CN219366352U

CN219366352U - Diagonal flow fan blade, fan and humidifying equipment

Info

Publication number: CN219366352U
Application number: CN202223457634.9U
Authority: CN
Inventors: 张驰; 柳洲; 梁浩; 李文龙; 单敬伟
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2022-12-22
Filing date: 2022-12-22
Publication date: 2023-07-18
Anticipated expiration: 2032-12-22

Abstract

The application relates to an oblique flow fan blade, a fan and humidifying equipment, wherein the oblique flow fan blade comprises a hub and a blade arranged on the hub, a reference variable base cylindrical surface is arranged, and the base cylindrical surface and the hub are concentrically arranged; the base cylindrical surface is intersected with the blade to obtain a base circular section by cutting, and an included angle between a chord line of the base circular section and a rotation plane of the blade in the radial direction of the hub is a blade mounting angle; the radius of the base cylindrical surface is R, the maximum radius of the diagonal flow fan blade is R, and the installation angle of the fan blade is Q; the variation range of the R/R ratio is between 0.35 and 0.98, when the R/R ratio is gradually increased, the angle value of Q is gradually reduced, and the variation range of the angle value of Q is between 57.5 and 33 degrees. According to the wind turbine blade, the angle value change range of the blade installation angle is set between 57.5 degrees and 33 degrees, the wind rate expansion rate is higher than or equal to the torque increase rate, the load of the blade is reduced, the wind performance is improved, and the wind efficiency is improved.

Description

Diagonal flow fan blade, fan and humidifying equipment

Technical Field

The application relates to the technical field of fan blades, in particular to an oblique flow fan blade, a fan and humidifying equipment.

Background

Along with the improvement of living standard, people also increase along with the function of fan, performance diversity demand, and more favour to bringing the fan of comfortable experience, for example possess the thermantidote of humidification function, evaporation formula humidifier, among the conventional art, the fan all adopts ordinary axial fan blade, possesses the advantage that the amount of wind is big, the noise is low, but ordinary axial fan blade has the problem that the air quantity performance promotes the inefficiency that the income leads to lowly.

Disclosure of Invention

Based on this, it is necessary to provide an oblique flow fan blade, a fan and a humidifying device which can increase the air volume performance improvement benefit to make the fan blade efficiency high, aiming at the problem of low efficiency caused by the low air volume performance improvement benefit in the existing common axial flow fan blade.

In a first aspect, the present application provides an oblique flow fan blade, including a hub and a blade disposed on the hub, where a reference variable base cylindrical surface is disposed, and the base cylindrical surface is disposed concentrically with the hub;

the base cylindrical surface is intersected with the blade to obtain a base circular section by cutting, and an included angle between a chord line of the base circular section and a rotation plane of the blade in the radial direction of the hub is a blade mounting angle;

the radius of the base cylindrical surface is R, the maximum radius of the diagonal flow fan blade is R, and the installation angle of the fan blade is Q;

the variation range of the R/R ratio is between 0.35 and 0.98, when the R/R ratio is gradually increased, the angle value of Q is gradually reduced, and the variation range of the angle value of Q is between 57.5 and 33 degrees.

In one embodiment, the blade has a tip, a root, a leading edge and a trailing edge, the tip and the root being disposed opposite and spaced apart from each other in a radial direction of the hub, the leading edge and the trailing edge being disposed between the tip and the root, the leading edge and the trailing edge being disposed opposite and spaced apart from each other in a rotational direction of the diagonal flow blade, the leading edge being disposed forward of the trailing edge in the rotational direction;

the sweep of the leading edge increases gradually from the root to the tip.

In one embodiment, in the axial direction of the hub, the base circle cross section and the front edge intersect to form a second intersection point, a connecting line of the second intersection point and the center point of the hub is L4, a tangent line of the front edge at the second intersection point is L5, and an included angle between the L4 and the L5 is a net bending angle A2 of the blade;

wherein the angle value of A2 is varied between 12 DEG and 46 deg.

the degree of sweep of the tip increases gradually from the trailing edge to the leading edge.

