CN210686426U

CN210686426U - Axial flow wind wheel and air conditioner with same

Info

Publication number: CN210686426U
Application number: CN201921667055.2U
Authority: CN
Inventors: 游斌; 张敏
Original assignee: Midea Group Co Ltd; GD Midea Air Conditioning Equipment Co Ltd
Current assignee: Midea Group Co Ltd; GD Midea Air Conditioning Equipment Co Ltd
Priority date: 2019-09-30
Filing date: 2019-09-30
Publication date: 2020-06-05
Anticipated expiration: 2029-09-30

Abstract

The utility model discloses an axial flow wind wheel and have its air conditioner. The radius of a hub of the axial flow wind wheel is R1, the maximum outer radius of the axial flow wind wheel is R2, the radial blade height of each blade is Rm, and Rm is R2-R1; taking the axis of the wind wheel as the center, respectively taking R1+ 90% Rm, R1+ 5% Rm, R1+ 50% Rm, R1+ 70% Rm and R1+ 30% Rm as the radiuses to make a first circle to a fifth circle, wherein the intersection points of the five circles and the leading edge of the blade are respectively a point A1, a point A3, a point A5, a point A7 and a point A9. The connecting line of the point a1 and the point A3 is a first connecting line, the distances from the point a5, the point a7 and the point a9 to the first connecting line are h1, h2 and h3 respectively, h1 is greater than h2, h1 is greater than h3, h1 is (0.09-0.13) R2, h2 is (0.06-0.10) R2, and h3 is (0.06-0.10) R2. According to the utility model discloses an axial flow wind wheel can improve axial flow wind wheel's the amount of wind.

Description

Axial flow wind wheel and air conditioner with same

Technical Field

The utility model belongs to the technical field of the wind wheel and specifically relates to an axial flow wind wheel and have its air conditioner is related to.

Background

At present, aiming at increasingly strict requirements on energy conservation and emission reduction, the aim of further improving the energy efficiency of the air conditioner is to improve the heat exchange efficiency of the air conditioner, namely how to improve the air volume of the air conditioner on the premise of not increasing the noise so as to aim at reducing the power of a compressor and improving the heat dissipation capacity of the air conditioner.

SUMMERY OF THE UTILITY MODEL

The utility model discloses aim at solving one of the technical problem that exists among the prior art at least. Therefore, the utility model provides an axial flow wind wheel to improve axial flow wind wheel's the amount of wind.

The utility model discloses still aim at providing an air conditioner that has above-mentioned axial compressor wind wheel to improve the amount of wind of air conditioner.

According to the utility model discloses axial-flow wind wheel, including wheel hub and a plurality of blade, a plurality of blade intervals are established on the wheel hub, every blade includes leading edge, trailing edge, blade top, pressure surface and suction surface, the leading edge of blade is swept forward to the upstream direction of intaking and is the arc form; the radius of the hub is R1, the maximum outer radius of the axial flow wind wheel is R2, the radial blade height of each blade is Rm, and Rm is R2-R1; taking the rotation central axis of the axial flow wind wheel as a center, taking R1+ 90% Rm as a radius to make a first circle, wherein the intersection point of the first circle and the leading edge is a first intersection point A1, and the intersection point of the first circle and the trailing edge is a second intersection point A2; taking R1+ 5% Rm as a radius to form a second circle, wherein the intersection point of the second circle and the leading edge is a third intersection point A3, and the intersection point of the second circle and the trailing edge is a fourth intersection point A4; a third circle is formed by taking R1+ 50% Rm as a radius, the intersection point of the third circle and the leading edge is a fifth intersection point A5, and the intersection point of the third circle and the trailing edge is a sixth intersection point A6; making a fourth circle by taking R1+ 70% Rm as a radius, wherein the intersection point of the fourth circle and the leading edge is a seventh intersection point A7, and the intersection point of the fourth circle and the trailing edge is an eighth intersection point A8; making a fifth circle with R1+ 30% Rm as a radius, wherein the intersection point of the fifth circle and the leading edge is a ninth intersection point A9, and the intersection point of the fifth circle and the trailing edge is a tenth intersection point A10; a connection line between the first intersection point a1 and the third intersection point A3 is a first connection line L1, a distance from the fifth intersection point a5 to the first connection line L1 is h1, a distance from the seventh intersection point a7 to the first connection line L1 is h2, a distance from the ninth intersection point a9 to the first connection line L1 is h3, wherein h1> h2, h1> h3, h1 ═ R2, (0.09-0.13) R2, h2 ═ 539 (0.06-0.10) R2, and h3 ═ R2 (0.06-0.10).

According to the utility model discloses axial flow wind wheel is through the shape of injecing the leading edge for the leading edge is circular-arc sweepforward direction of air admission, thereby the blade can form C shape static pressure distribution at apex surface area, can reduce the response of blade to import flow field distortion, and the noise reduction reduces the swirl loss, makes the blade have great flow margin, and then improves axial flow wind wheel's the amount of wind.

In some embodiments, at least a portion of the trailing edge of the blade projects in an air flow direction toward a downstream air exit direction.

