JP6225332B2 - Blower and outdoor unit equipped with the blower - Google Patents

Description

  The present invention relates to an air blower, particularly one mounted on an outdoor unit of a refrigeration apparatus such as an air conditioner or a heat pump type water heater.

  In recent years, in refrigeration apparatuses such as air conditioners, energy saving is rapidly progressing as a countermeasure against global warming, and reduction of input of equipment is demanded. Moreover, in order to improve the heating comfort of the air conditioner, it is indispensable to improve the performance of the heat exchanger of the outdoor unit, reduce the noise of the blower mounted on the outdoor unit, and increase the air volume.

  Conventionally, axial blowers or mixed flow blowers have been used for outdoor unit blowers from the viewpoint of low noise and large air flow, but the blower performance of the blower while maintaining low noise as an outdoor unit. There is a demand for further improvement.

  As a technique for reducing the noise and increasing the air volume of such a blower, a static pressure recovery vane (static blade) that converts the dynamic pressure energy of the air flow into static pressure energy and recovers it downstream of the propeller fan (blower) ) (For example, see Patent Document 1).

  FIG. 10 shows a conventional outdoor unit described in Patent Document 1. In FIG. In FIG. 10, the outdoor unit 101 includes a propeller fan 105, a mouth ring 106 provided on the outer periphery of the propeller fan 105, and a static pressure collection vane 107 provided inside the mouth ring 106 on the discharge side of the propeller fan 105. ing.

  The mouth ring 106 is located on the rear edge side of the propeller fan 105 and guides the air flow blown out, and an enlarged air outlet 106A having a larger diameter than the front part is formed at the rear part of the mouth ring 106. . The static pressure recovery vane 107 is located downstream from the rear edge of the propeller fan 105. The chord length of the static pressure recovery vane 107 is formed so as to increase from the center toward the outer periphery.

  In the outdoor unit configured as described above, the static air flow collecting vane 107 collects the swirling flow that causes energy loss in the circumferential direction as a static pressure, thereby increasing the axial air flow rate. Further, since the swirl flow from the propeller fan 105 can be decelerated by the static pressure recovery vane 107, noise can be reduced.

JP 2000-130799 A

  However, in the rotary blade (blade) of a blower used in a conventional outdoor unit or the like, the mainstream concentrates on the outer peripheral side of the blade in the radial direction, so the swirl direction component is large but the axial component is also large. Also, the inflow speed from the wake of the moving blade will be large.

  For this reason, when the chord length of the static pressure recovery vane (static vane) 107 is increased from the central portion toward the outer circumference as in Patent Document 1, the blade surface friction loss and the loss due to the increase in the wake width of the wake are caused. Had the problem of increasing.

  In addition, the leakage flow between the rotating blades of the propeller fan (moving blade) 105 and the mouth ring (orifice) 106 and the influence of the tip vortex generated at the tip of the moving blade are affected by the downstream static pressure recovery vane (static Wings) reaches the leading edge of 107. This influence is particularly great from the center of the stationary blade to the outer peripheral edge. For this reason, if the chord length of the outer peripheral end of the static pressure recovery vane (static blade) 107 is large as in the above-mentioned Patent Document 1, the effect of hindering the flow is increased, and only the loss due to turbulence is increased. However, the swirl direction component cannot be recovered as static pressure.

  The present invention solves the above-mentioned conventional problems, and improves aerodynamic performance (low noise, large size) in an axial flow type or mixed flow type blower used for an outdoor unit of an air conditioner or a heat pump water heater. The purpose is to increase the air volume. Another object of the present invention is to realize power saving and noise reduction by an outdoor unit equipped with a blower.

  In order to solve the above-described conventional problems, the blower of the present invention includes a moving blade and a stationary blade, and the stationary blade of the stationary blade has a blade mounting angle on the outer peripheral side from the central portion in the radial direction of the stationary blade. The blade mounting angle on the fixed hub side is larger than the central portion.

  By adopting such a configuration, the collision loss at the inlet of the stationary blade of the stationary blade can be reduced on the outer peripheral side from the central portion of the stationary blade of the stationary blade, and the swirl direction component can be efficiently recovered to the static pressure.

  The aerodynamic performance of the blower of the present invention is improved. Moreover, the outdoor unit equipped with the blower of the present invention can realize power saving and noise reduction.