In one embodiment, in the axial direction of the hub, a line connecting a midpoint of a blade top and a midpoint of an arc of a base circle section is L1, a line connecting a midpoint of a blade root and a center point of the hub is L2, a line connecting an intersection point of L1 and the base circle section and a center point of the hub is L3, and an included angle between L2 and L3 is a net bending angle A1 of the blade;

wherein the angle value of A1 is varied between 1 DEG and 15 deg.

in the axial direction of the hub, the base circle cross section and the rear edge are intersected to form a third intersection point, the connecting line of the third intersection point and the central point of the hub is L6, the tangent line of the rear edge at the third intersection point is L7, and the included angle between the L6 and the L7 is the net bending angle A3 of the blade;

wherein the angle value of A3 is between 10 DEG and 13 deg.

an included angle alpha is formed between the front edge and the blade tip, and the range of the angle alpha is 50-60 degrees.

In one embodiment, the number of the fan blades is a plurality of fan blades and an odd number of fan blades.

In one embodiment, the hub is conical, the hub is provided with a first end and a second end which are opposite along the axial direction of the hub, the diameter of the end face of the first end is d1, the diameter of the end face of the second end is d2, d1 is less than d2, and the wind flow direction of the diagonal flow fan blade flows from the first end to the second end;

the maximum outer diameter of the diagonal flow fan blade is D, D1/D is more than or equal to 0.25 and less than or equal to 0.4, and D2/D is more than or equal to 0.7 and less than or equal to 0.8.

In one embodiment, the hub is conical, the front edge and the rear edge of the blade are opposite to each other along the rotation direction of the diagonal flow fan blade and are arranged at intervals, and the front edge is positioned in front of the rear edge along the rotation direction;

wherein the front edge of the blade forms a first intersection point with the outer conical surface of the hub, and the diameter of a base circle concentric with the hub through the first intersection point is d3, d3/d1=1.1.

In one embodiment, the blade has a tip and a root, the tip and the root being opposite and spaced apart along a radial direction of the hub;

the chord length of the chord line of the base circle section is k, and the ratio of k/R gradually increases from the blade root to the blade top.

In one embodiment, the ratio of k/R varies from 0.45 to 1.3.

In a second aspect, a fan is provided, including the diagonal flow fan blade in any of the foregoing embodiments.

In a third aspect, a humidifying device is provided, including the blower.

According to the diagonal flow fan blade, the fan and the humidifying equipment, the change range of the R/R ratio is set between 0.35 and 0.98, when the R/R ratio is gradually increased, the angle value of the blade mounting angle is gradually reduced, the change range of the angle value of the blade mounting angle is 57.5-33 degrees, the strength of the diagonal flow fan blade can be effectively ensured, and the overall load of the diagonal flow fan blade can be reduced. In addition, the inlet resistance is reduced, the fluid is smoothly developed, the pressure pulsation on the blades is reduced, the load noise of the blades is reduced, the energy loss of the air flow is reduced, and the efficiency of the fan is improved. In addition, the change range of the angle value of the blade installation angle is set between 57.5 degrees and 33 degrees, so that the air volume expansion rate is higher than or equal to the torque increase rate, the load of the blade is reduced, the air volume performance improvement benefit is increased, and the efficiency of the blade is further improved.

Drawings

FIG. 1 is a schematic view of a diagonal flow fan blade according to an embodiment of the present disclosure;

FIG. 2 is a rear view of a portion of the structure of the diagonal flow fan blade shown in FIG. 1;

FIG. 3 is a right side view of the diagonal flow fan blade shown in FIG. 1;

FIG. 4 is a cross-sectional view of one of the diagonal flow blades shown in FIG. 1;

FIG. 5 is a front view of the diagonal flow fan blade shown in FIG. 1;

FIG. 6 is a rear view of the diagonal flow fan blade of FIG. 1;

FIG. 7 is a front view of a portion of the structure of the diagonal flow fan blade shown in FIG. 1;

FIG. 8 is a graph showing the performance of a diagonal flow blade as a function of blade mounting angle at the blade root;

FIG. 9 shows a pressure distribution contrast of a vane;

FIG. 10 shows a graph of the variation in the wind volume of a fan blade for different wind resistances;

FIG. 11 shows a vane wake vortex comparison schematic.

Reference numerals:

diagonal flow fan blade 100;

a hub 10;

a blade 20;

blade root 21, blade tip 22, leading edge 23, trailing edge 24, suction side 25, pressure side 26.

Detailed Description

In order to make the above objects, features and advantages of the present application more comprehensible, embodiments accompanied with figures are described in detail below. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present application. This application is, however, susceptible of embodiment in many other forms than those described herein and similar modifications can be made by those skilled in the art without departing from the spirit of the application, and therefore the application is not to be limited to the specific embodiments disclosed below.

Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. The terminology used herein in the description of the application is for the purpose of describing particular embodiments only and is not intended to be limiting of the application. The term "and/or" as used herein includes any and all combinations of one or more of the associated listed items.

