Blades, impellers and ventilation devices

Abstract

This application relates to a blade, impeller, and ventilation device. The blade has a top surface and a bottom surface arranged opposite each other. Along a first direction from the bottom surface to the top surface, the trailing edge of the blade is sequentially provided with a first serrated segment, a second serrated segment, and a third serrated segment. The size of the first serrated tooth in the first serrated segment is larger than the size of the second serrated tooth in the second serrated segment, and the size of the second serrated tooth in the second serrated segment is larger than the size of the third serrated tooth in the third serrated segment. The technical solution of this application effectively solves the technical problems of low air volume, high noise, and high power consumption generated by traditional ventilation devices.

Description

Technical Field

[0001] This application relates to the field of impeller technology, and more particularly to a blade, impeller and ventilation equipment. Background Technology

[0002] Centrifugal fans are devices that use input mechanical energy to increase gas pressure and discharge gas. They are widely used in air conditioning equipment and household appliances. The impeller is a common component of centrifugal fans, and its performance is mainly reflected in airflow volume and noise control. In related technologies, to obtain a larger airflow, the impeller speed needs to be increased. However, when the impeller speed is too high, it can cause various abnormal sound qualities, creating significant noise and causing noise disturbance to users; at the same time, excessively high speeds also lead to greater power consumption. Summary of the Invention

[0003] This application provides a blade, impeller, and ventilation device to solve the technical problems of small air volume, high noise, and high power consumption of traditional ventilation devices.

[0004] To this end, in a first aspect, this application provides a blade having a top surface and a bottom surface disposed opposite to each other, and the trailing edge of the blade having a first serrated segment, a second serrated segment and a third serrated segment sequentially disposed along a first direction from the bottom surface to the top surface, wherein the size of the first serrated tooth of the first serrated segment is larger than the size of the second serrated tooth of the second serrated segment, and the size of the second serrated tooth of the second serrated segment is larger than the size of the third serrated tooth of the third serrated segment.

[0005] In one possible implementation, in the first direction, the total height of the blade is h, the height of the first serrated segment is h1, and the height of the second serrated segment is h2, wherein h1:h ranges from 0.15 to 0.25, and (h2+h1):h ranges from 0.3 to 0.5.

[0006] In one possible implementation, the height of the first sawtooth is d1, and the tooth depth of the first sawtooth is L1, wherein L1:d1 ranges from 0.6 to 0.8; and / or,

[0007] The height of the second sawtooth is d2, and the tooth depth of the second sawtooth is L2, where L2:d2 ranges from 1.1 to 1.5; and / or,

[0008] The height of the third saw tooth is d3, and the tooth depth of the third saw tooth is L3, where the range of L3:d3 is 0.5 to 0.7.

[0009] In one possible implementation, the midline of the two-dimensional airfoil of the blade is a free curve, and the free curve intersects the single circular arc in an X-shape or Y-shape.

[0010] In one possible implementation, in the direction from the leading edge to the trailing edge of the blade, the angle between the line connecting the starting point of the free curve and the center point of the impeller and the line connecting the ending point of the free curve and the center point of the impeller is γ, and the angle between the line connecting the starting point of the free curve and the center point of the impeller and the line connecting the intersection of the free curve and the single circular arc and the center point of the impeller is γ1, wherein γ1:γ ranges from 0.6 to 0.85.

[0011] In one possible implementation, the ratio of γ1:γ gradually decreases along a first direction.

[0012] In one possible implementation, there are multiple blades, which are arranged non-equidistantly on the circumference of the impeller, wherein the distribution pattern of the multiple blades satisfies the sinusoidal modulation theory.

[0013] In one possible implementation, the trailing edge of the blade is gradually widened in the first direction.

[0014] Secondly, this application also provides an impeller, comprising:

[0015] Wheel hub;

[0016] The chassis is located on the outer periphery of the wheel hub;

[0017] Wheel covers, concentrically positioned opposite the chassis; and

[0018] The blades described above are disposed between the chassis and the wheel cover, with the top surface of the blades facing the wheel cover.

[0019] In one possible implementation, the wheel cover includes an axially connected arcuate portion and a straight portion, the arcuate portion being disposed towards the chassis, and the connection between the straight portion and the arcuate portion being tangent.