The meridional sectional view of the blower in Embodiment 1 of the present invention The front view seen from the discharge side of the air blower in the embodiment The figure which shows the relationship between the discharge airflow from a moving blade and the attachment angle of a stationary blade in the a) AA cross section of FIG. 1, b) BB cross section, and c) CC cross section. The figure which shows the relationship between the radial direction position of a fixed blade | wing and blade | wing attachment angle in the same embodiment The principal part perspective view of the connection part of the fixed blade | wing and support frame in the embodiment Cross-sectional view of an outdoor unit equipped with a blower in the same embodiment Vertical sectional view of another outdoor unit equipped with a blower in the same embodiment Meridian cross-sectional view of a blower in Embodiment 2 of the present invention The front view seen from the discharge side of the air blower in the embodiment Longitudinal sectional view of an outdoor unit of a conventional air conditioner

  According to a first aspect of the present invention, there is provided a moving blade having a rotating hub having a rotating shaft and a plurality of rotating blades provided around the rotating hub, an orifice provided on an outer peripheral side of the moving blade, and discharge of the moving blade. A stationary blade having a stationary hub and a plurality of stationary blades provided around the stationary hub, wherein the stationary blade is attached to a blade on an outer peripheral side from a central portion in the radial direction of the stationary blade. The blower is provided such that the corner is larger than the blade mounting angle on the fixed hub side from the radial central portion of the fixed blade.

By adopting such a configuration, the main flow of the air flow discharged from the moving blade is concentrated, and the swirl direction component becomes large. Collision loss can be kept small. For this reason, a turning direction component can be efficiently recovered to a static pressure.

  In a second aspect of the invention, in particular, in the first aspect of the invention, the blade mounting angle of the fixed blade is provided so as to be maximum between the central portion in the radial direction of the fixed blade and the outer peripheral end. .

  With this configuration, the blade mounting angle at the outer peripheral edge of the fixed blade is slightly smaller than the blade mounting angle from the center to the outer peripheral side, so the collision loss at the fixed blade inlet at the outer peripheral end of the fixed blade. Can be kept small. For this reason, the swirl direction component can be efficiently recovered to the static pressure from the center portion of the fixed blade to the outer peripheral side and further to the outer peripheral end.

  According to a third invention, in particular, in the first or second invention, the blade mounting angle at the outer peripheral end of the fixed blade is set to be smaller than the blade mounting angle at the radial center portion of the fixed blade. It is what was done.

  By setting it as this structure, the collision loss at the inlet of a fixed blade | wing can be restrained small by the outer peripheral end of a fixed blade | wing. For this reason, the swirl direction component can be efficiently recovered to the static pressure from the center to the outer periphery of the fixed blade, and the swirl can be efficiently swung even at the outer peripheral end affected by the leakage flow of the rotating blades of the rotor blade and the tip vortex. Directional components can be recovered to static pressure.

  In the fourth invention, in particular, the fixed blade of any one of the first to third inventions has a constant height on the meridian plane from the fixed hub side to the outer peripheral end.

  By adopting such a configuration, the chord length can be suppressed without extending from the fixed hub side to the outer peripheral side of the fixed blade, so that it is possible to suppress an increase in the surface friction loss of the fixed blade and an increase in loss due to an increase in the wake width of the wake. . In addition, since the chord length can be kept near the outer peripheral edge of the fixed blade without increasing the length, the rotor blade and orifice, which are easily affected when the chord length at the outer peripheral edge is long (when the meridian height is high), The influence of the leakage flow between the blades and the tip vortex generated at the tip of the rotor blade can be minimized. For this reason, it is possible to recover the swirl direction component of the air flow at the outer peripheral end of the fixed blade to a static pressure while suppressing an increase in loss due to turbulence.

  According to a fifth aspect of the invention, in particular, in the fixed blade of any one of the first to fourth aspects, the outer peripheral side is inclined in the counter-rotating direction of the moving blade with respect to the fixed hub side in a plane perpendicular to the rotating shaft. It is what.

  With this configuration, when the air flow discharged from the moving blade passes through the stationary blade of the stationary blade, it passes at a different timing for each radial position. The amount of noise generated can be reduced.

  6th invention is the outdoor unit which mounts the air blower of any one invention of 1st-5th invention especially. With this configuration, it is possible to reduce the input of the motor that drives the blower and the input to the entire outdoor unit. In addition, noise generated from the outdoor unit can be reduced.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. The present invention is not limited to the embodiments.
(Embodiment 1)
FIG. 1 is a meridional sectional view of a blower according to Embodiment 1 of the present invention. Here, the meridional sectional view is a sectional view obtained by rotationally projecting the rotating blade of the moving blade or the fixed blade of the stationary blade on a plane including the rotating shaft of the moving blade or the central axis of the stationary blade. Moreover, FIG. 2 is the front view seen from the discharge side of the air blower in the embodiment.

  As shown in FIGS. 1 and 2, the blower 1 includes a rotating hub 3 attached to a rotating shaft 2 and a moving blade 5 having two rotating blades 4 provided around the rotating hub 3. . A stationary blade 8 having a fixed hub 6 and 13 fixed blades 7 provided around the fixed hub 6 is provided on the discharge side (downstream side) of the moving blade 5. Further, at a position corresponding to the outer periphery on the discharge side of the moving blade 5 and the outer periphery on the suction side (upstream side) of the stationary blade 8, an orifice 9 is provided with a predetermined gap between the moving blade 5 and the stationary blade 8. ing.