In the description of the present application, it should be understood that the terms "center," "longitudinal," "transverse," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," etc. indicate orientations or positional relationships based on the orientation or positional relationships shown in the drawings, are merely for convenience in describing the present application and simplifying the description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be configured and operated in a particular orientation, and therefore should not be construed as limiting the present application.

Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In the description of the present application, the meaning of "plurality" is at least two, such as two, three, etc., unless explicitly defined otherwise.

In this application, unless specifically stated and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; either directly or indirectly, through intermediaries, or both, may be in communication with each other or in interaction with each other, unless expressly defined otherwise. The specific meaning of the terms in this application will be understood by those of ordinary skill in the art as the case may be.

In this application, unless expressly stated or limited otherwise, a first feature "up" or "down" a second feature may be the first and second features in direct contact, or the first and second features in indirect contact via an intervening medium. Moreover, a first feature being "above," "over" and "on" a second feature may be a first feature being directly above or obliquely above the second feature, or simply indicating that the first feature is level higher than the second feature. The first feature being "under", "below" and "beneath" the second feature may be the first feature being directly under or obliquely below the second feature, or simply indicating that the first feature is less level than the second feature.

It will be understood that when an element is referred to as being "fixed" or "disposed" on another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and the like are used herein for illustrative purposes only and are not meant to be the only embodiment.

The accompanying drawings are not 1:1, and the relative dimensions of the various elements are drawn by way of example only in the drawings and are not necessarily drawn to true scale.

FIG. 1 is a schematic view of a diagonal flow fan blade according to an embodiment of the present disclosure; FIG. 2 is a rear view of a portion of the structure of the diagonal flow fan blade shown in FIG. 1; FIG. 3 is a right side view of the diagonal flow fan blade shown in FIG. 1; FIG. 4 is a cross-sectional view of one of the diagonal flow blades shown in FIG. 1.

Referring to the drawings, an embodiment of the present application provides a diagonal flow fan blade 100, which includes a hub 10 and blades 20 disposed on the hub 10. The diagonal flow fan blade 100 is applied to a fan, and the diagonal flow fan blade 100 is driven to rotate by a motor. Specifically, the fan can be applied to humidification equipment such as a cooling fan with a humidification function and an evaporation type humidifier.

The root of the blade 20 is fixedly connected to the outer peripheral wall of the hub 10, and in particular, the blade 20 is an airfoil blade. The blade 20 includes a blade root 21 and a blade tip 22 disposed opposite to the blade root 21 in a radial direction of the hub 10 at a distance, and the blade 20 further includes a leading edge 23 and a trailing edge 24 between the blade root 21 and the blade tip 22, wherein the leading edge 23 and the trailing edge 24 are disposed opposite to and at a distance in a rotational direction of the diagonal flow blade 100.

The blade 20 is also provided with a suction surface 25 and a pressure surface 26 which are positioned between the blade root 21 and the blade tip 22 and between the front edge 23 and the rear edge 24, wherein the suction surface 25 is the surface facing the air flow during the rotation of the diagonal flow blade 100, and the pressure surface 26 is the surface facing away from the air flow during the rotation of the diagonal flow blade 100.

The diagonal flow fan blade 100 may include a plurality of blades 20, and the plurality of blades 20 are spaced apart from each other along the circumferential direction of the hub 10.

In the embodiment of the present application, the number of the blades 20 is an odd number, and the number of the blades 20 may be 7, 3, 5, 9, or the like. The number of the blades 20 can intuitively influence the working area and the flow cross-section area of the diagonal flow fan blade 100, and the smaller number of the blades 20 can reduce the whole working area of the diagonal flow fan blade 100, so that the air quantity of the diagonal flow fan blade 100 is influenced. Too many blades 20 will increase the area ratio of the blades 20 at the flow break surface, so that the fluid flow passage area is reduced, and at the same time, too many blades 20 will increase the overall load of the diagonal flow fan blade 100, so as to increase the motor cost. In addition, since the diagonal flow fan blade 100 having the even number of blades 20 has a symmetrical structure, axial tension generated during operation of the diagonal flow fan blade 100 is more likely to cause fatigue fracture and vibration of the blades 20.

The number of the blades 20 is an odd number, so that the generation of axial tension can be avoided, and the breakage and vibration of the blades 20 can be avoided. Preferably, the number of the blades 20 is 7, so that the diagonal flow fan blade 100 has a higher working area, the wind flow of the diagonal flow fan blade 100 is improved, and the fluid flow passage area is large.