Specifically, a connection line between the second intersection point a2 and the fourth intersection point a4 is a second connection line L2, a distance from the sixth intersection point a6 to the second connection line L2 is W1, a distance from the tenth intersection point a10 to the second connection line L2 is W2, and a distance from the eighth intersection point A8 to the second connection line L2 is W3, where W1> W2> W3 includes W1 (0.08-0.12) R2, W2 (0.06-0.09) R2, and W3 (0.03-0.06) R2.

In some embodiments, a connection line between the first intersection point a1 and the rotation center o of the axial flow wind wheel is a third connection line L3, a connection line between the second intersection point a2 and the rotation center o is a fourth connection line L4, an included angle between the third connection line L3 and the fourth connection line L4 is defined as a first included angle Ω 1, and the range of Ω 1 is 85 ° to 105 °; a connecting line between the third intersection point A3 and the rotation center o is a fifth connecting line L5, a connecting line between the fourth intersection point a4 and the rotation center o is a sixth connecting line L6, an included angle between the fifth connecting line L5 and the sixth connecting line L6 is defined as a second included angle Ω 2, the range of Ω 2 is 70-90 °, and Ω 1 is greater than Ω 2.

In some embodiments, the orthographic area of each blade in the horizontal plane is S1, and the annular area between the hub and the maximum outer diameter of the blade is S2, wherein S1/S2 is 0.23-0.26.

In some embodiments, the tip curves from the pressure face to the suction face.

Specifically, the height at which the tip curves from the pressure surface to the suction surface is T, where T ═ 0.02 to 0.04) R2.

In some embodiments, an arc line between the first intersection point a1 and the second intersection point a2 is defined as a seventh connecting line L7, a plane passing through the rotation center o of the axial-flow wind wheel and the seventh connecting line L7 is a longitudinal plane, the longitudinal plane is a longitudinal section of a cross section of the blade, in a direction from the blade tip to the rotation center o, a boundary line of the longitudinal section on the suction surface includes a first section of curve q1, a second section of curve q2 and a third section of curve q3 which are sequentially connected, the first section of curve q1 extends from top to bottom toward the rotation center, the second section of curve q2 extends from bottom to top toward the rotation center, and the third section of curve q3 extends from top to bottom toward the rotation center; in the direction from the blade tip to the rotation center o, the boundary line of the longitudinal section on the pressure surface includes a fourth section of curve q4, a fifth section of curve q5 and a sixth section of curve q6 which are connected in sequence, the fourth section of curve q4 extends from top to bottom toward the rotation center, the fifth section of curve q5 extends from bottom to top toward the rotation center, and the sixth section of curve q6 extends from top to bottom toward the rotation center.

Specifically, the lowest point where the first section of curve q1 and the second section of curve q2 intersect is a point K, and the radial distance between the point K and the rotation center o is Rk, where Rk is R1+ (0.85-0.95) Rm.

Further, three of the longitudinal sections are respectively f1, f2 and f3, and pass through quartering points a11, a12 and a13 on the seventh connecting line L7, and in the direction from the front edge to the tail edge; the highest point of the intersection of the fifth section of curve q5 and the sixth section of curve q6 is a point G, the vertical distance between the point G and the point K is V, the V value of the longitudinal section f1 is V1, the V value of the longitudinal section f2 is V2, and the V value of the longitudinal section f3 is V3, wherein V1< V2< V3.

According to the utility model discloses the air conditioner, include the above-mentioned embodiment of the utility model axial flow wind wheel.

According to the utility model discloses air conditioner, shape through the leading edge of injecing axial flow wind wheel for the leading edge is circular-arc sweepforward direction of air inlet sweepforward, can reduce the swirl loss, makes the blade have great flow margin, thereby can promote the amount of wind of air conditioner, reduces compressor power, reduces the noise of air conditioner, improves the heat dissipation capacity of air conditioner.

Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.

Drawings

The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:

fig. 1 is a perspective view of an axial flow wind wheel according to an embodiment of the present invention (in which a blade tip and a suction surface face upward);

fig. 2 is a perspective view of the axial flow wind wheel in another view angle according to the embodiment of the present invention (in which the blade tip and the suction surface face upward);

fig. 3 is a perspective view of an axial flow wind wheel according to an embodiment of the present invention (in which the blade tip is downward and the pressure surface is upward);

fig. 4 is a schematic view showing a projection of a partial structure of an axial flow wind wheel in the embodiment of the present invention on a horizontal plane (in which a suction surface faces upward);

fig. 5 is a schematic view of the axial flow wind wheel in the embodiment of the present invention projected on a horizontal plane (in which the pressure surface faces upward);

fig. 6 is a schematic view of the axial flow wind wheel in the embodiment of the present invention projected on a horizontal plane (in which the suction surface faces upward);

fig. 7 is a schematic view of the axial flow wind wheel in the embodiment of the present invention projecting on a vertical plane;

fig. 8 is a schematic view of a projection of a partial structure of an axial flow wind wheel in the embodiment of the present invention on a horizontal plane (in which a trailing edge protrudes toward a downstream air outlet direction);

fig. 9 is a schematic view of a projection of a partial structure of an axial flow wind wheel in an embodiment of the present invention on a horizontal plane (where a first included angle of a blade is greater than a second included angle);