  The rotating shaft 2 is provided on the suction side of the moving blade 5 and is connected to a driving shaft of a motor 10 that rotationally drives the moving blade 5. Since the motor 10 and the orifice 9 are both supported by a housing (not shown), the relative positions of the moving blade 5 and the orifice 9 are adjusted and held. Further, the fixed blade 7 is supported by the housing via the support frame 11, so that the relative positions of the stationary blade 8 and the orifice 9 are adjusted and held. The support frame 11 is a substantially annular member provided on the outer peripheral side of the stationary blade 8 and is formed integrally with the stationary blade 8.

  The rotating hub 3 of the moving blade 5 has a cylindrical shape or a truncated cone shape whose diameter increases toward the discharge side. The axial length of the rotating hub 3 is the meridian height at the center of the rotating blade 4 (the axial length when the rotating blade 4 of the moving blade 5 is rotationally projected onto a plane including the rotating shaft 2 of the moving blade 5. A) It is configured to be shorter than h1.

  The stationary hub 6 of the stationary blade 8 has a cylindrical shape, and the outer diameter thereof is the same as the diameter at the discharge-side end face of the rotating hub 3 (that is, the largest diameter of the rotating hub 3). The axial length of the fixed hub 6 is shorter than that of the rotating hub 3. The axial length of the fixed hub 6 is the meridian height of the fixed blade 7 (the axial length when the fixed blade 7 of the stationary blade 8 is rotationally projected onto a plane including the central axis of the stationary blade 8) h2. Is almost the same.

  The outer diameter of the stationary blade 8 is larger than the outer diameter of the moving blade 5, that is, the radial length of the fixed blade 7 is longer than the radial length of the rotating blade 4.

  The orifice 9 includes a minimum diameter portion 9x. In the minimum diameter portion 9x, the gap between the rotor blade 5 and the outer peripheral end of the rotary blade 4 is minimized. In FIG. 1, the minimum diameter portion 9x is formed of a cylindrical surface having a straight portion extending in the axial direction with a constant diameter. However, the minimum diameter portion 9x is configured as a constant diameter circumference without the straight portion. May be. The diameter of the orifice 9 increases from the minimum diameter portion 9x to the discharge side, and a discharge side opening 9y is formed at the end on the discharge side. In addition, the diameter of the orifice 9 increases from the minimum diameter portion 9x to the suction side, and a suction side opening 9z is formed at the end on the suction side.

  The position of the moving blade 5 in the axial direction is adjusted so that the outer peripheral end of the rear edge (discharge-side edge) of the rotary blade 4 faces the minimum diameter portion 9 x of the orifice 9. The moving blade 5 is positioned such that the discharge side end of the rotary hub 3 faces the minimum diameter portion 9x of the orifice 9, or between the minimum diameter portion 9x of the orifice 9 and the discharge side opening 9y. Thus, the position in the axial direction is adjusted.

The stationary blade 8 has its axial position adjusted so that the outer peripheral end of the front edge (suction side edge) of the fixed blade 7 is located between the minimum diameter portion 9x of the orifice 9 and the discharge side opening 9y. ing. Further, the stationary blade 8 is provided so as to form a predetermined gap S between the outer peripheral end on the front edge side of the fixed blade 7 and the orifice 9. Since the outer diameter of the stationary blade 8 is larger than the outer diameter of the moving blade 5 and the diameter of the orifice 9 increases toward the discharge side, the clearance S is formed at the outer peripheral end of the trailing edge of the rotating blade 4 of the moving blade 5. And the gap between the minimum diameter portion 9x of the orifice 9 and substantially the same. The stationary blade 8 is adjusted in the axial direction so that the suction side end of the fixed hub 6 is positioned between the minimum diameter portion 9x of the orifice 9 and the discharge side opening 9y.

  Here, the shape of the fixed blade 7 of the stationary blade 8 will be described in detail. As shown in FIG. 1, the height (meridional surface height) h2 of the fixed blade 7 on the meridian surface is configured to be substantially constant from the end (fixed hub side end) 7a on the fixed hub 6 side to the outer peripheral end 7b. Has been. Further, as shown in FIG. 2, the front edge of the fixed blade 7 on the surface perpendicular to the rotating shaft 2 of the moving blade 5 is such that the outer peripheral end 7b of the rotating blade 4 of the moving blade 5 with respect to the fixed hub side end 7a. Inclined so as to be positioned in the counter-rotating direction.

  3A is the same on the hub side (A-A cross section in FIG. 1), b) outer peripheral side (BB cross section in FIG. 1), and c) outer peripheral end (CC cross section in FIG. 1). It is a figure which shows the cross-sectional shape of the rotary blade 4 and the fixed blade 7 in the cross section in a radial position, and the relationship between the air flow discharged from the moving blade 5, and the blade attachment angle of the fixed blade 7. FIG. 4 is a diagram showing the relationship between the radial position of the fixed blade 7 and the blade mounting angle.