With continued reference to fig. 1, 5 and 6, in the embodiment of the present application, the hub 10 is tapered, the hub 10 has a first end and a second end opposite to each other along an axial direction thereof, a diameter of an end face of the first end is D1, a diameter of an end face of the second end is D2, D1 is less than D2, a wind flow direction of the diagonal flow fan blade 100 flows from the first end to the second end, a maximum outer diameter of the diagonal flow fan blade 100 is D, D1/D is more than or equal to 0.25 and less than or equal to 0.4, and D2/D is more than or equal to 0.7 and less than or equal to 0.8.

By designing the hub 10 into a small-end air inlet and large-end air outlet mode, the radial fluid suction at the air inlet is increased on the basis of the direct inlet and direct outlet axial air supply of the traditional axial flow fan blade, the air suction range is enlarged, and therefore the working flow of the diagonal flow fan blade 100 is increased. Moreover, the conical hub 10 is designed to increase the centrifugal force in the radial direction while the diagonal flow fan blade 100 supplies air in the axial direction, and increase the negative pressure on the surface of the blade 20, so that the negative pressure suction force of the diagonal flow fan blade 100 is increased, and the area of the suction inlet is larger than the area of the air outlet when the diagonal flow fan blade 100 is matched with the air supply of a runner, and according to the continuity of fluid, the air speed of the air outlet can be increased, the kinetic energy of the blade is increased, the loss of the kinetic energy when the negative pressure of the blade 20 is increased is counteracted, and the working capacity of the blade 20 is ensured.

With continued reference to fig. 2, in some embodiments, when the hub 10 is tapered, the leading edge 23 of the blade 20 forms a first intersection point a with the outer conical surface of the hub 10, and a base circle concentric with the hub 10 through the first intersection point a has a diameter d3, d3/d1=1.1.

In this way, the aerodynamic performance of the front edge 23 of the blade 20 is ensured, and the blade surface work-doing efficient area is reserved, so that the blade 20 can be normally installed relative to the hub 10, and the work-doing performance is ensured not to be influenced by the structure of the hub 10.

Referring to fig. 4 and 7, for a more clear description of the shape and size of the blades 20 of the present application, reference variable base cylindrical surface S is incorporated herein, the base cylindrical surface S being disposed concentrically with the hub 10.

The base cylindrical surface S intersects the blade 20 to intercept a base circular section AA, and an angle between a chord line CL of the base circular section AA and a rotation plane PR of the blade 20 in a radial direction of the hub 10 is a blade mounting angle.

The chord line CL of the base circle section AA refers to the line connecting the two ends of the base circle section AA.

The rotation plane PR is a plane in which the tip locus of the blade 20 is located when the blade 20 rotates one revolution around the axis of the hub 10. The rotation plane PR appears as a straight line when seen in the radial direction of the hub 10.

The radius of the base cylindrical surface S is R, R is a variable, the maximum radius of the diagonal flow fan blade 100 is R, that is, the maximum outer diameter of the blade 20, and the blade mounting angle is Q.

It should be noted that the ratio R/R increases gradually from the root 21 toward the tip 22, and the blade mounting angle Q changes with the radius of the base cylindrical surface.

The angle value of the blade installation angle Q close to the blade root 21 is large, so that the strength of the diagonal flow fan blade 100 can be effectively ensured, the overload is avoided, the angle value of the blade installation angle Q gradually decreases from the blade root 21 to the blade top 22, the overall load of the diagonal flow fan blade 100 can be effectively reduced, and the pressure of a motor in a fan is reduced.

In addition, if the angle value of the blade mounting angle Q is excessively large, the space when the air fluid flows through the diagonal flow fan blade 100 is reduced, the inlet resistance is increased, the development of the fluid is hindered, and the large angle value of the blade mounting angle Q increases the load on the blade 20, thereby affecting the pressure distribution of the blade meter, increasing the pressure pulsation, and causing the load noise of the blade 20 to be increased. If the angle value of the blade mounting angle Q is too small, the lift force of the blade 20 decreases, so that the axial power capability of the blade 20 to the air flow decreases, the energy loss of the air flow increases, and the fan efficiency decreases.