FIG. 10 is a schematic view showing a projection of a partial structure of an axial flow wind wheel in an embodiment of the present invention on a horizontal plane (wherein, a shaded portion is an annular area between a hub and a maximum outer diameter of a blade)

Fig. 11 is a schematic view of a longitudinal section of an axial flow wind wheel in an embodiment of the present invention;

fig. 12 is a schematic view showing a projection of a partial structure of an axial flow wind wheel in the embodiment of the present invention on a horizontal plane (where, a11, a12, a13 are quartering points on a seventh connecting line L7);

FIG. 13 is a schematic illustration of three longitudinal sections of the axial flow wind rotor shown in FIG. 12 taken along f1, f2, f 3;

reference numerals:

an axial flow wind wheel 100,

The blade comprises a hub 1, a front edge 2, a tail edge 3, a blade top 4, a pressure surface 5 and a suction surface 6.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are exemplary only for the purpose of explaining the present invention, and should not be construed as limiting the present invention.

In the description of the present invention, it is to be understood that the terms "upper", "lower", "inner", "outer", "radial", "circumferential", "central", "longitudinal", "transverse", "vertical", "horizontal", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience in describing the present invention and simplifying the description, but do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore should not be construed as limiting the present invention. Furthermore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.

In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood in specific cases to those skilled in the art.

An axial flow wind wheel 100 according to an embodiment of the present invention is described below with reference to fig. 1 to 13.

According to the utility model discloses axial-flow wind wheel 100, as shown in fig. 1-3, including wheel hub 1 and a plurality of blade, a plurality of blade intervals are established on wheel hub 1, and every blade includes leading edge 2, trailing edge 3, blade top 4, pressure side 5 and suction surface 6, and leading edge 2 of blade is swept forward upstream air intake direction and is the arc line shape. It should be noted here that, when the axial flow wind turbine 100 is in operation, airflow flows in from the leading edge and flows out from the trailing edge. That is, the position of the blade contacted by the airflow first is the front edge 2, the position of the airflow flowing out of the blade last is the tail edge 3, the air inlet direction refers to the incoming flow direction of the airflow, and the air outlet direction refers to the outflow direction of the airflow. The blade tip 4 refers to the boundary area of the blade, in the radial direction of the blade, which is remote from the hub 1. The pressure surface 5 is the surface of the blade facing the air outlet direction and is also the surface with higher pressure. The suction surface 6 is a surface of the blade facing the air intake direction and is also a surface having a lower pressure. The surface of the blade is taken as a reference surface, the area of the blade facing the air inlet direction is upstream, and the area of the blade facing the air outlet direction is upstream.

As shown in fig. 4, the radius of the hub 1 is R1, the maximum outer radius of the axial-flow wind wheel 100 is R2, and the radial blade height of the blade is Rm, which is R2-R1. As shown in fig. 5 and 6, when the hub 1 is cylindrical, R1 is a cylindrical radius. When the hub 1 is not a cylinder with an equal diameter or radius, for example, the hub 1 is a cone (not shown), that is, one end of the hub 1 is large, and the other end is small, the average radius of the hub 1 is taken as R1. The maximum outer radius of axial flow wind wheel 100 is R2, which is the maximum outer circumferential radius of the blade. For some special application occasions, when the outer ring of the blade is additionally provided with the water ring, the size of the water ring is not considered, and the maximum outer circumference radius of the blade is taken.

As shown in fig. 4, a first circle a is formed by taking the rotation central axis of the axial flow wind wheel 100 as a center and taking R1+ 90% Rm as a radius, the intersection point of the first circle a and the leading edge 2 is a first intersection point a1, and the intersection point of the first circle a and the trailing edge 3 is a second intersection point a 2; taking R1+ 5% Rm as a radius to form a second circle b, wherein the intersection point of the second circle b and the leading edge 2 is a third intersection point A3, and the intersection point of the second circle b and the trailing edge 3 is a fourth intersection point A4; taking R1+ 50% Rm as a radius to form a third circle c, wherein the intersection point of the third circle c and the leading edge 2 is a fifth intersection point A5, and the intersection point of the third circle c and the trailing edge 3 is a sixth intersection point A6; taking R1+ 70% Rm as a radius to form a fourth circle d, wherein the intersection point of the fourth circle d and the leading edge 2 is a seventh intersection point A7, and the intersection point of the fourth circle d and the trailing edge 3 is an eighth intersection point A8; taking R1+ 30% Rm as a radius to form a fifth circle e, wherein the intersection point of the fifth circle e and the leading edge 2 is a ninth intersection point A9, and the intersection point of the fifth circle e and the trailing edge 3 is a tenth intersection point A10; a connecting line of the first intersection point a1 and the third intersection point A3 is a first connecting line L1, a distance from the fifth intersection point a5 to the first connecting line L1 is h1, a distance from the seventh intersection point a7 to the first connecting line L1 is h2, a distance from the ninth intersection point a9 to the first connecting line L1 is h3, wherein h1> h2, h1> h3, h1 ═ 0.09-0.13) R2, h2 ═ 0.06-0.10) R2, and h3 ═ 0.06-0.10) R2.

