Mixed flow blade, fan and humidifying device

Abstract

The application relates to an axial flow fan blade, a fan and a humidifying device. The axial flow fan blade comprises a hub and a blade arranged on the hub, is provided with a reference variable base cylindrical surface, and the base cylindrical surface is arranged concentrically with the hub. The base cylindrical surface intersects with the blade to obtain a base circular section. In the radial direction of the hub, the included angle between the chord of the base circular section and the rotation plane of the blade is a blade installation angle. The radius of the base cylindrical surface is r, the maximum radius of the axial flow fan blade is R, and the blade installation angle is Q. The ratio of r / R is in the range of 0.35-0.98. When the ratio of r / R gradually increases, the angle value of Q gradually decreases, and the angle value of Q is in the range of 57.5 DEG -33 DEG. The application sets the angle value of the blade installation angle in the range of 57.5 DEG -33 DEG, can make the wind volume increase rate higher than or equal to the torque increase rate, thereby reducing the load of the blade, increasing the wind volume performance improvement benefit, and further improving the fan blade efficiency.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of fan blades, in particular to a mixed flow blade, a fan and a humidifying device. BACKGROUND

[0002] With the improvement of living standards, people's demand for fan functions and performance diversity also increases, and people prefer fans that bring comfortable experience, such as cold fans with humidifying function and evaporative humidifiers. In the traditional technology, the fan adopts ordinary axial flow fan blades, which have the advantages of large air volume and low noise, but the ordinary axial flow fan blades have the problem of low efficiency due to low air volume performance improvement benefit. SUMMARY

[0003] Therefore, it is necessary to provide a mixed flow blade, a fan and a humidifying device capable of increasing air volume performance improvement benefit to make the fan blade efficient in view of the problem of low efficiency due to low air volume performance improvement benefit of the existing ordinary axial flow fan blade.

[0004] In a first aspect, the present application provides a mixed flow fan blade, comprising a hub and a blade arranged on the hub, and a reference variable base cylindrical surface, wherein the base cylindrical surface is arranged concentrically with the hub;

[0005] The base cylindrical surface intersects with the blade to obtain a base circular cross section, and in the radial direction of the hub, the included angle between the chord of the base circular cross section and the rotation plane of the blade is a blade installation angle;

[0006] Wherein, the radius of the base cylindrical surface is r, the maximum radius of the mixed flow fan blade is R, and the blade installation angle is Q;

[0007] The ratio of r / R ranges from 0.35 to 0.98, when the ratio of r / R gradually increases, the angle value of Q gradually decreases, and the angle value of Q ranges from 57.5° to 33°.

[0008] In one embodiment, the blade has a tip, a root, a leading edge and a trailing edge, the tip and the root are arranged opposite and spaced apart in the radial direction of the hub, the leading edge and the trailing edge are located between the tip and the root, the leading edge and the trailing edge are arranged opposite and spaced apart in the rotation direction of the mixed flow fan blade, and the leading edge is located in front of the trailing edge in the rotation direction;

[0009] The sweep degree of the leading edge gradually increases from the root to the tip.

[0010] In one embodiment, in the axial direction of the hub, the base circular cross section intersects with the leading edge to form a second intersection point, the line connecting the second intersection point and the center point of the hub is L4, the tangent line of the leading edge at the second intersection point is L5, and the included angle between L4 and L5 is a blade net bending angle A2;

[0011] The angle value of A2 ranges from 12° to 46°.

[0012] In one embodiment, the blade has a tip, a root, a leading edge and a trailing edge, the tip and the root are oppositely and spacedly arranged along the radial direction of the hub, the leading edge and the trailing edge are located between the tip and the root, the leading edge and the trailing edge are oppositely and spacedly arranged along the rotation direction of the blade, and the leading edge is located in front of the trailing edge along the rotation direction.

[0013] The sweep degree of the tip gradually increases from the trailing edge to the leading edge.

[0014] In one embodiment, in the axial direction of the hub, the line connecting the midpoint of the tip and the midpoint of the circular arc of the base circle section is L1, the line connecting the midpoint of the root and the center point of the hub is L2, the line connecting the intersection point of L1 and the base circle section and the center point of the hub is L3, and the included angle between L2 and L3 is the net bending angle A1 of the blade.

[0015] The angle value of A1 ranges from 1° to 15°.