Therefore, in the diagonal flow fan blade 100, the R/R ratio change range is set between 0.35 and 0.98, when the R/R ratio is gradually increased, the angle value of Q is gradually reduced, the angle value change range of Q is 57.5-33 degrees, the strength of the diagonal flow fan blade 100 can be effectively ensured, and the overall load of the diagonal flow fan blade 100 can be reduced. In addition, inlet resistance is reduced, fluid is smoothly developed, pressure pulsation on the blades 20 is reduced, load noise of the blades 20 is reduced, energy loss of air flow is reduced, and fan efficiency is improved.

To further verify the effect achieved by the ratio of R/R ranging from 0.35 to 0.98, as the ratio of R/R increases gradually, the angle value of Q decreases gradually, and the angle value of Q ranges from 57.5 ° to 33 °, the following comparative examples and examples are provided for reference:

table 1:

table 1 shows the variation of the performance of the diagonal flow blade with the blade mounting angle of the blade root.

FIG. 8 shows a graph of performance of a diagonal flow blade as a function of blade mounting angle at the blade root.

As can be seen from table 1 and fig. 8, the air volume and torque of the diagonal flow fan blade 100 increase with the increase of the angle value of the blade mounting angle Q of the blade root 21, and when the angle value of the blade mounting angle Q of the blade root 21 is greater than about 57 degrees, the air volume expansion rate is lower than the torque increase rate, the load of the blade 20 increases, and the air volume performance improvement benefit decreases.

Therefore, the angle value change range of the blade mounting angle Q is set between 57.5 degrees and 33 degrees, and the air volume expansion rate can be higher than or equal to the torque increase rate, so that the load of the blade 20 is reduced, the air volume performance improves the gain, and the efficiency of the blade is improved.

In a preferred embodiment of the present application, Q corresponds to values of 57.2 °, 51.2 °, 46.4 °, 42 °, 39 °, 36.4 °, 33 ° when the R/R ratio is 0.35, 0.4, 0.5, 0.65, 0.75, 0.85, 0.98.

In some embodiments, the chord length of the chord line CL of the base circular section AA is k, with the ratio of k/R increasing from the root 21 to the tip 22.

The main source of the noise generated by the fan is the airflow pulsating force acting on the blade 20, and the airflow pulsating force can cause the blade surface vortex and the vortex to be separated, so that the noise is generated, and the ratio of b/R is gradually increased from the blade root 21 to the blade top 22, namely the width of the blade 20 close to the blade top 22 is larger than the width close to the blade root 21, so that the formation and separation of the blade surface vortex can be effectively inhibited and reduced, and the noise reduction purpose is achieved. In addition, the pressure gradient between the blade root 21 and the blade tip 22 can be reduced, so as to achieve the purpose of reducing the low power consumption area of the blade 20.

Further, the ratio of k/R varies from 0.45 to 1.3.

Preferably, when the R/R ratio is 0.35, 0.4, 0.5, 0.65, 0.75, 0.85, 0.98, the k/R corresponds to a value of 0.45, 0.54, 0.66, 0.8, 0.92, 1.1, 1.3.

In some embodiments, the degree of sweep of the tip 22 increases gradually from the trailing edge 24 to the leading edge 23.

The low speed of the main flow in the boundary layer of a conventional axial flow fan blade, the centrifugal force of which is greater than the radial pressure gradient, causes the low energy fluid in the boundary layer to migrate radially outwards and accumulate near the tip 22, thereby increasing tip 22 loss and tip 22 stall. When the sweep of the blade tip 22 increases gradually from the trailing edge 24 to the leading edge 23, the centrifugal force of the fluid in the boundary layer of the blade 20 can be reduced, so that the blade tip 22 of the blade 20 can be effectively restrained from stalling, the energy loss of the blade 20 at the blade tip 22 is reduced, and the air supply efficiency of the blade 20 is improved.

Further, in the axial direction of the hub 10, the line between the midpoint b of the blade tip 22 and the arc midpoint c of the base circle section AA is L1, the line between the midpoint d of the blade root 21 and the center point O of the hub 10 is L2, the line between the intersection point of L1 and the base circle surface S and the center point O of the hub 10 is L3, the included angle between L2 and L3 is the net blade bending angle A1, and the variation range of the angle value of A1 is between 1 ° and 15 °.

Preferably, when the R/R ratio is 0.35, 0.4, 0.5, 0.65, 0.75, 0.85, 0.98, the A1 corresponds to values of 1 °, 3 °, 5 °, 8 °, 10 °, 13 °, 15 °.

In some embodiments, the sweep of the leading edge 23 increases gradually from the root 21 to the tip 22.

