rather than the section between the radii Ri and Ri2. It becomes gentle in the section.

  As described above, according to the blower of the second embodiment, as it progresses downstream from the blade radius Ri, the blade edge outer diameter Ro is increased in two stages with the leading edge inflection point 15a as a boundary. In the outer periphery where the propeller fan 1 and the bell mouth 7 approach, the air path can be reduced gradually, and the generation of vortices due to the sudden reduction can be further suppressed.

Embodiment 3 FIG.
FIG. 10 is a view of propeller fan 1 of a blower according to Embodiment 3 of the present invention as viewed from the front side. In FIG. 10, one blade 3 is shown enlarged. In the present embodiment, for the radius of the blade 3, an arbitrary radius Ri3 between the radius Ri of the leading edge most upstream point 18 of the leading edge 15 and the blade outermost diameter Ro is defined, and a section between Ri and Ri3 is defined. The position on the trailing edge 16 serving as a boundary is defined as a trailing edge inflection point 16a.

  In the present embodiment, attention is paid to the increase rate of the blade radius of the trailing edge 16 (defined as the ratio ΔR / Δθ of the radius change ΔR when the unit angle Δθ moves backward in the rotation direction). In the propeller fan 1 of the present embodiment, the radius increase rate (ΔR3 / Δθ3) from Ri to Ri3 is smaller than the radius increase rate (ΔR4 / Δθ4) from i2 to the blade outermost diameter Ro. This means that the area of the wing area of the trailing edge 16 that recedes in the rotational direction equal to or larger than the radius Ri is wide. Here, Δθ3 is an angle formed by the trailing edge reference point 19, the rotation center 12, and the trailing edge inflection point 16a. Δθ4 is an angle formed by the trailing edge inflection point 16a, the rotation center 12, and the trailing edge end point 16b.

  For example, the airflow that has flowed into the blade 3 flows on the blade surface toward the outer peripheral side by centrifugal force. If the wing shape as described above is used, the path through which the airflow passes to the outer peripheral side increases, so that the work amount that the airflow obtains from the propeller fan 1 increases.

Embodiment 4 FIG.
FIG. 11: is the figure which looked at the propeller fan 1 of the air blower concerning Embodiment 4 of this invention from the front side. In FIG. 11, the blade outermost diameter starting point 27 described above becomes the blade outermost diameter Ro on the outermost part 17 on the most upstream side with respect to the air flow in the rotation direction 13.

  FIG. 12 is a view of the propeller fan 1 according to Embodiment 4 of the present invention as viewed from the side. FIG. 12 shows a cross-sectional shape of the outer peripheral portion 28, which is a part of the outer peripheral portion 17 from the leading edge most upstream point 18 to the blade outermost diameter starting point 27, including the fan rotation shaft 9. In the blower of the present embodiment, the blade radius is between the radius Ri where the leading edge most upstream point 18 of the propeller fan 1 is located and the blade outermost diameter starting point 27 which is the blade outermost diameter Ro. An inclination inflection point 32 at which the angle of the inclination 31 in the direction of the fan rotation axis 9 changes is provided. The inclined inflection point 32 is a point in the cross-sectional shape viewed from the side surface side, but the wing 3 is linear because the inclined inflection point 32 is continuous.

  The airflow flowing in from the leading edge uppermost stream point 18 flows radially outward due to the influence of centrifugal force. Here, in the propeller fan 1, the portion on the upstream side with respect to the air flow in the rotation direction 13, which is the inflow side of air (airflow 10), has a small diameter, and thus the airflow at the blade tip tends to leak from the blade 3. For example, when the differential pressure between the downstream surface 29 (pressure surface 29) and the upstream surface (negative pressure surface 30) of the blade surface increases, the downstream side to the upstream side with respect to the air flow in the direction of the fan rotation shaft 9 This creates a strong vortex that winds around the blade and causes noise on the blade surface.

  Therefore, in the propeller fan 1 according to the present embodiment, the air flow in the direction of the fan rotation axis 9 at the boundary of the inflection point 32 between the outer radius 28 where the blade radius changes from Ri to the outermost blade diameter Ro. In contrast, from the downstream side toward the upstream side (from the pressure surface 29 toward the negative pressure surface 30), the blade 3 is formed in which the angle of the inclination 31 is changed from the inclination 31a to the inclination 31b. For this reason, although the backflow of the air flow 10 in the outer peripheral portion 28 is allowed, the pressure difference between the pressure surface 29 and the negative pressure surface 30 is alleviated so that a strong vortex is not generated even if a leakage flow occurs. it can.

  Therefore, in the blower of the fourth embodiment, turbulence caused by the vortex generated on the front edge 15 side and noise increase can be suppressed.