That is, in the projection view of the blade on the horizontal plane, as shown in fig. 7, the leading edge 2 is in a circular arc shape and sweepforward towards the upstream air intake direction, that is, as shown in fig. 4, in the region between the radial blade height of 5% Rm and the radial blade height of 90% Rm, the shape of the leading edge 2 of the blade can be smoothly fitted by using a section of circular arc curve, and the single-edge error fluctuation of the fitted arc is within less than 3 mm.

Here, R1+ 90% Rm is selected as the radius of the first circle a, instead of R1+ Rm as the circle of the first intersection point a1 intersecting the leading edge 2 and the second intersection point a2 intersecting the trailing edge 3 as the points to be considered, in order to protect the safety of the leading edge 2 and the trailing edge 3 near the tip 4 region and reduce the falling damage of the tip or tip region of the trailing edge 3. In particular, the leading edge 2, the trailing edge 3 near the blade tip area may be provided with chamfers or fillets or the like. For example, in the region beyond 90% Rm, the region may extend outward along the curve of the leading edge 2 or the trailing edge 3 to intersect with the blade tip 4, and the front and rear intersection points are chamfered, so as to reduce the sharpness of the tip or the top region of the trailing edge 3 and improve the rigidity of the blade. The tip of the blade means the region of the leading edge 2 adjacent to the tip 4.

On the other hand, R1+ 5% Rm is selected as the radius to make the second circle b, instead of directly selecting the hub 1 with the radius of R1 to make a circle as the third intersection point A3 intersecting the leading edge 2 of the blade and the fourth intersection point a4 intersecting the trailing edge 3 of the blade as the points to be considered, because in the root region with the radial blade height of less than 5% Rm, the corresponding radius is small, the rotational linear speed is low, the work capacity corresponding to the blade is weak, the influence of the flow on the wind volume and noise of the whole wind wheel is small, and therefore, the regions other than 5% Rm are mainly considered. In this way, at the position where the blade root is connected with the hub 1, the strengthening design, the large fillet design and the like can be carried out according to the requirements so as to improve the strength of the blade in the hub 1 area. For another example, when the blade root region is thick, a deduplication process may be performed at the position where the blade is connected to the hub 1 to reduce the weight of the axial flow wind turbine 100. It should be noted that the blade root refers to the area of the blade adjacent to the hub 1.

It can be understood that in the related art, the axial flow wind wheel mostly adopts straight blades, when the blades rotate, the linear velocity of the area adjacent to the blade tip is high, and the blade tip is easy to form vortex, so that vortex loss is generated, and the noise is high. The embodiment of the utility model provides an in, the leading edge 2 of blade is circular-arc sweepforward direction of admitting air sweepforward, and the blade can form C shape static pressure distribution at apex surface area, reduces the response of blade to import flow field distortion, and the noise reduction reduces the swirl loss for the blade has great flow margin, thereby improves axial flow wind wheel 100's the amount of wind.

According to the utility model discloses axial flow wind wheel 100, through the shape of injecing leading edge 2 for leading edge 2 is circular-arc sweepforward direction of air admission sweepforward, thereby the blade can form C shape static pressure distribution at apex surface area, can reduce the response of blade to import flow field distortion, and the noise reduction reduces the vortex loss, makes the blade have great flow margin, and then improves axial flow wind wheel 100's the amount of wind.

In a particular embodiment of the invention, the shape of the leading edge 2 may be completely designed as a circular arc. Preferably, the radius of the arc of the leading edge 2 is 0.63R2, h1 is 0.10R2, h2 is 0.08R2, and h3 is 0.08R2, so that the aerodynamic noise characteristics are excellent.

In some embodiments, as shown in fig. 7, at least a portion of the trailing edge 3 of the blade projects in the downstream air exit direction in the air flow direction. Therefore, the area of the blade can be increased and the working capacity of the blade can be improved through the ingenious design that the tail edge 3 protrudes towards the downstream, so that the air quantity of the axial flow wind wheel 100 is improved.

Specifically, as shown in fig. 8, a connection line between the second intersection a2 and the fourth intersection a4 is a second connection line L2, a distance from the sixth intersection a6 to the second connection line L2 is W1, a distance from the tenth intersection a10 to the second connection line L2 is W2, and a distance from the eighth intersection A8 to the second connection line L2 is W3, where W1> W2> W3, W1 ═ R2 (0.08-0.12), W2 ═ R2 (0.06-0.09), and W3 ═ 0.03-0.06) R2. The intersection, the connection line and the distance value are all the intersection, the connection line and the distance value corresponding to the projection view of the blade on the horizontal plane when the blade tip of the blade is upward and the blade is horizontally placed on the horizontal plane. The distances from the intersection points to the connection points are all vertical distances from the intersection points to the connection lines.

It will be appreciated that by defining W1> W2> W3, W1 ═ 0.08 to 0.12R 2, W2 ═ 0.06 to 0.09R 2, and W3 ═ 0.03 to 0.06R 2, the radially central region of the blade projects more in the downstream air-exit direction and the trailing edge 3 projects less downstream near the blade root and the blade tip 4. Meanwhile, the projection amount of the 30% Rm radial blade height area is larger than that of the 70% Rm radial blade height area. Therefore, by controlling the protrusion amount of different areas of the blade, the secondary flow on the surface of the blade can be improved, the air quantity of the axial flow wind wheel 100 is improved, the influence of the wake of the blade is weakened, and the noise and the wake loss are reduced.