This arrangement eliminates backflow from the leading edge 23 of the blade 20, absorbs low energy fluid from the endwall region into the high energy main flow in the blade 20, and reduces end low energy fluid accumulation, thereby reducing flow losses and flow blockage. Secondly, the influence of the shell and the end wall of the hub 10 on She Daona flow can be weakened, accumulation of low-energy fluid is restrained, the attenuation speed of wake of the blade 20 is accelerated, the characteristic that the low-energy fluid at the end wall near the suction surface 25 of the blade 20 is carried downstream by the main flow can obviously improve the internal flow state of the blade 20, thereby restraining the shedding of vortex on the surface of the blade 20, reducing broadband noise of the blade 20 and improving sound quality.

Further, the base circle cross section AA and the front edge 23 intersect to form a second intersection point e, a connecting line of the second intersection point e and the center point O of the hub 10 is L4, a tangent line of the front edge 23 at the second intersection point e is L5, an included angle between the L4 and the L5 is a net bending angle A2 of the blade, and a variation range of an angle value of the A2 is between 12 ° and 46 °.

Preferably, when the R/R ratio is 0.35, 0.4, 0.5, 0.65, 0.75, 0.85, 0.98, the A2 corresponds to values of 12 °, 13 °, 15 °, 20 °, 22 °, 28 °, 40 °.

To further verify the other effects achieved by the angular values of A2 ranging from 12 ° to 46 °, the present application provides comparative examples and examples for reference, and fig. 9 shows a pressure distribution comparison of the blade.

As can be seen from fig. 9, compared with a common axial flow fan blade, the diagonal flow fan blade 100 according to the embodiment of the present application can effectively reduce the pressure gradient of the blade 20 at the front edge 23, increase the She Biaogao power distribution area, and promote the functional power of the area close to the blade root 21, thereby improving the overall performance of the blade 20 under high wind resistance.

In some embodiments, the base circle cross-section AA intersects the trailing edge 24 to form a third intersection point f, the third intersection point f is connected with the center point O of the hub 10 by L6, the tangent line of the trailing edge 24 at the third intersection point f is L7, the included angle between L6 and L7 is the blade net bending angle A3, and the angle value of A3 ranges from 10 ° to 13 °.

It should be noted that the net blade bending angle A3 is constant at the same base circle section AA.

When the turbulent boundary on the surface of the blade 20 passes the trailing edge 24 of the blade 20, local pulsating forces are generated, and furthermore, the karman vortex street at the trailing edge of the blade 20 also generates local pulsating forces with narrower frequency characteristics, and due to the existence of these aerodynamic forces, vortex shedding occurs on the blade 20, thereby generating blade 20 noise. The range of the angle value of the A3 is between 10 degrees and 13 degrees, so that the separation of vortex at the rear edge 24 of the blade 20 can be effectively restrained, and the noise of the blade 20 is reduced.

In some embodiments, the leading edge 23 forms an angle α with the tip 22 that ranges between 50 ° and 60 °.

By setting the alpha angle to be 50-60 degrees, the generation of blade tip vortex and front edge 23 separation vortex can be effectively reduced, thereby achieving the purpose of reducing aerodynamic noise.

In the preferred embodiment of the present application, the number of blades 20 is an odd number, the hub 10 is tapered, 0.25.ltoreq.d1/D.ltoreq.0.4, and 0.7.ltoreq.d2/D.ltoreq.0.8. d3/d1=1.1. The variation range of the R/R ratio is between 0.35 and 0.98, when the R/R ratio is gradually increased, the angle value of Q is gradually reduced, and the variation range of the angle value of Q is between 57.5 and 33 degrees. The ratio k/R increases gradually. The ratio of k/R varies from 0.45 to 1.3. The degree of sweep of the tip 22 increases gradually from the trailing edge 24 to the leading edge 23. The angle value of A1 is varied between 1 DEG and 15 deg. The sweep of the leading edge 23 increases gradually from the root 21 to the tip 22. The angle value of A2 is varied between 12 DEG and 46 deg. The angle value of A3 is between 10 DEG and 13 deg. The leading edge 23 forms an angle alpha with the tip 22 in the range of 50 deg. to 60 deg..

To further verify the effect of the preferred embodiments of the present application described above, the present application provides the following comparative examples and examples for reference:

table 2:

table 2 shows the variation of the wind volume of the fan blade at different wind resistances.

as can be seen from table 2 and fig. 10, under the working condition of larger wind resistance, the performance of the preferred fan blade is obviously higher than that of the common fan blade, the resistance is improved to some extent, and the air loss is small, so that the air flow channel air pressure is further increased while the air flow performance is ensured, the overall performance of the air channel system is improved, the interaction capability of the dry and wet air of the air channel of the humidifying equipment is further improved, and the humidifying capacity of the humidifying equipment can achieve the expected effect.