Embodiment 5 FIG.
FIG. 13 shows an outdoor unit 100 according to Embodiment 5 of the present invention. In the above-described embodiments, the outdoor unit that blows out air in the horizontal direction has been described. However, the present invention is not limited to this. For example, the present invention can also be applied to an outdoor unit that blows air upward (upward blowing), such as an outdoor unit of a large air conditioner for buildings. As shown in FIG. 15, the outdoor unit 100 according to the present embodiment is mounted such that the front surface of the propeller fan 1 is substantially upward in the vertical direction, and covers the side surface of the outdoor unit with the outdoor heat exchanger 4 and the outer panel 8. .

  FIG. 14 is a view showing a cross section of the outdoor unit 100 including the fan rotation shaft 9. The airflow 10 passes through the outdoor heat exchanger 4 and flows into the propeller fan 1. Since the air flow 10 passing through the outdoor heat exchanger 4 proceeds so as to minimize the ventilation resistance, the air flow immediately after passing through the outdoor heat exchanger 4 flows in from the fan rotation shaft 9 side. Since it is difficult for the airflow 10 to bend and flow to the outer peripheral side of the fan, the suction airflow of the propeller fan 1 also drifts in the center in the outdoor unit 100 of the present embodiment. For this reason, the effect similar to the effect mentioned above can be acquired by applying the propeller fan 1 of Embodiment 1-4 mentioned above to the outdoor unit of top blowing.

Embodiment 6 FIG.
FIG. 15 is a configuration diagram of an air-conditioning apparatus according to Embodiment 6 of the present invention. In the present embodiment, an air conditioner will be described as an example of a refrigeration cycle apparatus having the outdoor unit 100 described above. The air conditioner of FIG. 15 includes the outdoor unit 100 and the load unit (indoor unit) 200 described above, which are connected by a refrigerant pipe, constitute a refrigerant circuit, and circulate the refrigerant. Among the refrigerant pipes, a pipe through which a gaseous refrigerant (gas refrigerant) flows is referred to as a gas pipe 300, and a pipe through which a liquid refrigerant (liquid refrigerant, which may be a gas-liquid two-phase refrigerant) flows is referred to as a liquid pipe 400.

  The outdoor unit 100 is the outdoor unit described in the first to fifth embodiments, and each unit (means) of the compressor 5, the outdoor heat exchanger 4, the four-way valve 102, the outdoor fan 104, and the outdoor controller 105. ).

  As described above, the compressor 5 compresses and discharges the sucked refrigerant. Further, as described above, the outdoor heat exchanger 4 performs heat exchange between the refrigerant and air (outdoor air). Here, the outdoor heat exchanger 4 of the present embodiment functions as an evaporator, for example, during heating operation, performs heat exchange between the low-pressure refrigerant flowing from the liquid pipe 400 and the air, and evaporates the refrigerant. Vaporize. Further, during the cooling operation, it functions as a condenser and performs heat exchange between the refrigerant and air compressed in the compressor 5 flowing in from the four-way valve 102 side, thereby condensing and liquefying the refrigerant. The outdoor heat exchanger 4 is provided with the blower described in Embodiments 1 to 5 as the outdoor blower 104 in order to efficiently exchange heat between the refrigerant and the air. Here, for the outdoor blower 104, the rotational speed of the propeller fan 1 may be finely changed by arbitrarily changing the operating frequency of the fan motor by the inverter device.

  The four-way valve 102 switches the refrigerant flow between the cooling operation and the heating operation based on an instruction from the outdoor control device 105. Moreover, the outdoor side control apparatus 105 consists of a microcomputer etc., for example. It can be wired or wirelessly communicated with the load-side control device 204, for example, based on data relating to detection of various detection means (sensors) in the air conditioner, the operation frequency control of the compressor 5 by inverter circuit control, etc. The respective units related to the air conditioner are controlled to control the operation of the entire air conditioner.

  On the other hand, the load unit 200 includes a load side heat exchanger 201, a load side expansion device (expansion valve) 202, a load side blower 203, and a load side control device 204. The load side heat exchanger 201 performs heat exchange between the refrigerant and air. For example, it functions as a condenser during heating operation, performs heat exchange between the refrigerant flowing in from the gas pipe 300 and air, condenses and liquefies the refrigerant (or gas-liquid two-phase), and moves to the liquid pipe 400 side. Spill. On the other hand, during the cooling operation, it functions as an evaporator, performs heat exchange between the refrigerant and the air whose pressure is reduced by the load-side throttle device 202, causes the refrigerant to take heat of the air, evaporates it, and vaporizes it. It flows out to the piping 300 side. In addition, the load unit 200 is provided with a load-side blower 203 for adjusting the flow of air for heat exchange. The operating speed of the load-side fan 203 is determined by, for example, user settings. The load side expansion device 202 is provided to adjust the pressure of the refrigerant in the load side heat exchanger 201 by changing the opening degree.

  The load-side control device 204 is also composed of a microcomputer or the like, and can communicate with the outdoor-side control device 105 by wire or wireless, for example. Based on an instruction from the outdoor control device 105 and an instruction from a resident or the like, for example, each device (means) of the load unit 200 is controlled so that the room has a predetermined temperature. Further, a signal including data related to detection by the detection means provided in the load unit 200 is transmitted.