  As shown in FIG. 3, the rotary blade 4 has an arc shape or a wing-like cross section that is convex in the counter-rotating direction of the moving blade 5, and the rotary shaft 2 so that the trailing edge is located on the discharge side. The rotary hub 3 is fixed to the rotating hub 3 at an angle. The fixed blade 7 has an arc shape or a blade-shaped cross section that is convex in the rotation direction of the moving blade 5, and is a surface perpendicular to the central axis of the fixed hub 6 so that the leading edge is located on the suction side. Is fixed to the fixed hub 6 with a blade mounting angle θ that is inclined with respect to. Here, the blade attachment angle θ is an angle formed by a straight line connecting the front edge and the rear edge of the fixed blade 7 and a horizontal plane perpendicular to the central axis of the fixed hub 6, and a horizontal plane perpendicular to the central axis of the fixed hub 6. The angle increases from the suction side to the suction side or the counter-rotation direction side of the rotor blade 5.

  The blade attachment angle θ of the fixed blade 7 is configured to vary depending on the position of the fixed blade 7 in the radial direction.

  As shown in FIGS. 3 and 4, at the end where the fixed blade 7 and the fixed hub 6 are in contact (fixed hub side end 7a), the blade mounting angle θa is minimum. Then, the blade attachment angle θ increases as it goes to the outer peripheral side in the radial direction of the fixed blade 7, and becomes the blade attachment angle θm at the central portion 7 m of the fixed blade 7. As it goes further to the outer peripheral side than the central portion 7m, the blade attachment angle θ further increases, and becomes the maximum (blade attachment angle θb) between the central portion 7m and the outer peripheral end 7b of the fixed blade 7. Further on the outer peripheral side than the position where the blade attachment angle θb is reached, the blade attachment angle θ gradually decreases and becomes the blade attachment angle θc at the outer peripheral end 7 b of the fixed blade 7. The blade attachment angle θc is larger than the blade attachment angle θa at the fixed hub side end 7a and smaller than the blade attachment angle θm at the center portion 7m.

  That is, the blade attachment angle θbc on the outer peripheral side from the central portion 7m is larger than the blade attachment angle θab on the fixed hub 6 side from the central portion 7m. In addition, the blade attachment angle θb is maximized on the outer peripheral side from the central portion 7m.

  The meridional height of the fixed blade 7 is substantially constant regardless of the position in the radial direction, and the blade mounting angle θ of the fixed blade 7 varies depending on the position in the radial direction. The curvature of the arc is the smallest at the fixed hub side end 7a in contact with 6, and the curvature of the arc is maximized between the central portion 7m and the outer peripheral end 7b. Further, the curvature of the arc at the outer peripheral end 7b is larger than the curvature of the arc at the fixed hub side end 7a and smaller than the curvature of the arc at the center portion 7m. Further, the curvature of the arc on the outer peripheral side from the center portion 7m is larger than the curvature of the arc on the fixed hub 6 side from the center portion 7m.

Next, the shape of the connection portion between the stationary blade 7 of the stationary blade 8 and the support frame 11 will be described in detail. FIG. 5 is a perspective view of a main part of the connecting portion between the stationary blade 7 of the stationary blade 8 and the support frame 11 as viewed from the rear edge side of the stationary blade 7. As shown in FIG. 5, the outer peripheral end 7 b of the fixed blade 7 is provided with a plate-like extension 12 that extends the fixed blade 7 in the radial direction only on the rear edge side of the fixed blade 7. One surface of the extension portion 12 (the surface on the concave side of the fixed blade 7) is formed with the same curvature as the concave side of the arc of the fixed blade 7, while the back surface is parallel to the central axis of the fixed hub 6. It is formed with. For this reason, the thickness of the extension 12 is the same as the thickness of the fixed blade 7 on the rear edge side, but is formed so as to increase toward the front edge side. Further, the length (the meridional section height) of the extension 12 in the central axis direction is formed to be shorter than the length of the leg 13 described later in the central axis direction. Further, the height of the meridional section of the extension 12 is formed to be substantially constant regardless of the position in the radial direction.

  On the other hand, the support frame 11 is provided with leg portions 13 projecting toward the discharge side. The leg portion 13 is a plate-like member having both surfaces formed in parallel with the central axis of the fixed hub 6, and the thickness of the leg portion 13 is the same as the thickness of the fixed blade 7. Further, the length of the leg portion 13 in the central axis direction is formed to be shorter than the meridional surface height h2 of the fixed blade 7. Further, the leg portion 13 is provided so as to support the fixed blade 7 at a radial position on the outer peripheral side from the discharge side opening 9 y of the orifice 9.