[0016] In one embodiment, the blade has a tip, a root, a leading edge and a trailing edge, the tip and the root are oppositely and spacedly arranged along the radial direction of the hub, the leading edge and the trailing edge are located between the tip and the root, the leading edge and the trailing edge are oppositely and spacedly arranged along the rotation direction of the blade, and the leading edge is located in front of the trailing edge along the rotation direction.

[0017] In the axial direction of the hub, the base circle section intersects with the trailing edge to form a third intersection point, the line connecting the third intersection point and the center point of the hub is L6, the tangent line of the trailing edge at the third intersection point is L7, and the included angle between L6 and L7 is the net bending angle A3 of the blade.

[0018] The angle value of A3 ranges from 10° to 13°.

[0019] In one embodiment, the blade has a tip, a root, a leading edge and a trailing edge, the tip and the root are oppositely and spacedly arranged along the radial direction of the hub, the leading edge and the trailing edge are located between the tip and the root, the leading edge and the trailing edge are oppositely and spacedly arranged along the rotation direction of the blade, and the leading edge is located in front of the trailing edge along the rotation direction.

[0020] An included angle α is formed between the leading edge and the tip, and the angle α ranges from 50° to 60°.

[0021] In one embodiment, the number of the blades is multiple and is an odd number.

[0022] In one of the embodiments, the hub is conical, the hub has opposite first and second ends along its axial direction, the end face of the first end has a diameter of d1, the end face of the second end has a diameter of d2, d1 < d2, and the airflow direction of the axial flow fan blade is from the first end to the second end;

[0023] The maximum outer diameter of the axial flow fan blade is D, 0.25 ≤ d1 / D ≤ 0.4, and 0.7 ≤ d2 / D ≤ 0.8.

[0024] In one of the embodiments, the hub is conical, the hub has opposite first and second ends along its axial direction, the end face of the first end has a diameter of d1, the end face of the second end has a diameter of d2, d1 < d2, and the airflow direction of the axial flow fan blade is from the first end to the second end;

[0025] In one of the embodiments, the hub is conical, the hub has opposite first and second ends along its axial direction, the end face of the first end has a diameter of d1, the end face of the second end has a diameter of d2, d1 < d2, and the airflow direction of the axial flow fan blade is from the first end to the second end;

[0026] In one of the embodiments, the chord of the base circle section has a chord length k, and the ratio of k / R gradually increases from the root to the tip.

[0027] In one of the embodiments, the ratio of k / R ranges from 0.45 to 1.3.

[0028] In one of the embodiments, the chord of the base circle section has a chord length k, and the ratio of k / R gradually increases from the root to the tip.

[0029] In one of the embodiments, the chord of the base circle section has a chord length k, and the ratio of k / R gradually increases from the root to the tip.

[0030] The axial flow fan blade, the fan and the humidifying device can effectively ensure the strength of the axial flow fan blade, and can reduce the overall load of the axial flow fan blade. In addition, the inlet resistance is reduced, the fluid develops smoothly, the pressure pulsation on the blade is reduced, the load noise of the blade is reduced, the airflow energy loss is reduced, and the fan efficiency is improved. In addition, the angle value of the blade installation angle is set to range from 57.5° to 33°, so that the airflow rate increase rate is higher than or equal to the torque increase rate, thereby reducing the load of the blade, improving the airflow performance, increasing the benefit, and further improving the fan efficiency. BRIEF DESCRIPTION OF DRAWINGS

[0031] Figure 1 FIG. 1 is a structural schematic view of an axial flow fan blade in an embodiment of the present application;

[0032] Figure 2 FIG. 2 is a front view of the partial structure of the axial flow fan blade shown in FIG. 1; Figure 1 ​

[0033] Figure 3 Fig. 1 is a perspective view of a cross-flow fan blade according to the present application; Figure 1 Fig. 2 is a right view of the cross-flow fan blade shown in Fig. 1;

[0034] Figure 4 Fig. 3 is a sectional view of one of the blades of the cross-flow fan blade shown in Fig. 1; Figure 1

[0035] Fig. 4 is a front view of the cross-flow fan blade shown in Fig. 1; Figure 5 Figure 1 Fig. 5 is a rear view of the cross-flow fan blade shown in Fig. 1;

[0036] Figure 6 Figure 1 Fig. 6 is a front view of a partial structure of the cross-flow fan blade shown in Fig. 1;

[0037] Figure 7 Fig. 7 is a graph showing the performance of the cross-flow blade as a function of the blade installation angle of the blade root; Figure 1