In some specific embodiments, W1 ═ 0.10R2, W2 ═ 0.073R2, and W3 ═ 0.047R2, so that axial flow wind turbine 100 has lower blade wake, excellent low noise characteristics and high wind volume, less swirl loss.

In some embodiments, as shown in fig. 9, a connection line between the first intersection point a1 and the rotation center o of the axial-flow wind wheel 100 is a third connection line L3, a connection line between the second intersection point a2 and the rotation center o is a fourth connection line L4, and an included angle between the third connection line L3 and the fourth connection line L4 is defined as a first included angle Ω 1, where Ω 1 is in a range from 85 ° to 105 °. A connecting line between the third intersection point A3 and the rotation center o is a fifth connecting line L5, a connecting line between the fourth intersection point a4 and the rotation center o is a sixth connecting line L6, an included angle between the fifth connecting line L5 and the sixth connecting line L6 is defined as a second included angle Ω 2, the range of Ω 2 is 70-90 °, and Ω 1 is greater than Ω 2. It is understood that the inner flow characteristics of the axial flow wind turbine 100 may be improved by defining a range between the first included angle and the second included angle. Particularly, the range of the first included angle omega 1 is 85 degrees to 105 degrees, so that the whole area of the blade is large, the working capacity of the blade is favorably improved, in addition, the sharp degree of the front edge 2 is moderate, the rigidity of the blade is favorably improved, the production and the processing are convenient, and the mutual interference between the blades is reduced. The range of the second included angle omega 2 is 70-90 degrees, so that the area of the blade in the blade root area is moderate, the rigidity of the blade root is favorably improved, the connection stability of the blade and the hub 1 is improved, and the working safety of the axial flow wind wheel 100 is improved.

In a specific embodiment of the present invention, Ω 1 takes 93 °, Ω 2 takes 81 °, and axial flow wind wheel 100 has a better internal flow characteristic.

In some embodiments, as shown in FIG. 10, the orthographic area of each blade in the horizontal plane is S1, and the annular area between the hub 1 and the maximum outer diameter of the blade is S2, wherein S1/S2 is 0.23-0.26. The projection area of the blade on the horizontal plane refers to the projection area of the blade on the horizontal plane when the tip of the blade is upward and the blade is horizontally placed on the horizontal plane, and does not refer to the area of the blade in space. In actual operation, the blade has a certain installation angle, and the projected area S1 of the blade on the horizontal plane is smaller than the actual area of the blade, and the projected area S1 does not include the area in the area of the blade hub 1. Here, the annular area S2 between the hub 1 and the maximum outer diameter R2 of the blade is the area occupied by the region of the maximum outer diameter R2 of the blade minus the area occupied by the region of the central hub 1, i.e., S2 is 3.14 (R2 × R2-R1 × R1).

It can be understood that the projection area S1 of the blade on the horizontal plane accounts for 23% to 26% of the annular area S2 between the hub 1 and the maximum outer diameter of the blade, so that a single blade is large, the working capacity of the blade can be improved, the leakage of the gap between the blade top 4 can be reduced, the air volume of the axial flow wind wheel 100 can be improved, the stability of the blade during rotation can be improved, and the noise can be reduced.

In one embodiment of the present invention, S1/S2 may be 0.243, and axial flow wind wheel 100 has low noise and high wind volume.

In some embodiments, as shown in FIGS. 7 and 11, the tip 4 curves from the pressure side 5 to the suction side 6. Therefore, the airflow condition of the area of the blade top 4 can be improved, the gap loss of the area of the blade top 4 is reduced, the air quantity is increased, and the noise is reduced.

In particular, it is characterized in that the height of the tip 4 curving from the pressure side 5 to the suction side 6 is T, where T is (0.02-0.04) R2. Therefore, the height of the bending of the blade top 4 from the pressure surface 5 to the suction surface 6 is limited, so that the throughput of airflow at the blade top 4 can be improved, the blockage of the bending of the blade top 4 to the airflow is reduced, the airflow distribution in the area of the blade top 4 can be further improved, and the gap loss in the area of the blade top 4 is reduced.

In some embodiments, as shown in fig. 11 and 12, an arc line between the first intersection point a1 and the second intersection point a2 is defined as a seventh line L7, a plane passing through the rotation center o of the axial-flow wind turbine 100 and the seventh line L7 is a longitudinal plane, the longitudinal plane is a longitudinal section of a section of the blade, and in a direction from the blade tip 4 to the rotation center o, a boundary line of the longitudinal section on the suction surface 6 includes a first section of curve q1, a second section of curve q2, and a third section of curve q3 connected in this order, the first section of curve q1 extends from top to bottom toward the rotation center, the second section of curve q2 extends from bottom to top toward the rotation center, and the third section of curve q3 extends from top to bottom toward the rotation center; in the direction from the blade tip 4 to the rotation center o, the boundary line of the longitudinal section on the pressure surface 5 includes a fourth curve q4, a fifth curve q5, and a sixth curve q6 connected in this order, the fourth curve q4 extends from top to bottom toward the rotation center, the fifth curve q5 extends from bottom to top toward the rotation center, and the sixth curve q6 extends from top to bottom toward the rotation center. Therefore, leakage of gaps of the blade tops 4 can be effectively reduced by the aid of the first section curve q and the fourth section curve q4, secondary flow on the surfaces of the blades can be improved by the aid of the curve sections, air flow on the surfaces of the blades is reorganized, air quantity of the axial flow wind wheel 100 is effectively improved, loss of the axial flow wind wheel 100 can be reduced, noise of the axial flow wind wheel 100 is reduced, and aerodynamic performance is improved.