[0020] In one possible implementation, in the first direction, the height of the wheel cover is SH1, and the height of the straight portion is SH2, wherein the ratio of SH2 to SH1 is in the range of 0.08 to 0.4; and / or,

[0021] The curvature of the arc-shaped portion is 0.15–0.35; and / or,

[0022] The angle of the end of the arc-shaped part away from the straight part is α, and it satisfies the following condition: 45°≤α≤60°.

[0023] In one possible implementation, the diameter of the chassis is D1 and the diameter of the wheel cover is D2 in the radial direction of the impeller, wherein the ratio of D2 to D1 is 1.02 to 1.1.

[0024] Thirdly, this application also provides a ventilation device, characterized in that it includes a housing, an impeller as described above, and a motor, wherein the impeller is rotatably disposed within the housing, and the motor is disposed at the rotation center axis of the impeller hub.

[0025] According to the blades, impellers and ventilation equipment provided in the embodiments of this application, the trailing edge of the blade is composed of at least three different tooth profiles to perform functional zoning of the trailing edge of the blade, thereby reducing torque, reducing power consumption, reducing noise generation and increasing air volume. Specifically, the first sawtooth section has the largest size of the first sawtooth, which reduces the chord length of the blade by reducing the size of the sawtooth, thereby achieving a rapid decrease in blade torque and power consumption, achieving the goal of low torque and low power consumption. The third sawtooth section has the smallest size of the third sawtooth, which introduces disturbance at the blade trailing edge, causing the laminar boundary layer on the blade surface to transition to the turbulent boundary layer in advance, effectively reducing the wake loss of the airflow. In addition, the large vortex of airflow at the blade exit end breaks into smaller vortices and detaches, thus disrupting the consistency of vorticity along the spanwise direction. In this way, the airflow can be increased while suppressing the increase of noise, achieving the goal of large airflow and low noise. The second sawtooth section is located between the first and third sawtooth sections, and the second sawtooth on it is of medium size. The medium-sized sawtooth enables stable flow of airflow between different functional areas at the blade trailing edge, improving the operational stability of the blade trailing edge. Attached Figure Description

[0026] The accompanying drawings, incorporated in and forming part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application. To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, those skilled in the art can obtain other drawings based on these drawings without creative effort. One or more embodiments are illustrated by way of example through the corresponding images in the accompanying drawings. These exemplary descriptions do not constitute a limitation on the embodiments. Elements with the same reference numerals in the drawings represent similar elements. Unless otherwise stated, the figures in the drawings do not constitute a limitation on scale.

[0027] Figure 1 A three-dimensional structural schematic diagram of the impeller provided in an embodiment of this application;

[0028] Figure 2 for Figure 1 The main view;

[0029] Figure 3 and Figure 4 All Figure 2 Enlarged view of point A in the middle;

[0030] Figure 5 for Figure 1 A partial top view, in which the free curve midline of the blade intersects the traditional single circular arc linear midline of the blade in an X-shape;

[0031] Figure 6 for Figure 5 A magnified view of a portion of the image;

[0032] Figure 7 for Figure 1 A partial top view, in which the free curve midline of the blade and the traditional single circular arc linear midline of the blade are distributed in an approximately Y-shaped intersection;

[0033] Figure 8 for Figure 7 A magnified view of a portion of the image;

[0034] Figure 9 for Figure 1 Top view;

[0035] Figure 10 for Figure 9 Perspective view;

[0036] Figure 11 for Figure 1 Main perspective view;

[0037] Figure 12 for Figure 11 Enlarged view of point B in the image;

[0038] Figure 13 for Figure 1 A bottom view;

[0039] Figure 14 This is a schematic diagram of the ventilation equipment provided in an embodiment of this application.

[0040] Explanation of reference numerals in the attached figures:

[0041] 100. First sawtooth segment; 110. First sawtooth;

[0042] 200. Second sawtooth segment; 210. Second sawtooth;

[0043] 300. Third sawtooth segment; 310. Third sawtooth;

[0044] 400. Freeform curve;

[0045] 10. Blade; 11. Leading edge; 12. Trailing edge; 20. Wheel cover; 21. Curved section; 22. Straight section; 30. Chassis; 40. Hub;

[0046] 1. Impeller; 2. Housing; 3. Motor;

[0047] Z, first direction; M, single circular arc; O, intersection point. Detailed Implementation

[0048] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0049] The following disclosure provides numerous different embodiments or examples for implementing various structures of this application. To simplify the disclosure, specific examples of components and arrangements are described below. These are merely examples and are not intended to limit the scope of this application. Furthermore, reference numerals and / or letters may be repeated in different examples. Such repetition is for simplification and clarity and does not in itself indicate a relationship between the various embodiments and / or arrangements discussed. In addition, various specific examples of processes and materials are provided in this application; however, those skilled in the art will recognize the applicability of other processes and / or the use of other materials.