  As described above, in the air conditioner of the sixth embodiment, by using the blower described in the first to fifth embodiments as the outdoor blower 104 for the outdoor unit 100, energy saving of the outdoor unit 100 is achieved and noise is reduced. Can be suppressed.

  As an application example of the present invention, the present invention can be widely used for an outdoor unit constituting a refrigeration cycle apparatus, for example, an outdoor unit such as a water heater, and various other devices and facilities in which a blower is installed.

  1 propeller fan, 2 bosses, 3 blades, 4 outdoor heat exchanger, 5 compressor, 6 separator, 7 bell mouth, 8 outer panel, 9 fan rotation shaft, 10 air current, 11 corner, 12 rotation center, 13 rotation direction , 14 boss root, 15 leading edge, 15a leading edge inflection point, 16 trailing edge, 16a trailing edge inflection point, 16b trailing edge end point, 17 outer periphery, 18 leading edge most upstream point, 19 trailing edge reference point, 20a Trailing edge outer periphery, 20b Trailing edge inner periphery, 21 lap region, 22 wrap start point, 23 end point, 24 air flow, 25 vortex, 26 airflow, 27 blade outermost diameter start point, 28 outer periphery portion, 29 pressure surface, 30 Negative pressure surface, 31, 31a, 31b Inclination, 32 Inflection point, 100 Outdoor unit, 102 Four-way valve, 104 Outdoor fan, 105 Outdoor controller, 200 Load unit, 201 Load side Exchanger, 202 load-side throttle device, 203 a load-side fan, 204 load controller, 300 a gas pipe, 400 liquid pipe.

Claims (7)

A propeller fan having a plurality of blades that rotate around a fan rotation axis to generate a gas flow;
A wall surface is formed outside the outer peripheral edge of the blade along the rotation direction of the propeller fan so as to overlap a part of the blade as viewed from a direction perpendicular to the fan rotation axis direction, and the gas is rectified. With a bell mouth for
The most upstream point of the leading edge of the blade in the air flow with respect to the direction of rotation of the propeller fan is at a position where the blade radius is shorter than the outermost diameter of the blade that is the longest blade radius in the blade;
On the suction side, which is upstream with respect to the gas flow in the fan rotation axis direction, the edge of the blade is at the outermost position at a position further upstream than the point where the propeller fan and the bell mouth start to overlap. To be the diameter,
At the trailing edge of the blade, a portion having a blade radius longer than the trailing edge reference point corresponding to the blade radius of the most upstream point of the leading edge of the blade recedes with respect to the rotational direction from the trailing edge reference point. A blower characterized by being in a position to perform.   The portion of the trailing edge of the blade, which has a blade radius shorter than the trailing edge reference point, is located downstream of the trailing edge reference point in the air flow with respect to the rotational direction. Item 1. The blower according to item 1. A leading edge inflection point on the leading edge of the blade between the most upstream point of the leading edge of the blade and a point that becomes the outermost diameter of the blade;
The most upstream point and the leading edge inflection point of the leading edge of the blade with respect to the angle formed by the leading edge and the rotation center of the leading edge of the blade and the leading edge inflection point when viewed from the fan rotation axis direction The leading edge inflection point and the blade outermost diameter with respect to the angle formed by the leading edge inflection point, the rotation center and the blade outermost diameter point. The blower according to claim 1 or 2, wherein a rate of change in the blade radius is larger. A trailing edge inflection point on the trailing edge of the blade between the trailing edge reference point and the point that becomes the outermost diameter of the blade;
The fan rotation axis is larger than the ratio of the change in blade radius between the trailing edge inflection point and the trailing edge end point with respect to the angle formed by the trailing edge inflection point, the rotation center, and the trailing edge end point having the outermost diameter of the blade. When viewed from the direction, the ratio of the change in blade radius between the trailing edge reference point and the trailing edge inflection point with respect to the angle formed by the trailing edge reference point, the rotation center, and the trailing edge inflection point is more The blower according to any one of claims 1 to 3, wherein the blower is large. In a cross section in which the blade is cut by a plane including the fan rotation axis,
A tilt inflection point where the tilt angle changes from the downstream side to the upstream side with respect to the gas flow in the fan rotation axis direction, from the blade radius at the most upstream point of the leading edge of the blade to the outermost diameter of the blade. It has in between, The air blower as described in any one of Claims 1-4 characterized by the above-mentioned. A compressor for compressing the refrigerant;
An outdoor heat exchanger for exchanging heat between refrigerant and air;
An outdoor unit comprising the blower according to any one of claims 1 to 5 for allowing the air to pass through the outdoor heat exchanger. A load unit having a plurality of load-side heat exchangers for exchanging heat between the heat exchange object and the refrigerant, and a flow rate adjusting means for adjusting the flow rate of the refrigerant flowing into the load-side heat exchanger;
A refrigerating cycle device comprising a refrigerant circuit connected by piping to the outdoor unit according to claim 6.

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