  Then, by joining the outer peripheral side end of the extension part 12 and the fixed hub 6 side end part of the leg part 13, a predetermined gap T is formed between the front edge side of the fixed blade 7 and the support frame 11. , Supported by the support frame 11. In addition, it is desirable that the fixed blade 7, the extension portion 12, the leg portion 13, and the support frame 11 are integrally formed in order to ensure strength.

  Further, as shown in FIG. 5, the outlet side end portion 13 e of the leg portion 13 is joined so as to be located on the same plane as the outlet side end portion 12 e of the extension portion 12 and the rear edge 7 e of the fixed blade 7. . For this reason, the front edge of the fixed blade 7 protrudes from the support frame 11 toward the suction side. Further, the rear edge of the fixed blade 7 protrudes from the support frame 11 to the discharge side.

  As shown in FIG. 2, the length at which the extension 12 connects the fixed blade 7 and the support frame 11 (the length in the radial direction of the extension 12) varies depending on the position where the fixed blade 7 is attached. The extension 12 of the fixed blade 7 located on the top, bottom, left and right in the direction of gravity is short, and the extension of the other fixed blade 7 is long. According to this, it becomes easy to ensure sufficient strength to hold the stationary blade 8 on the support frame 11.

  About the air blower comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

  First, when the rotating shaft 2 is rotationally driven by the motor 10, the moving blade 5 rotates counterclockwise as shown in FIG. 2, and air is guided to the moving blade 5 from the side where the motor 10 is disposed. At that time, dynamic pressure and static pressure are applied to the air by the plurality of rotating blades 4 and the orifices 9 provided around the rotating blades 4.

  Then, the air (discharged airflow) discharged from the moving blade 5 is guided to the stationary blade 8. As shown in FIG. 3, the inflow velocity V of air guided to the stationary blade 8 has an angle with respect to the axial direction of the rotating shaft 2, and the axial flow direction component Va flowing in the axial direction and the moving blade 5 And a turning direction component Vt flowing in the rotation direction. The axial flow direction component Va is a speed related to the air volume, but the swirl direction component Vt is perpendicular to the axial direction, that is, a circumferential direction component, and thus is not related to the air volume, but merely stirs the air. If it is not smoothly turned in the axial direction, the energy is lost.

  Therefore, by using the stationary blade 8 having a plurality of fixed blades 7, the swirl direction component of the discharge airflow of the moving blade 5 is reduced, and the swirl direction component (swirling flow) that causes energy loss is recovered as a static pressure. The air blowing action is achieved while improving the efficiency.

  Here, the blade mounting angle of the fixed blade 7 is set to the blade mounting angle θa on the fixed hub 6 side from the central portion 7m in accordance with the discharge airflow of the moving blade 5 where the main flow is concentrated on the outer peripheral side from the central portion of the rotating blade 4. In comparison, the blade attachment angle θb on the outer peripheral side from the central portion 7m is increased. For this reason, the collision loss at the inlet of the fixed blade 7 is smaller in the region on the outer peripheral side than the central portion 7m where the swirl direction component at the inlet of the stationary blade 8 is larger than the region on the fixed hub 6 side from the central portion 7m. In this way, the turning speed component can be efficiently recovered to static pressure.

  Further, when the moving blade 5 is an axial flow type or a mixed flow type and only the discharge side of the rotating blade 4 of the moving blade 5 is surrounded by the orifice 9, a large blade tip vortex is formed on the outer periphery of the rotating blade 4. Occurs, and the discharge air velocity on the outer peripheral side of the rotor blade 5 is greatly reduced. In particular, when a leakage flow that is influenced by the blade tip vortex and flows backward from the gap between the orifice 9 and the rotary blade 4 to the suction side occurs, the axial component of the discharge airflow is greatly reduced. However, in the present embodiment, the blade mounting angle is maximized between the central portion 7m and the outer peripheral end 7b, and the blade mounting angle θc at the outer peripheral end 7b of the fixed blade 7 is adjusted to the central portion accordingly. Since it is made smaller than the blade attachment angle θm at 7 m, the collision loss at the inlet of the fixed blade 7 at the outer peripheral end 7 b of the fixed blade 7 of the stationary blade 8 can be suppressed small.

  For this reason, while being able to collect | recover efficiently a turning speed component to a static pressure from the center part 7m of the fixed blade | wing 7 to an outer peripheral side, the fixed blade | wing 7 which is easy to receive to the influence of the leakage flow of the rotating blade 4 of a moving blade 5, or a blade tip vortex. Even at the outer peripheral end 7b, the turning speed component can be efficiently recovered to static pressure.

  In the region from the fixed hub side end 7a of the fixed blade 7 to the portion where the blade mounting angle θ on the outer peripheral side is the maximum, the blade mounting angle θ of the fixed blade 7, particularly the inlet angle, matches the discharge air flow angle of the moving blade 5. Therefore, the swirl velocity component of the airflow discharged from the moving blade 5 can be efficiently converted to a static pressure without increasing the meridional height h2 of the fixed blade 7 and increasing the chord length.