[0050] For ease of description, spatial relative terms may be used in the text to describe the relative position or movement of one element or feature relative to another element or feature, as shown in the figure. These relative terms include, for example, "inside," "outside," "middle," "outer," "below," "below," "above," "front," "back," etc. Such spatial relative terms are intended to include different orientations of the device in use or operation, other than those depicted in the figure. For example, if the device in the figure undergoes a positional flip, orientation change, or change of motion, these directional indications will change accordingly. For instance, an element described as "below other elements or features" or "below other elements or features" will subsequently be oriented "above other elements or features" or "above other elements or features." Therefore, the example term "below" can include both upper and lower orientations. The device may be otherwise oriented (rotated 90 degrees or in other directions), and the spatial relative descriptors used in the text will be interpreted accordingly.

[0051] See Figures 1 to 10This application provides a blade 10 having a top surface and a bottom surface disposed opposite to each other. The trailing edge 12 of the blade 10 is provided with a first serrated segment 100, a second serrated segment 200 and a third serrated segment 300 sequentially arranged along a first direction Z from the bottom surface to the top surface. The size of the first serrated tooth 110 of the first serrated segment 100 is larger than the size of the second serrated tooth 210 of the second serrated segment 200, and the size of the second serrated tooth 210 of the second serrated segment 200 is larger than the size of the third serrated tooth 310 of the third serrated segment 300.

[0052] In this embodiment, the trailing edge 12 of the blade 10 is composed of at least three different tooth profiles to functionally partition the trailing edge 12 of the blade 10, thereby reducing torque, power consumption, noise generation, and increasing airflow. Specifically, the first serration 110 on the first serrated section 100 has the largest size, which reduces the chord length of the blade 10, thus achieving a rapid decrease in blade torque and power consumption, achieving the goal of low torque and low power consumption; the third serration 310 on the third serrated section 300 has the smallest size, which introduces disturbance at the trailing edge 12 of the blade 10, causing the laminar boundary layer on the surface of the blade 10 to transition to the turbulent boundary layer earlier, effectively reducing the wake loss of the airflow, and the blade The large vortex of airflow at the outlet end of blade 10 breaks into smaller vortices and detaches, thus disrupting the consistency of vortex volume along the span. This can increase airflow while suppressing noise increase, achieving the goal of large airflow and low noise. The second serrated section 200 is positioned between the first serrated section 100 and the third serrated section 300, with the second serration 210 on it being centered. The medium-sized serrations enable stable airflow between different functional zones at the trailing edge 12 of blade 10, improving the operational stability of the trailing edge 12 of blade 10.

[0053] It should be explained that the top surface of blade 10 is the side facing the impeller cover 20 after blade 10 is installed in impeller 1, and this top surface extends radially along impeller 1, with airflow flowing into impeller 1 from the top surface of blade 10; the bottom surface of blade 10 is the side facing the chassis 30 after blade 10 is installed in impeller 1, and this bottom surface extends radially along impeller 1, with the top and bottom surfaces of blade 10 spaced apart along the axial direction of impeller 1. The trailing edge 12 of blade 10 is the side away from hub 40 after blade 10 is installed in impeller 1, and this trailing edge 12 extends axially along impeller 1, with airflow exiting from the trailing edge 12 of blade 10.

[0054] In one example, a plurality of first serrations 110 are provided on the first serrated segment 100, and the plurality of first serrations 110 are spaced apart along the first direction Z; a plurality of second serrations 210 are provided on the second serrated segment 200, and the plurality of second serrations 210 are spaced apart along the first direction Z; a plurality of third serrations 310 are provided on the third serrated segment 300, and the plurality of third serrations 310 are spaced apart along the first direction Z. In this way, by providing multiple serrations on different serrated segments, torque can be further reduced, power consumption can be reduced, air volume can be increased, noise can be reduced, and the operational stability of the blade 10 can be improved, at least in terms of quantity.