[0038] Fig. 8 is a graph showing the pressure distribution of the blade; Figure 8

[0039] Fig. 9 is a graph showing the change in the air volume of the fan blade under different air resistance; Figure 9

[0040] Fig. 10 is a contrast schematic diagram showing the wake vortex of the blade. Figure 10

[0041] Fig. 11 is a perspective view of a cross-flow fan blade according to the present application; Figure 11

[0042] Reference numerals:

[0043] cross-flow fan blade 100;

[0044] wheel hub 10;

[0045] blade 20;

[0046] blade root 21, blade tip 22, leading edge 23, trailing edge 24, suction surface 25, pressure surface 26. DETAILED DESCRIPTION

[0047] In order to make the above objects, features and advantages of the present application more apparent, specific embodiments of the present application will be described in detail below with reference to the accompanying drawings. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present application. However, it will be apparent to one skilled in the art that the present application can be practiced in a variety of ways beyond those specifically disclosed in the present application, and that the present application can be practiced with modifications and alterations without departing from the spirit and scope of the present application, and therefore the present application is not limited to the specific embodiments disclosed below.

[0048] ​​​Unless otherwise defined, 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 in the description herein is for describing particular embodiments only and is not intended to be limiting of the application. As used herein, the term "and / or" includes any and all combinations of one or more of the associated listed items.

[0049] In the description of the present application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the purpose of facilitating the description of the present application and simplifying the description, and 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 cannot be understood as limiting the present application.

[0050] In addition, the terms "first", "second", "third", etc. are used only for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Therefore, the features defined as "first", "second", etc. can explicitly or implicitly include at least one of the features. In the description of the present application, the meaning of "a plurality of" is at least two, such as two, three, etc., unless otherwise specifically limited.

[0051] In the present application, unless otherwise specifically defined and limited, the terms "mounting", "connecting", "connecting", "fixing" and the like should be understood broadly, for example, it can be fixedly connected, or it can be detachably connected, or it can be integrated; it can be mechanically connected, or it can be electrically connected; it can be directly connected, or it can be indirectly connected through an intermediate medium; it can be the internal communication of two elements or the interaction relationship between two elements, unless otherwise specifically defined. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0052] In the present application, unless otherwise specifically defined and limited, the first feature is "on" or "under" the second feature, which can be direct contact between the first and second features, or indirect contact between the first and second features through an intermediate medium. Moreover, the first feature "above", "above" and "above" the second feature can be directly above or obliquely above the first feature, or only indicate that the horizontal height of the first feature is higher than that of the second feature. The first feature "below", "below" and "below" the second feature can be directly below or obliquely below the first feature, or only indicate that the horizontal height of the first feature is less than that of the second feature.

[0053] It is to be noted that when an element is referred to as being "on" or "connected to" another element, it can be directly on the other element or intervening elements can 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 can also be present. The terms "vertical", "horizontal", "upper", "lower", "left", "right" and similar terms as used herein are for the purpose of illustration only and do not in any way limit the scope of the present application.

[0054] The accompanying drawings are not drawn to scale and the relative dimensions of the various elements in the drawings are only meant to be illustrative and not necessarily to scale.

[0055] Figure 1 A schematic view of a structure of a mixed flow impeller according to an embodiment of the present application; Figure 2 A schematic view of a structure of a mixed flow impeller according to an embodiment of the present application; Figure 1 A rear view of a partial structure of a mixed flow impeller according to an embodiment of the present application; Figure 3 A rear view of a partial structure of a mixed flow impeller according to an embodiment of the present application; Figure 1 A right view of a mixed flow impeller according to an embodiment of the present application; Figure 4 A right view of a mixed flow impeller according to an embodiment of the present application; Figure 1 A cross-sectional view of one of the blades of a mixed flow impeller according to an embodiment of the present application.

[0056] With reference to the drawings, an embodiment of the present application provides a mixed flow impeller 100, which comprises a hub 10 and blades 20 arranged on the hub 10. The mixed flow impeller 100 is applied to a fan, and is driven to rotate by a motor. Specifically, the fan can be applied to a cooling fan with a humidifying function, an evaporative humidifier or other humidifying equipment.

[0057] The root of the blade 20 is fixedly connected to the outer peripheral wall of the hub 10. Specifically, the blade 20 is an airfoil blade. The blade 20 comprises a blade root 21 and a blade tip 22 arranged opposite to the blade root 21 along the radial direction of the hub 10. The blade 20 further comprises a leading edge 23 and a trailing edge 24 arranged opposite to each other along the rotation direction of the mixed flow impeller 100.