  Further, the chord length can be suppressed without increasing toward the outer peripheral side of the fixed blade 7, and an increase in loss due to an increase in the surface friction loss of the fixed blade 7 and the wake width of the wake can be suppressed.

  Further, if the blade mounting angle at the outer peripheral end 7b of the fixed blade 7 is smaller than the blade mounting angle in the region on the outer peripheral side from the central portion 7m, the leakage flow between the moving blade 5 and the orifice 9 or the moving blade 5 Due to the tip vortex generated at the tip of the blade, the angle of the discharge airflow from the outer peripheral end of the moving blade 5 is likely to be greatly affected. However, in the present embodiment, the meridional height h2 of the fixed blade 7 is provided so as to be substantially constant from the fixed hub side end 7a to the outer peripheral end 7b, so that the vicinity of the outer peripheral end 7b of the fixed blade 7 However, it can be suppressed without increasing the meridian height. For this reason, when the chord length of the outer peripheral end 7b of the stationary blade 7 of the stationary blade 8 is large, the fluctuation of the flow that is greatly affected is suppressed as much as possible, and the loss due to the turbulence is suppressed. The swirl velocity component of the discharged airflow can be efficiently recovered to static pressure.

  Further, the fixed blade 7 is provided on the plane perpendicular to the rotating shaft 2 of the moving blade 5 such that the outer peripheral side is inclined in the counter-rotating direction of the moving blade 5 with respect to the hub side. Since the discharge airflow passes at different timings depending on the radial position of the fixed blade 7, the noise generated when the discharge airflow passes through the fixed blade 7 can be shifted and generated when it passes through the stationary blade 8. The amount of noise can be reduced.

In addition, a predetermined gap between the outer peripheral end of the rotating blade 4 of the moving blade 5 and the orifice 9 expands from the minimum diameter portion 9x toward the discharge side opening 9y, and in front of the fixed blade 7 of the stationary blade 8. The axial position of the outer peripheral edge of the edge is provided so as to be positioned between the minimum diameter portion 9x of the orifice 9 and the discharge side opening 9y, so that the swirl in the region from the outer peripheral side of the moving blade 5 to the outer peripheral end is performed. A discharge airflow having a large directional component can be introduced between the blades of the fixed blade 7 before shifting to a flow that expands in the radial direction toward the discharge-side opening 9y (a flow having a radial component). For this reason, a discharge air current with a large swirl direction component can be forcibly converted into an axial direction component, and can be efficiently recovered as a static pressure.

  Further, if all the strong swirl direction component flows in the vicinity of the outer peripheral edge 7b of the stationary blade 7 of the stationary blade 8 are forced to be converted into the axial component, the flow and static flow on the rear edge near the outer peripheral end 7b of the fixed blade 7 are static. A contracted flow is generated between the blade 8 and the flow from the outer peripheral side, and a flow that is not converted into static pressure is generated on the rear edge side in the vicinity of the outer peripheral end 7 b of the fixed blade 7. However, in the present embodiment, a predetermined gap S is provided between the outer peripheral end of the stationary blade 7 on the front edge side of the stationary blade 7 and the orifice 9, so that the pressure surface side of the front edge is intended to be on the suction surface side. Therefore, a slight leakage flow can be generated. This makes it difficult for contraction to occur on the rear edge side of the outer peripheral end 7b, and it can be efficiently recovered as static pressure. Further, the slight leakage flow from the pressure surface side to the negative pressure side in the gap S can be smoothly decelerated along the expanding discharge side opening 9y on the discharge side of the orifice 9, so that the flow loss increases. There is nothing.

  Further, a turbulent tip vortex generated in the vicinity of the outer peripheral end of the rotary blade 4 flows downstream, and a disturbance occurs when it collides with the extension portion 12 from the outer peripheral side of the fixed blade 7. However, in the present embodiment, the stationary blade 8 is fixed to the support frame 11 by the extension portion 12 in which only the rear edge side of the outer peripheral end 7b of the fixed blade 7 is extended, and the front edge side of the fixed blade 7 is the support frame. 11 is not fixed. That is, the extension portion 12 is positioned on the rear edge side of the fixed blade 7. For this reason, the turbulence of the airflow in the extension part 12 can be reduced on the front edge side of the fixed blade 7.

  Further, similarly to the operation of the fixed blade 7 with the orifice 9 described above, since the predetermined gap T is provided between the outer peripheral end of the fixed blade 7 of the stationary blade 8 on the front edge side and the support frame 11, the front edge A slight leakage flow can be intentionally generated from the pressure surface side to the suction surface side. This makes it difficult for contraction to occur on the rear edge side of the outer peripheral end 7b, and it can be efficiently recovered as static pressure. Further, the slight leakage flow from the pressure surface side to the negative pressure side in the gap T can be smoothly decelerated along the expanding discharge side opening 9y on the discharge side of the orifice 9, so that the flow loss increases. There is nothing.