Specifically, the lowest point where the first section of curve q1 and the second section of curve q2 intersect is a point K, and the radial distance between the point K and the rotation center o is Rk, where Rk is R1+ (0.85-0.95) Rm. In other embodiments, for ease of manufacturing, the area of the pressure surface 5 where the first curve q1 intersects the second curve q2 may be partially ground to form a small straight line, where the lowest point of the intersection is not a point, and where the outermost point of the line segment corresponding to the lowest point with the largest radius is taken as the K point.

Therefore, the radial position of the K point is located in a (85% -95%) Rm radial blade height area, so that the gap loss of a blade top 4 area can be well reduced, the air quantity and the noise are improved, the work efficiency of the impeller is improved, and the aerodynamic noise characteristic is improved.

Further, three longitudinal sections are provided, which pass through quartering points a11, a12 and a13 on a seventh connecting line L7 respectively, and are f1, f2 and f3 respectively in the direction from the front edge 2 to the tail edge 3; the highest point of the intersection of the fifth section of curve q5 and the sixth section of curve q6 is a point G, the vertical distance between the point G and the point K is V, the V value of the longitudinal section f1 is V1, the V value of the longitudinal section f2 is V2, and the V value of the longitudinal section f3 is V3, wherein V1< V2< V3. When the suction surface 6 is provided with the reinforcing ribs locally, the suction surface is locally thickened, and the height position of the point G does not include the height of the reinforcing ribs locally designed. Therefore, the gap loss of the blade top 4 area can be well reduced, the air quantity is improved, the noise is reduced, and the work efficiency and the pneumatic performance of the impeller are improved.

In a specific embodiment of the present invention, V1 of the f1 section is 0.012R2, and T1 is 0.032R 2; v2 ═ 0.022R2 and T2 ═ 0.032R2 for the f2 section; the V3 of the f3 section is 0.081R2, the T3 is 0.028R2, when V1< V2< V3, the value of T is 2% -4% of the radius of the outer circumference of the impeller, and the axial flow wind wheel 100 has excellent aerodynamic noise characteristics. T1 is the height at which the tip 4 corresponding to the longitudinal section f1 bends from the pressure surface 5 to the suction surface 6, T2 is the height at which the tip 4 corresponding to the longitudinal section f2 bends from the pressure surface 5 to the suction surface 6, and T3 is the height at which the tip 4 corresponding to the longitudinal section f3 bends from the pressure surface 5 to the suction surface 6. Where T corresponds to the maximum of T1, T2, T3.

The utility model discloses a specific embodiment, the position of the K point on f1 cross-section is located 0.90Rm department, and the position of the K point on f2 cross-section is located 0.88Rm department, and the position of the K point on f3 cross-section is located 0.91Rm department, can reduce the regional clearance loss of top of leaf 4 better, improves the amount of wind and noise reduction, promotes the efficiency of doing work of impeller.

The utility model discloses axial flow wind wheel 100 has that the amount of wind is big, and the noise is low, and the low power dissipation, work margin is big, the wide characteristic of operating mode scope. For example, when the axial flow wind wheel 100 (diameter 535, height 170) of the present invention is applied to an outdoor unit of an air conditioner, the noise can be reduced by 3-4 db and the motor power is reduced by 5% compared to the conventional axial flow wind wheel when the air volume of 3700 cubic meters/hour is generated.

An axial flow wind turbine 100 in one implementation of the invention is described below with reference to fig. 1-13.

According to the utility model discloses axial compressor wind wheel 100, including wheel hub 1 and a plurality of blade, a plurality of blade intervals are established on wheel hub 1, and every blade includes leading edge 2, trailing edge 3, blade top 4, pressure side 5 and suction surface 6.

The radius of the hub 1 is R1, the maximum outer radius of the axial flow wind wheel 100 is R2, the radial blade height of each blade is Rm, and Rm is R2-R1; taking the axis of the wind wheel as the center, respectively taking R1+ 90% Rm, R1+ 5% Rm, R1+ 50% Rm, R1+ 70% Rm and R1+ 30% Rm as the radiuses to make a first circle to a fifth circle, wherein the intersection points of the five circles and the blade leading edge 2 are respectively a point A1, a point A3, a point A5, a point A7 and a point A9. The connecting line of the point a1 and the point A3 is a first connecting line, the distances from the point a5, the point a7 and the point a9 to the first connecting line are h1, h2 and h3 respectively, h1 is greater than h2, h1 is greater than h3, h1 is (0.09-0.13) R2, h2 is (0.06-0.10) R2, and h3 is (0.06-0.10) R2.