[0058] The blade 20 further comprises a suction surface 25 and a pressure surface 26 arranged between the blade root 21 and the blade tip 22 and between the leading edge 23 and the trailing edge 24. The suction surface 25 is a surface facing the airflow during the rotation of the mixed flow impeller 100, and the pressure surface 26 is a surface facing away from the airflow during the rotation of the mixed flow impeller 100.

[0059] The mixed flow impeller 100 can comprise a plurality of blades 20 arranged opposite to each other along the circumferential direction of the hub 10.

[0060] In the embodiments of the present application, the number of blades 20 is odd, and the number of blades 20 can be 7, 3, 5, 9, etc. The number of blades 20 will have a direct impact on the working area and the flow area of the oblique flow fan blade 100. A smaller number of blades 20 will reduce the overall working area of the oblique flow fan blade 100, thereby affecting the air volume of the oblique flow fan blade 100. Too many blades 20 will increase the area ratio of the blades 20 at the flow break surface, reduce the fluid flow area, and increase the overall load of the oblique flow fan blade 100, thereby increasing the cost of the motor. In addition, the oblique flow fan blade 100 with an even number of blades 20 has a symmetrical structure, which will generate an axial tension when the oblique flow fan blade 100 is running, and is more likely to cause fatigue fracture and vibration of the blades 20.

[0061] Therefore, the number of blades 20 in the present application is odd, which can avoid generating axial tension and avoid blade 20 fracture and vibration. Preferably, the number of blades 20 is 7, which can make the oblique flow fan blade 100 have a higher working area, improve the airflow of the oblique flow fan blade 100, and have a large fluid flow area.

[0062] Please continue to refer to Figure 1 , Figure 5 and Figure 6 In the embodiments of the present application, the hub 10 is conical, and the hub 10 has opposite first and second ends along its axial direction. The diameter of the end face of the first end is d1, and the diameter of the end face of the second end is d2, d1 < d2. The airflow direction of the oblique flow fan blade 100 is from the first end to the second end, and the maximum outer diameter of the oblique flow fan blade 100 is D, 0.25 ≤ d1 / D ≤ 0.4, and 0.7 ≤ d2 / D ≤ 0.8.

[0063] By designing the hub 10 as a small-end inlet and a large-end outlet, the traditional axial flow fan blade can increase the radial fluid suction at the inlet and expand the suction range, thereby increasing the working flow of the oblique flow fan blade 100. In addition, the conical hub 10 design can increase the centrifugal force in the radial direction while the oblique flow fan blade 100 is axially blowing, thereby increasing the negative pressure on the surface of the blade 20, increasing the negative pressure suction of the oblique flow fan blade 100, and increasing the outlet area when the flow channel is used for blowing. According to the continuity of fluid, the outlet air speed can be increased, the kinetic energy of the blade can be increased, the loss of kinetic energy when the blade 20 is lifted can be offset, and the working capacity of the blade 20 can be ensured.

[0064] Please continue to refer to Figure 2 In some embodiments, when the hub 10 is conical, the leading edge 23 of the blade 20 forms a first intersection point a with the outer conical surface of the hub 10, and the diameter of the base circle concentric with the hub 10 through the first intersection point a is d3, d3 / d1 = 1.1.

[0065] Thus, the aerodynamic performance of the leading edge 23 of the blade 20 is ensured, and the high-efficiency area of the blade surface is reserved, so that the blade 20 can meet the normal installation relative to the hub 10 and ensure the working performance without being affected by the structure of the hub 10.

[0066] Please refer to Figure 4 and Figure 7 In order to more clearly describe the shape and size of the blade 20 of the present application, a reference variable base cylindrical surface S is introduced herein, which is arranged concentrically with the hub 10.

[0067] The base cylindrical surface S intersects the blade 20 to obtain a base circular cross section AA. In the radial direction of the hub 10, the included angle between the chord line CL of the base circular cross section AA and the rotation plane PR of the blade 20 is the blade installation angle.

[0068] The chord line CL of the base circular cross section AA refers to the connecting line between the two ends of the base circular cross section AA.

[0069] The rotation plane PR refers to the plane in which the tip trajectory of the blade 20 is located when the blade 20 rotates one revolution around the axis of the hub 10. When the rotation plane PR is viewed in the radial direction of the hub 10, it appears as a straight line.