Fig. 11 shows a comparative schematic of the blade wake vortices, where (a) shows the blade wake vortices of a common fan blade and (b) shows the blade wake vortices of a preferred embodiment of the present application.

As can be seen from FIG. 11, the conventional fan blade generates a relatively obvious vortex in the wake of the fan blade, and the preferred fan blade of the present application can effectively inhibit the vortex of the wake of the fan blade.

Based on the same inventive concept, the present application also provides a fan, including the diagonal flow fan blade 100 in any embodiment described above.

Specifically, the fan further comprises a shell and a motor, the diagonal flow fan blade 100 is arranged in the shell, and the motor is connected with the hub of the diagonal flow fan blade 100 and used for driving the diagonal flow fan blade 100 to rotate.

Based on the same inventive concept, the application also provides a humidifying device, which comprises the fan in any embodiment.

The diagonal flow fan blade 100, the fan and the humidifying equipment provided by the embodiment of the application have the following beneficial effects:

according to the diagonal flow fan blade 100, the change range of the R/R ratio is set between 0.35 and 0.98, when the R/R ratio is gradually increased, the angle value of Q is gradually reduced, the change range of the angle value of Q is between 57.5 and 33 degrees, the strength of the diagonal flow fan blade 100 can be effectively ensured, and the overall load of the diagonal flow fan blade 100 can be reduced. In addition, inlet resistance is reduced, fluid is smoothly developed, pressure pulsation on the blades 20 is reduced, load noise of the blades 20 is reduced, energy loss of air flow is reduced, and fan efficiency is improved.

According to the method, the angle value change range of the blade mounting angle Q is set between 57.5 degrees and 33 degrees, the air volume expansion rate can be higher than or equal to the torque increase rate, so that the load of the blade 20 is reduced, the air volume performance improves the gain and further the efficiency of the fan blade is improved.

The technical features of the above-described embodiments may be arbitrarily combined, and all possible combinations of the technical features in the above-described embodiments are not described for brevity of description, however, as long as there is no contradiction between the combinations of the technical features, they should be considered as the scope of the description.

The above examples only represent a few embodiments of the present application, which are described in more detail and are not to be construed as limiting the scope of the patent. It should be noted that it will be apparent to those skilled in the art that several variations and modifications can be made without departing from the spirit of the utility model, which are all within the scope of the present application. Accordingly, the scope of protection of the present application is to be determined by the claims appended hereto.

Claims

1. The diagonal flow fan blade (100) is characterized by comprising a hub (10) and blades (20) arranged on the hub (10), wherein a reference variable base cylindrical surface is arranged, and the base cylindrical surface and the hub (10) are concentrically arranged;

the base cylindrical surface is intersected with the blade (20) to obtain a base circular section, and an included angle between a chord line of the base circular section and a rotation plane of the blade (20) in the radial direction of the hub (10) is a blade (20) mounting angle;

the radius of the base cylindrical surface is R, the maximum radius of the diagonal flow fan blade (100) is R, and the installation angle of the blade (20) is Q;

2. The diagonal flow blade (100) according to claim 1, wherein the blade (20) has a blade tip (22), a blade root (21), a leading edge (23) and a trailing edge (24), the blade tip (22) being arranged opposite and spaced from the blade root (21) in a radial direction of the hub (10), the leading edge (23) and the trailing edge (24) being located between the blade tip (22) and the blade root (21), the leading edge (23) being arranged opposite and spaced from the trailing edge (24) in a rotational direction of the diagonal flow blade (100), the leading edge (23) being located in front of the trailing edge (24) in the rotational direction;

the sweep of the leading edge (23) increases gradually from the blade root (21) to the blade tip (22).

3. Diagonal flow blade (100) according to claim 2, wherein in the axial direction of the hub (10) the base circular cross section intersects the leading edge (23) to form a second intersection point, the line connecting the second intersection point with the centre point of the hub (10) is L4, the tangent of the leading edge (23) at the second intersection point is L5, the angle between L4 and L5 is the net bending angle A2 of the blade (20);

wherein the angle value of A2 is varied between 12 DEG and 46 deg.