The intersection points of these five circles with the trailing edge 3 of the blade are point a2, point a4, point a6, point A8 and point a10, respectively. The connecting line of the point A2 and the point A4 is a second connecting line, the distance from the point A6 to the second connecting line is W1, the distance from the point A10 to the second connecting line is W2, and the distance from the point A8 to the second connecting line is W3, wherein W1> W2> W3, W1 is (0.08-0.12) R2, W2 is (0.06-0.09) R2, and W3 is (0.03-0.06) R2.

The connecting lines of the point a1, the point a2, the point A3 and the point a4 with the rotation center o of the axial flow wind wheel 100 are respectively a third connecting line, a fourth connecting line, a fifth connecting line and a sixth connecting line, an included angle between the third connecting line L3 and the fourth connecting line L4 is defined as a first included angle Ω 1, the range of Ω 1 is 85-105 °, an included angle between the fifth connecting line L5 and the sixth connecting line L6 is defined as a second included angle Ω 2, the range of Ω 2 is 70-90 °, and Ω 1> Ω 2. The orthographic projection area of each blade on the horizontal plane is S1, the annular area between the hub 1 and the maximum outer diameter of each blade is S2, and S1/S2 is 0.23-0.26.

The height of the curve of the blade tip 4 from the pressure side 5 to the suction side 6 is T, where T is (0.02 to 0.04) R2.

An arc line between the point a1 and the point a2 is defined as a seventh connecting line, a plane passing through a rotation center o of the axial flow wind wheel 100 and the seventh connecting line is a longitudinal plane, the longitudinal plane is a longitudinal section relative to the section of the blade, and in the direction from the blade top 4 to the rotation center o, the boundary line of the longitudinal section on the suction surface 6 comprises a first section of curve q1, a second section of curve q2 and a third section of curve q3 which are sequentially connected, the first section of curve q1 extends from top to bottom towards the rotation center, the second section of curve q2 extends from bottom to top towards the rotation center, and the third section of curve q3 extends from top to bottom towards the rotation center; in the direction from the blade tip 4 to the rotation center o, the boundary line of the longitudinal section on the pressure surface 5 includes a fourth curve q4, a fifth curve q5, and a sixth curve q6 connected in this order, the fourth curve q4 extends from top to bottom toward the rotation center, the fifth curve q5 extends from bottom to top toward the rotation center, and the sixth curve q6 extends from top to bottom toward the rotation center. The lowest point where the first section of curve q1 and the second section of curve q2 intersect is a point K, and the radial distance between the point K and the rotation center o is Rk, wherein Rk is R1+ (0.85-0.95) Rm.

The three longitudinal sections respectively pass through quartering points A11, A12 and A13 on a seventh connecting line L7, and are f1, f2 and f3 in the direction from the front edge 2 to the tail edge 3; the highest point of the intersection of the fifth section of curve q5 and the sixth section of curve q6 is a point G, the vertical distance between the point G and the point K is V, the V value of the longitudinal section f1 is V1, the V value of the longitudinal section f2 is V2, and the V value of the longitudinal section f3 is V3, wherein V1< V2< V3.

According to the utility model discloses the air conditioner, include the utility model discloses the axial compressor wind wheel 100 of above-mentioned embodiment.

According to the utility model discloses the air conditioner is through the shape of injecing axial flow wind wheel 100's leading edge 2 for leading edge 2 is circular-arc sweepforward direction of air inlet sweepforward, can reduce the swirl loss, makes the blade have great flow margin, thereby can promote the amount of wind of air conditioner, reduces compressor power, reduces the noise of air conditioner, improves the heat dissipation capacity of air conditioner.

Other configurations of the air conditioner according to the embodiments of the present invention, such as guide vanes and electric control boxes, etc., and operations thereof are known to those skilled in the art, and will not be described in detail herein.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "an illustrative embodiment," "an example," "a specific example," or "some examples" or the like mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

While embodiments of the present invention have been shown and described, it will be understood by those of ordinary skill in the art that: various changes, modifications, substitutions and alterations can be made to the embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the claims and their equivalents.

Claims

1. An axial flow wind wheel is characterized by comprising a hub and a plurality of blades, wherein the blades are arranged on the hub at intervals, each blade comprises a front edge, a tail edge, a blade top, a pressure surface and a suction surface, and the front edge of each blade is swept forward in an arc shape in an upstream air inlet direction;

the radius of the hub is R1, the maximum outer radius of the axial flow wind wheel is R2, the radial blade height of each blade is Rm, and Rm is R2-R1;