[0070] Wherein, the radius of the base cylindrical surface S is r, r is a variable, the maximum radius of the mixed-flow fan blade 100 is R, that is, the maximum outer diameter of the blade 20, and the blade installation angle is Q.

[0071] The ratio of r / R changes in the range of 0.35-0.98. When the ratio of r / R gradually increases, the angle value of Q gradually decreases, and the angle value of Q changes in the range of 57.5°-33°.

[0072] It should be noted that the ratio of r / R gradually increases from the blade root 21 to the blade tip 22, and the blade installation angle Q changes with the change of the radius of the base cylindrical surface.

[0073] The angle value of the blade installation angle Q near the blade root 21 is large, which can effectively ensure the strength of the mixed-flow fan blade 100 and prevent the load from being too large. The angle value of the blade installation angle Q gradually decreases from the blade root 21 to the blade tip 22, which can effectively reduce the overall load of the mixed-flow fan blade 100, thereby reducing the pressure of the motor in the fan.

[0074] Furthermore, if the blade installation angle Q is too large, it will reduce the space for airflow through the oblique flow blade 100, increasing inlet resistance and hindering fluid development. A large blade installation angle Q will also increase the load on the blade 20, affecting the pressure distribution on the blade surface, increasing pressure pulsation, and causing increased load noise on the blade 20. If the blade installation angle Q is too small, the lift of the blade 20 will decrease, weakening its axial work capacity on the airflow, increasing airflow energy loss, and reducing fan efficiency.

[0075] Therefore, the oblique flow fan blade 100 of this application, by setting the r / R ratio variation range between 0.35 and 0.98, allows the angle value of Q to gradually decrease as the r / R ratio gradually increases, and the angle value of Q varies between 57.5° and 33°. This effectively ensures the strength of the oblique flow fan blade 100 and reduces the overall load on the oblique flow fan blade 100. Furthermore, it reduces inlet resistance, facilitates smooth fluid development, reduces pressure pulsation on the blade 20, lowers the load noise of the blade 20, reduces airflow energy loss, and improves fan efficiency.

[0076] To further verify the effect achieved when the r / R ratio is set between 0.35 and 0.98, and when the r / R ratio gradually increases, the angle value of Q gradually decreases, and the angle value of Q varies between 57.5° and 33°, this application provides the following comparative examples and embodiments for reference:

[0077] Table 1:

[0078]

[0079] Table 1 shows the variation of the performance of the oblique flow blade with the blade installation angle at the blade root.

[0080] Figure 8 The graph shows the performance of the oblique flow blade as a function of the blade installation angle at the blade root.

[0081] Combining Table 1 and Figure 8 It can be seen that the air volume and torque of the oblique flow fan blade 100 increase with the increase of the blade installation angle Q of the blade root 21. When the blade installation angle Q of the blade root 21 is greater than about 57 degrees, the air volume increase rate is lower than the torque increase rate, the load on the blade 20 increases, and the benefit of improving air volume performance decreases.

[0082] Therefore, this application sets the blade installation angle Q to a range of 57.5° to 33°, which enables the air volume increase rate to be higher than or equal to the torque increase rate, thereby reducing the load on the blade 20, increasing the benefits of improved air volume performance, and thus improving the efficiency of the blade.

[0083] In a preferred embodiment of the present application, when the ratio of r / R is 0.35, 0.4, 0.5, 0.65, 0.75, 0.85, 0.98, the corresponding value of Q is 57.2°, 51.2°, 46.4°, 42°, 39°, 36.4°, 33°.

[0084] In some embodiments, the chord length of the chord line CL of the base circle section AA gradually increases from the blade root 21 to the blade tip 22.

[0085] The main source of noise of the fan is the fluctuating force of the airflow acting on the blade 20, which can cause vortex shedding on the blade surface and thus generate noise. By gradually increasing the ratio of b / R from the blade root 21 to the blade tip 22, i.e., the width of the blade 20 near the blade tip 22 is greater than the width near the blade root 21, the formation and shedding of vortex on the blade surface can be effectively suppressed and reduced, thereby achieving the purpose of noise reduction. In addition, the pressure gradient between the blade root 21 and the blade tip 22 can also be reduced, achieving the purpose of reducing the low-power region of the blade 20.

[0086] Further, the ratio of k / R ranges from 0.45 to 1.3.