4. The diagonal flow blade (100) according to claim 1, wherein the blade (20) has a blade tip (22), a blade root (21), a leading edge (23) and a trailing edge (24), the blade tip (22) being arranged opposite and spaced from the blade root (21) in a radial direction of the hub (10), the leading edge (23) and the trailing edge (24) being located between the blade tip (22) and the blade root (21), the leading edge (23) being arranged opposite and spaced from the trailing edge (24) in a rotational direction of the diagonal flow blade (100), the leading edge (23) being located in front of the trailing edge (24) in the rotational direction;

the sweep of the tip (22) increases gradually from the trailing edge (24) to the leading edge (23).

5. The diagonal flow blade (100) according to claim 4, wherein in the axial direction of the hub (10), a line between a midpoint of the blade tip (22) and a midpoint of an arc of the base circle section is L1, a line between a midpoint of the blade root (21) and a center point of the hub (10) is L2, a line between an intersection of the L1 and the base circle section and a center point of the hub (10) is L3, and an included angle between L2 and L3 is a net bending angle A1 of the blade (20);

wherein the angle value of A1 is varied between 1 DEG and 15 deg.

6. The diagonal flow blade (100) according to claim 1, wherein the blade (20) has a blade tip (22), a blade root (21), a leading edge (23) and a trailing edge (24), the blade tip (22) being arranged opposite and spaced from the blade root (21) in a radial direction of the hub (10), the leading edge (23) and the trailing edge (24) being located between the blade tip (22) and the blade root (21), the leading edge (23) being arranged opposite and spaced from the trailing edge (24) in a rotational direction of the diagonal flow blade (100), the leading edge (23) being located in front of the trailing edge (24) in the rotational direction;

in the axial direction of the hub (10), the base circle cross section and the rear edge (24) intersect to form a third intersection point, a connecting line of the third intersection point and the central point of the hub (10) is L6, a tangent line of the rear edge (24) at the third intersection point is L7, and an included angle between the L6 and the L7 is a net bending angle A3 of the blade (20);

wherein the angle value of A3 is between 10 DEG and 13 deg.

7. The diagonal flow blade (100) according to claim 1, wherein the blade (20) has a blade tip (22), a blade root (21), a leading edge (23) and a trailing edge (24), the blade tip (22) being arranged opposite and spaced from the blade root (21) in a radial direction of the hub (10), the leading edge (23) and the trailing edge (24) being located between the blade tip (22) and the blade root (21), the leading edge (23) being arranged opposite and spaced from the trailing edge (24) in a rotational direction of the diagonal flow blade (100), the leading edge (23) being located in front of the trailing edge (24) in the rotational direction;

an included angle alpha is formed between the front edge (23) and the blade tip (22), and the angle alpha is in the range of 50-60 degrees.

8. The diagonal flow blade (100) according to claim 1, wherein the number of blades is a plurality and an odd number.

9. The diagonal flow blade (100) according to claim 1, wherein the hub (10) is cone-shaped, the hub (10) has a first end and a second end opposite to each other along an axial direction thereof, a diameter of an end face of the first end is d1, a diameter of an end face of the second end is d2, d1 < d2, and a wind flow direction of the diagonal flow blade (100) flows from the first end to the second end;

the maximum outer diameter of the diagonal flow fan blade (100) is D, D1/D is more than or equal to 0.25 and less than or equal to 0.4, and D2/D is more than or equal to 0.7 and less than or equal to 0.8.

10. The diagonal flow blade (100) according to claim 1, wherein the hub (10) is conical, a leading edge (23) and a trailing edge (24) of the blade (20), the leading edge (23) being opposite to and spaced apart from the trailing edge (24) in a direction of rotation of the diagonal flow blade (100), the leading edge (23) being located in front of the trailing edge (24) in the direction of rotation;

wherein the leading edge (23) of the blade (20) forms a first intersection point with an outer conical surface of the hub (10), a base circle diameter concentric with the hub (10) via the first intersection point being d3, d3/d1=1.1.

11. The diagonal flow blade (100) according to claim 1, wherein the blade (20) has a tip (22) and a root (21), the tip (22) being opposite and spaced from the root (21) in a radial direction of the hub (10);

the chord length of the chord line of the base circle section is k, and the ratio of k/R gradually increases from the blade root (21) to the blade tip (22).

12. The diagonal flow blade (100) according to claim 11, wherein the ratio of k/R varies from 0.45 to 1.3.

13. A fan comprising a diagonal flow blade (100) according to any of claims 1-12.

14. A humidifying apparatus comprising the blower of claim 13.