taking the rotation central axis of the axial flow wind wheel as a center, taking R1+ 90% Rm as a radius to make a first circle, wherein the intersection point of the first circle and the leading edge is a first intersection point A1, and the intersection point of the first circle and the trailing edge is a second intersection point A2; taking R1+ 5% Rm as a radius to form a second circle, wherein the intersection point of the second circle and the leading edge is a third intersection point A3, and the intersection point of the second circle and the trailing edge is a fourth intersection point A4; a third circle is formed by taking R1+ 50% Rm as a radius, the intersection point of the third circle and the leading edge is a fifth intersection point A5, and the intersection point of the third circle and the trailing edge is a sixth intersection point A6; making a fourth circle by taking R1+ 70% Rm as a radius, wherein the intersection point of the fourth circle and the leading edge is a seventh intersection point A7, and the intersection point of the fourth circle and the trailing edge is an eighth intersection point A8; making a fifth circle with R1+ 30% Rm as a radius, wherein the intersection point of the fifth circle and the leading edge is a ninth intersection point A9, and the intersection point of the fifth circle and the trailing edge is a tenth intersection point A10;

a connection line between the first intersection point a1 and the third intersection point A3 is a first connection line L1, a distance from the fifth intersection point a5 to the first connection line L1 is h1, a distance from the seventh intersection point a7 to the first connection line L1 is h2, a distance from the ninth intersection point a9 to the first connection line L1 is h3, wherein h1> h2, h1> h3, h1 ═ R2, (0.09-0.13) R2, h2 ═ 539 (0.06-0.10) R2, and h3 ═ R2 (0.06-0.10).

2. The axial flow wind wheel of claim 1, wherein at least a portion of the trailing edge of the blade in an air flow direction is convex toward a downstream air exit direction.

3. The axial-flow wind wheel according to claim 2, wherein a connection line between the second intersection point a2 and a fourth intersection point a4 is a second connection line L2, a distance from the sixth intersection point a6 to the second connection line L2 is W1, a distance from the tenth intersection point a10 to the second connection line L2 is W2, and a distance from the eighth intersection point A8 to the second connection line L2 is W3, wherein W1> W2> W3 is W1 (0.08-0.12) R2, W2 (0.06-0.09) R2, and W3 (0.03-0.06) R2.

4. The axial-flow wind wheel according to claim 1, characterized in that a line connecting the first intersection point a1 and the rotation center o of the axial-flow wind wheel is a third line L3, a line connecting the second intersection point a2 and the rotation center o is a fourth line L4, an included angle between the third line L3 and the fourth line L4 is defined as a first included angle Ω 1, and the range of Ω 1 is 85 ° to 105 °;

a connecting line between the third intersection point A3 and the rotation center o is a fifth connecting line L5, a connecting line between the fourth intersection point a4 and the rotation center o is a sixth connecting line L6, an included angle between the fifth connecting line L5 and the sixth connecting line L6 is defined as a second included angle Ω 2, the range of Ω 2 is 70-90 °, and Ω 1 is greater than Ω 2.

5. The axial-flow wind wheel according to claim 1, wherein the orthographic projection area of each blade on the horizontal plane is S1, the annular area between the hub and the maximum outer diameter of the blade is S2, and S1/S2 is 0.23-0.26.

6. The axial wind wheel of claim 1, wherein the blade tips curve from the pressure face to the suction face.

7. The axial flow wind wheel of claim 6, wherein the height of the curvature of the blade tip from the pressure surface to the suction surface is T, where T ═ (0.02-0.04) R2.

8. The axial-flow wind wheel according to any of claims 1-7, characterized in that a circular arc line between the first intersection point A1 and the second intersection point A2 is defined as a seventh line L7, a plane passing through the rotation center o of the axial-flow wind wheel and the seventh line L7 is a longitudinal plane, the longitudinal plane is a longitudinal section to the cross section of the blade, the boundary line of the longitudinal section on the suction surface in the direction from the blade tip to the rotation center o includes a first section of curve q1, a second section of curve q2 and a third section of curve q3 connected in sequence, the first section of curve q1 extends from top to bottom toward the rotation center, the second section of curve q2 extends from bottom to top toward the rotation center, and the third section of curve q3 extends from top to bottom toward the rotation center;

in the direction from the blade tip to the rotation center o, the boundary line of the longitudinal section on the pressure surface includes a fourth section of curve q4, a fifth section of curve q5 and a sixth section of curve q6 which are connected in sequence, the fourth section of curve q4 extends from top to bottom toward the rotation center, the fifth section of curve q5 extends from bottom to top toward the rotation center, and the sixth section of curve q6 extends from top to bottom toward the rotation center.

9. The axial-flow wind wheel according to claim 8, wherein the lowest point where the first section curve q1 and the second section curve q2 intersect is a point K, and the radial distance between the point K and the rotation center o is Rk, wherein Rk is R1+ (0.85-0.95) Rm.

10. The axial wind rotor according to claim 9, characterized in that said longitudinal sections are three, three of said longitudinal sections passing through quartering points a11, a12, a13 on said seventh connecting line L7, respectively, and in a direction from said leading edge to said trailing edge, three of said longitudinal sections are f1, f2, f3, respectively;

the highest point of the intersection of the fifth section of curve q5 and the sixth section of curve q6 is a point G, the vertical distance between the point G and the point K is V, the V value of the longitudinal section f1 is V1, the V value of the longitudinal section f2 is V2, and the V value of the longitudinal section f3 is V3, wherein V1< V2< V3.

11. An air conditioner characterized by comprising the axial flow wind wheel according to any one of claims 1 to 10.