[0087] Preferably, when the ratio of r / R is 0.35, 0.4, 0.5, 0.65, 0.75, 0.85, 0.98, the corresponding value of k / R is 0.45, 0.54, 0.66, 0.8, 0.92, 1.1, 1.3.

[0088] In some embodiments, the sweep degree of the blade tip 22 gradually increases from the trailing edge 24 to the leading edge 23.

[0089] In a common axial fan, the main flow velocity in the boundary layer is low, and the centrifugal force is greater than the radial pressure gradient, which causes the low-energy fluid in the boundary layer to migrate radially outward and accumulate near the blade tip 22, thereby increasing the loss and stall of the blade tip 22. When the sweep degree of the blade tip 22 gradually increases 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, which can effectively suppress the stall of the blade tip 22 of the blade 20, thereby reducing the energy loss of the blade 20 at the blade tip 22 and improving the air supply efficiency of the blade 20.

[0090] Further, in the axial direction of the hub 10, the line connecting the midpoint b of the blade tip 22 and the midpoint c of the circular arc of the base circle section AA is L1, the line connecting the midpoint d of the blade root 21 and the center point O of the hub 10 is L2, the line connecting the intersection point of L1 and the base circle section S and the center point O of the hub 10 is L3, and the included angle between L2 and L3 is the net bending angle A1 of the blade, which ranges from 1° to 15°.

[0091] Preferably, when the r / R ratio is 0.35, 0.4, 0.5, 0.65, 0.75, 0.85, or 0.98, the corresponding values ​​of A1 are 1°, 3°, 5°, 8°, 10°, 13°, or 15°.

[0092] In some embodiments, the degree of sweep of the leading edge 23 gradually increases from the leaf root 21 to the leaf tip 22.

[0093] This scheme eliminates the backflow at the leading edge 23 of the blade 20, absorbing the low-energy fluid in the endwall region into the high-energy mainstream of the blade 20, thus reducing the accumulation of low-energy fluid at the end and reducing flow losses and flow blockage. Secondly, it reduces the influence of the casing and hub 10 endwalls on the flow inside the blade passage, suppresses the accumulation of low-energy fluid, and accelerates the decay rate of the blade 20 wake. The secondary flow characteristic of the low-energy fluid near the suction surface 25 of the blade 20 being carried downstream by the mainstream can significantly improve the internal flow state inside the blade 20, thereby suppressing the shedding of eddies on the surface of the blade 20, reducing the broadband noise of the blade 20, and improving sound quality.

[0094] Furthermore, the base circle section AA intersects with the leading edge 23 to form a second intersection point e. The line connecting the second intersection point e and the center point O of the hub 10 is L4. The tangent of the leading edge 23 at the second intersection point e is L5. The included angle between L4 and L5 is the blade net bending angle A2. The angle value of A2 varies between 12° and 46°.

[0095] Preferably, when the r / R ratio is 0.35, 0.4, 0.5, 0.65, 0.75, 0.85, or 0.98, the corresponding values ​​of A2 are 12°, 13°, 15°, 20°, 22°, 28°, or 40°.

[0096] To further verify other effects achieved by varying the angle value of A2 within the range of 12° to 46°, this application provides comparative examples and embodiments for reference. Figure 9 A comparison diagram of pressure distribution on the blades is shown.

[0097] Depend on Figure 9 As can be seen, compared with ordinary axial flow fan blades, the embodiment of this application is a diagonal flow fan blade 100, which can effectively reduce the pressure gradient at the leading edge 23 of the blade 20, increase the high efficiency distribution area on the blade surface, and improve the work capacity of the area near the blade root 21, thereby improving the overall performance of the blade 20 under high wind resistance.

[0098] In some embodiments, the base circle section AA intersects with the trailing edge 24 to form a third intersection point f. The line connecting the third intersection point f and the center point O of the hub 10 is L6. The tangent 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. The angle value of A3 is in the range of 10° to 13°.

[0099] It should be noted that the net bending angle A3 of the blade under the same base circle section AA is a constant value.

[0100] When the blade 20 surface turbulence boundary passes through the trailing edge 24 of the blade 20, a local pulsating force will be generated, in addition, the Karman vortex street of the trailing edge of the blade 20 also generates a local pulsating force with a narrower frequency characteristic. Due to the existence of these aerodynamic pulsating forces, vortex shedding occurs on the blade 20, thereby generating noise of the blade 20. The angle value of A3 in the present application is in the range of 10°-13°, which can effectively suppress the vortex shedding of the trailing edge 24 of the blade 20, thereby reducing the noise of the blade 20.