  Further, since one surface of the extension portion 12 is formed with the same curvature as the concave portion of the arc of the fixed blade 7, the static pressure can be efficiently recovered without disturbing the flow on the rear edge side of the fixed blade 7 as much as possible.

  As described above, in the present embodiment, the loss of flow caused by supporting the stationary blade 8 on the casing that holds the orifice 9 can be reduced, so that the efficiency of static pressure recovery in the stationary blade 8 can be reduced as much as possible. Can be suppressed.

  Further, the thickness of the extension portion 12 is the same as the thickness of the fixed blade 7 on the rear edge side, and becomes thicker toward the front edge side, so that the air flow direction greatly varies on the front edge side of the extension portion 12. It is possible to suppress the flow loss due to peeling that can be performed on the downstream side of the extension portion 12 and to secure the strength necessary for holding the fixed blade 7.

  Further, since the fixed blade 7 is supported at a radial position on the outer peripheral side of the discharge side opening 9 y of the orifice 9, the fixed blade 7 is outside the airflow flowing along the leg 13 along the discharge side opening 9 y of the orifice 9. The resistance on the discharge side of the orifice 9 can be reduced.

  Further, since the fixed blade 7 is supported so that the rear end of the fixed blade 7 protrudes to the blow-out side from the support frame 11, the airflow flowing through the leg portion 13 along the discharge side opening 9 y of the orifice 9 is supported. The resistance on the discharge side of the orifice 9 can be reduced.

  Hereinafter, the outdoor unit on which the blower is mounted will be described. FIG. 6 is a cross-sectional view of an outdoor unit equipped with the blower of the present embodiment.

  As shown in FIG. 6, the outdoor unit includes a compressor 22, an outdoor heat exchanger 23, and the like in a casing 21 that forms an outer shell. The motor 10 is fixed to the housing 21 via a motor fixing tool 24 on a pillar fixed to the bottom of the housing 21, so that the blower 1 has the discharge side opening 9 y of the orifice 9 in the housing 21. It is being fixed to the housing | casing 21 so that it may correspond to the front part 21a. Further, the support frame 11 is fixed to the front portion 21 a of the casing 21, so that the blower 1 is fixed to the casing 21.

  Further, a blowing grill 25 is provided on the front portion 21a of the casing 21 so as to cover the stationary blade 8 protruding from the front portion 21a to the front surface (discharge side). The blow-out grill 25 is supported at a position on the outer peripheral side further than the support frame 11.

  Such an outdoor unit constitutes a refrigeration cycle by being connected to an indoor unit of an air conditioner including an indoor heat exchanger or a unit of a heat pump type hot water heater. Then, the air around the outdoor unit is blown to the outdoor heat exchanger 23 by the blower 1, so that heat exchange is performed with the refrigerant flowing in the heat transfer pipe of the outdoor heat exchanger 23 by the operation of the compressor 22.

  In the outdoor unit configured as described above, the stationary blade 7 and the blowout grill 25 of the stationary blade 8 are not directly fixed, but are fixed to the casing 21. Even if an external force is applied to the blowing grill 25 due to a certain pressure, the external force is absorbed to some extent by the deformation of the front portion 21a of the casing 21, so that the stationary blade 8 is deformed or the stationary blade 8 is fixed. The positional relationship between the blade 7 and the orifice 9 does not shift. For this reason, it is not necessary to increase the strength of the blowing grill 25, and the outdoor unit can be configured at low cost.

  Moreover, since the stationary blade 7 and the blowing grill 25 of the stationary blade 8 can be configured separately, the molding accuracy when the stationary blade 7 is molded can be improved, and the static pressure can be efficiently recovered at a low cost. A possible stationary blade 8 can be manufactured. For example, when the fixed blade 7 and the blowing grill 25 are integrally formed, it is necessary to provide a fin for eliminating the undercut at a position where the fixed blade 7 and the blowing grill 25 intersect.

  Here, undercut refers to a shape that cannot be released only in the direction of opening the mold when the molded product is taken out (released) from the mold in the molding process. If it is not provided, it cannot be manufactured with a mold that opens only in the vertical direction, and it is necessary to provide a slide core (side core) that slides in the horizontal direction, which increases the cost of the mold and increases the manufacturing cost.

  However, in the present embodiment, it is not necessary to provide a fin for eliminating such an undercut. Therefore, by providing a fin on the fixed blade 7, performance degradation when the stationary blade 8 collects static pressure is suppressed. Can do.

  The outdoor unit on which the blower of the present embodiment is mounted may not be a front blowing type outdoor unit as shown in FIG. 6, but may be a top blowing type outdoor unit. FIG. 7 is a vertical cross-sectional view of an outdoor unit of a top blowing type equipped with a blower in the present embodiment.