[0101] In some embodiments, an angle a is formed between the leading edge 23 and the tip 22, and the angle a is in the range of 50°-60°.

[0102] By setting the angle a in the range of 50°-60°, the tip vortex and the leading edge 23 separation vortex can be effectively reduced, thereby achieving the purpose of reducing aerodynamic noise.

[0103] In the preferred embodiment of the present application, the number of blades 20 is odd, the hub 10 is conical, 0.25≤d1 / D≤0.4, and 0.7≤d2 / D≤0.8. d3 / d1=1.1. The ratio of r / R changes in the range of 0.35-0.98, when the ratio of r / R gradually increases, the angle value of Q gradually decreases, and the angle value of Q changes in the range of 57.5°-33°. The ratio of k / R gradually increases. The ratio of k / R changes in the range of 0.45-1.3. The sweep degree of the tip 22 gradually increases from the trailing edge 24 to the leading edge 23. The angle value of A1 changes in the range of 1°-15°. The sweep degree of the leading edge 23 gradually increases from the blade root 21 to the tip 22. The angle value of A2 changes in the range of 12°-46°. The angle value of A3 is in the range of 10°-13°. An angle a is formed between the leading edge 23 and the tip 22, and the angle a is in the range of 50°-60°.

[0104] In order to further verify the effect of the above preferred embodiment of the present application, the following comparative examples and examples are provided for reference:

[0105] Table 2:

[0106]

[0107] Table 2 shows the change amount of the air volume of the fan blade under different wind resistances.

[0108] Figure 10 The change curve of the air volume of the fan blade under different wind resistances is shown;

[0109] In combination with Table 2 andFigure 10 It can be known that, under the condition of large wind resistance, the performance of the preferred fan blade of the application is obviously higher than that of the ordinary fan blade, the resistance capacity is improved, the wind volume loss is small, so as to further increase the flow passage wind pressure while ensuring the wind volume performance, thereby improving the overall performance of the air duct system, and further improving the interaction ability of the dry and wet air of the air duct of the humidifying equipment, so that the humidifying capacity of the humidifying equipment can achieve the expected effect.

[0110] Figure 11 The blade wake vortex contrast schematic diagram is shown, wherein (a) shows the blade wake vortex of the ordinary fan blade, and (b) shows the blade wake vortex of the preferred embodiment of the application.

[0111] From the above, it can be known that the ordinary fan blade will generate obvious vortex in the blade wake, while the blade of the preferred fan blade of the application can effectively suppress the blade wake vortex. Figure 11

[0112] Based on the same inventive concept, the application further provides a fan, comprising the inclined flow fan blade 100 in any of the above embodiments.

[0113] Specifically, the fan further comprises a shell and a motor, the inclined flow fan blade 100 is arranged in the shell, and the motor is connected with the hub of the inclined flow fan blade 100 and used to drive the inclined flow fan blade 100 to rotate.

[0114] Based on the same inventive concept, the application further provides a humidifying equipment, comprising the fan in any of the above embodiments.

[0115] The inclined flow fan blade 100, the fan and the humidifying equipment provided in the embodiments of the application have the following beneficial effects:

[0116] The inclined flow fan blade 100 of the application sets the change range of the ratio of r / R to be between 0.35 and 0.98, when the ratio of r / R gradually increases, the angle value of Q gradually decreases, and the change range of the angle value of Q is between 57.5° and 33°, which can effectively ensure the strength of the inclined flow fan blade 100 and reduce the overall load of the inclined flow fan blade 100. In addition, the inlet resistance is reduced, the fluid develops smoothly, the pressure pulsation on the blade 20 is reduced, the load noise of the blade 20 is reduced, the airflow energy loss is reduced, and the fan efficiency is improved.

[0117] The application sets the change range of the angle value of the blade installation angle Q to be between 57.5° and 33°, which can make the wind volume increase rate higher than or equal to the torque increase rate, thereby reducing the load of the blade 20, increasing the wind volume performance, and further improving the fan blade efficiency.

[0118] ​Any combination of the technical features in the above-described embodiments can be made, and for the sake of brevity, not all possible combinations are described, however, as long as there is no conflict, any combination of the technical features should be considered within the scope of the present disclosure.

[0119] The above-described embodiments only express several implementation manners of the present application, and the description is relatively specific and detailed, but it should not be understood as a limitation on the patent scope. It should be pointed out that, for ordinary skilled persons in the art, several modifications and improvements can be made without departing from the concept of the present application, and these all belong to the protection scope of the present application. Therefore, the protection scope of the patent of the present application should be subject to the appended claims.

Claims

1. A type of oblique-flow fan blade (100), characterized in that, Includes a hub (10) and blades (20) disposed on the hub (10), and has a reference variable base cylindrical surface, which is concentrically disposed with the hub (10); The base cylindrical surface intersects the blade (20) to obtain a base circle section. In the radial direction of the hub (10), the angle between the chord of the base circle section and the plane of rotation of the blade (20) is the blade (20) mounting angle. Wherein, the radius of the base cylindrical surface is r, the maximum radius of the oblique flow fan blade (100) is R, and the installation angle of the blade (20) is Q; The ratio of r / R varies between 0.35 and 0.

98. As the ratio of r / R gradually increases, the angle value of Q gradually decreases, and the angle value of Q varies between 57.5° and 33°. 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) and the blade root (21) are opposite to each other and spaced apart along the radial direction of the hub (10). The leading edge (23) and the trailing edge (24) are located between the blade tip (22) and the blade root (21). The leading edge (23) and the trailing edge (24) are opposite to each other and spaced apart along the rotation direction of the oblique flow fan blade (100). The leading edge (23) is located in front of the trailing edge (24) along the rotation direction. In the axial direction of the hub (10), the base circle section intersects with the trailing edge (24) to form a third intersection point. The line connecting the third intersection point and the center point of the hub (10) is L6, and the tangent of the trailing edge (24) at the third intersection point is L7. The included angle between L6 and L7 is the net bending angle A3 of the blade (20). The angle value of A3 is in the range of 10° to 13°. The hub (10) is conical and has a first end and a second end along its axial direction. The diameter of the end face of the first end is d1. The leading edge (23) of the blade (20) and the outer conical surface of the hub (10) form a first intersection point. The diameter of the base circle concentric with the hub (10) through the first intersection point is d3, and d3 / d1=1.

1.

2. The oblique flow fan blade (100) according to claim 1, characterized in that, The degree of sweep of the leading edge (23) gradually increases from the leaf root (21) to the leaf tip (22).

3. The oblique flow fan blade (100) according to claim 2, characterized in that, In the axial direction of the hub (10), the base circle section intersects with the leading edge (23) to form a second intersection point. The line connecting the second intersection point and the center point of the hub (10) is L4. The tangent of the leading edge (23) at the second intersection point is L5. The included angle between L4 and L5 is the net bending angle A2 of the blade (20). The angle value of A2 varies between 12° and 46°.

4. The oblique flow fan blade (100) according to claim 1, characterized in that, The degree of sweep of the blade tip (22) gradually increases from the trailing edge (24) to the leading edge (23).

5. The oblique flow fan blade (100) according to claim 4, characterized in that, In the axial direction of the hub (10), the line connecting the midpoint of the blade tip (22) and the midpoint of the arc of the base circle section is L1, the line connecting the midpoint of the blade root (21) and the center point of the hub (10) is L2, the line connecting the intersection of L1 and the base circle section and the center point of the hub (10) is L3, and the angle between L2 and L3 is the net bending angle A1 of the blade (20); The angle value of A1 varies between 1° and 15°.

6. The oblique flow fan blade (100) according to claim 1, characterized in that, An angle α is formed between the leading edge (23) and the blade tip (22), and the angle α ranges from 50° to 60°.

7. The oblique flow fan blade (100) according to claim 1, characterized in that, The number of wind blades is multiple, and is an odd number.

8. The oblique flow fan blade (100) according to claim 1, characterized in that, The diameter of the end face of the second end is d2, d1 < d2, and the airflow direction of the oblique flow fan (100) is from the first end to the second end; The maximum outer diameter of the oblique flow fan blade (100) is D, where 0.25≤d1 / D≤0.4 and 0.7≤d2 / D≤0.

8.

9. The oblique flow fan blade (100) according to claim 1, characterized in that, The chord length of the chord of the base circle section is k, and the ratio of k / R gradually increases from the leaf root (21) to the leaf tip (22).

10. The oblique flow fan blade (100) according to claim 9, characterized in that, The k / R ratio varies between 0.45 and 1.

3.

11. A fan, characterized in that, Includes the oblique flow fan blade (100) as described in any one of claims 1 to 10.

12. A humidification device, characterized in that, Including the wind turbine as described in claim 11.

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