The outdoor unit in FIG. 7 is different from the outdoor unit described in FIG. 6 only in that the direction in which the blower 1 blows out air is the direction in which the blower 1 blows out from the upper surface portion 21b of the casing 21. Since it becomes the structure and effect | action similar to the case of the demonstrated front blowing type | formula, description is omitted.
(Embodiment 2)
FIG. 8 is a meridional sectional view of another blower according to Embodiment 1 of the present invention. FIG. 9 is a front view seen from the discharge side of another blower in the same embodiment. In the present embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.

  Only the differences between the present embodiment and the first embodiment will be described below.

  As shown in FIG. 8, in the present embodiment, the front edge side of the extension portion 12 is substantially parallel to the front surface portion 21 a, while the rear edge side is closer to the front surface portion 21 a side toward the outer peripheral side of the fixed blade 7. Inclined to approach. For this reason, the meridional section height of the extension portion 12 is formed so as to become shorter toward the outer peripheral side of the fixed blade 7.

  The tip vortex generated in the vicinity of the outer peripheral end of the rotary blade 4 flows downstream and is disturbed when it collides with the extension 12 from the outer periphery of the fixed blade 7. In this embodiment, the meridional section of the extension 12 is used. By lowering the height toward the outer peripheral side, the turbulence of the flow in the extension portion 12 can be kept small, and the flow resistance can be reduced.

  Moreover, as shown in FIG. 9, in this Embodiment, the extension part 12 is provided only in the one part fixed blade among the some fixed blades 17. As shown in FIG. The total number of fixed blades 17 is 13, while the number of fixed blades 17 provided with the extension 12 is five. In the upper part of the gravity direction, two fixed blades 17b not provided with the extension 12 are arranged next to the fixed blade 17a provided with the extension 12, and in the lower part of the fixed blade 17a provided with the extension 12. Next, one fixed blade 17b not provided with the extension 12 is disposed. That is, the number of fixed blades 17b provided between the fixed blades 17a provided with the extended portions 12 and not provided with the extended portions 12 is smaller in the lower portion than in the upper portion of the housing 21.

  With this configuration, the loss of the flow due to the provision of the extension 12 is not a part of the fixed blade 17 but a part of the fixed blade 17, so that the efficiency improvement in the stationary blade 18 is not hindered.

  Furthermore, sufficient strength for holding the stationary blade 18 on the support frame 11 can be ensured by placing the fixed blade 17b provided with the extension 12 in a lower part in the gravitational direction.

  As described above, the blower of the present embodiment can achieve both improved aerodynamic performance and higher efficiency. Moreover, the outdoor unit equipped with the blower of the present embodiment can realize power saving and noise reduction.

  As described above, since the blower having the configuration according to the present invention can achieve both improvement in aerodynamic performance and high efficiency, air conditioning equipment for home and commercial use air conditioners, home refrigerator refrigerators and vending machines. It can be applied not only to refrigeration equipment such as refrigeration equipment, heat pump equipment such as water heaters, and electronic equipment having thermoelectric components, but also to AV equipment and waste heat recovery equipment.

DESCRIPTION OF SYMBOLS 1 Blower 2 Rotating shaft 3 Rotating hub 4 Rotating blade 5 Rotor blade 6 Fixed hub 7, 17 Fixed blade 7a Fixed blade side end 7b Outer peripheral end 7m Central portion 8, 18 Stator blade 9 Orifice 9x Minimum diameter portion 9y Discharge side opening 9z Suction side opening 10 Motor 11 Support frame 12 Extension part 13 Leg part 21 Case 21a Front part 22 Compressor 23 Outdoor heat exchanger 24 Motor fixture 25 Blowing grill

Claims (5)

A moving blade having a rotating hub having a rotating shaft and a plurality of rotating blades provided around the rotating hub, an orifice provided on the outer peripheral side of the moving blade, and a discharge side of the moving blade, fixed A stationary blade having a hub and a plurality of fixed blades provided around the fixed hub, wherein the fixed blade has a blade mounting angle on an outer peripheral side from a central portion in a radial direction of the fixed blade. from the blade mounting angle of the fixed hub side from the central portion in the radial direction of the large Ri Na, besides the fixed vanes, the height of the meridian plane until the outer peripheral edge was characterized by constant der Rukoto from the fixed hub side Blower. The blower according to claim 1, wherein a blade mounting angle of the fixed blade is maximized between a central portion in the radial direction of the fixed blade and an outer peripheral end. The blower according to claim 1 or 2, wherein a blade attachment angle at an outer peripheral end of the fixed blade is provided so as to be smaller than a blade attachment angle at a central portion in a radial direction of the fixed blade. The fixed blade in the rotary shaft and the plane perpendicular to any one of claims 1 to 3 characterized in that the outer peripheral side is inclined in the counter rotational direction of the rotor blade relative to the fixed hub side The blower described. The outdoor unit which mounts the air blower of any one of Claim 1 to 4 .