[0055] In one possible implementation, in the first direction Z, the total height of the blade 10 is h, the height of the first serrated segment 100 is h1, and the height of the second serrated segment 200 is h2, wherein the range of h1:h is 0.15 to 0.25, and the range of (h2+h1):h is 0.3 to 0.5. This configuration allows the blade 10 to simultaneously reduce torque and power consumption while increasing airflow and suppressing noise generation.

[0056] like Figure 3 As shown, the total height of blade 10 in the first direction Z is h, the height of the first serrated segment 100 in the first direction Z is h1, the height of the second serrated segment 200 in the first direction Z is h2, and the height of the third serrated segment 300 in the first direction Z is (h-h1-h2). When the ratio of the height difference between the first serrated segment 100 and blade 10 is close to 0.15, the number of first serrated segments 100 is relatively small. In this case, the airflow sacrificed near the bottom surface of blade 10 is small, the torque reduction obtained by blade 10 is smaller, and the power consumption is larger. When the ratio of the height difference between the first serrated segment 100 and blade 10 is close to 0.25, the number of first serrated segments 100 is relatively large. In this case, the airflow sacrificed near the bottom surface of blade 10 is larger, the torque reduction obtained by blade 10 is larger, and the power consumption is lower. In practical applications, a balance can be struck between the amount of airflow sacrificed by blade 10 and the magnitude of torque reduction / power consumption. For example, but not limited to, h1:h = 0.21.

[0057] When the ratio of the sum of the heights of the first serrated section 100 and the second serrated section 200 to the height difference of the blade 10 is close to 0.3, the arrangement of the third serrated section 300 is relatively large. In this case, the space reserved for the first serrated section 100 and the second serrated section 200 is relatively small, resulting in poor stability at the trailing edge 12 of the blade 10. The blade 10 has a larger airflow disturbance area near the top surface, which increases the airflow of the blade 10 and improves noise suppression performance. When the ratio of the sum of the heights of the first serrated section 100 and the second serrated section 200 to the height difference of the blade 10 is close to 0.5, the arrangement of the third serrated section 300 is relatively small. In this case, the space reserved for the first serrated section 100 and the second serrated section 200 is relatively large, resulting in higher stability and lower torque of the blade 10. However, the blade 10 has a smaller airflow disturbance area near the top surface, limiting the increase in airflow and noise suppression performance. In practical applications, a balance can be struck between blade stability / low torque and airflow / noise suppression performance. For example, but not limited to...

[0058] (h1+h2): h=0.42.

[0059] In one possible implementation, the first serration 110 has a height of d1 and a tooth depth of L1, where L1:d1 ranges from 0.6 to 0.8; and / or, the second serration 210 has a height of d2 and a tooth depth of L2, where L2:d2 ranges from 1.1 to 1.5; and / or, the third serration 310 has a height of d3 and a tooth depth of L3, where L3:d3 ranges from 0.5 to 0.7. This arrangement allows for a reasonable distribution of serration density across different serration segments, enabling multiple functional areas of the trailing edge 12 of the blade 10 to work in tandem.

[0060] like Figure 4As shown, the distance between the opening of the first serration 110 and the farthest point along the direction from the leading edge 11 to the trailing edge 12 of the blade 10 is the tooth depth L1 of the first serration 110, and the opening size of the first serration 110 in the extending direction of the trailing edge 12 of the blade 10 is the tooth height d1 of the first serration 110. When the ratio between the tooth depth L1 and the tooth height d1 of the first serration 110 is 0.6, the degree of concavity of the first serration 110 is small, the first serration 110 is relatively flat, the density of the first serrations 110 distributed on the first serration segment 100 is small, and the blade 10 is easy to process; the blade 10 loses less chord length at the first serration 110, the torque reduction obtained by the blade 10 at the first serration segment 100 is small, and the power consumption is large. When the ratio of the tooth depth L1 to the tooth height d1 of the first serration 110 is 0.8, the first serration 110 has a greater degree of concavity, is steeper, and has a higher density of teeth on the first serration segment 100, making the blade 10 more difficult to manufacture. The blade 10 loses more chord length at the first serration 110, resulting in a greater reduction in torque and lower power consumption at the first serration segment 100. In practical applications, a balance can be struck between the ease of manufacturing the blade 10 and the magnitude of the torque reduction / power consumption. For example, but not limited to, L1:d1 = 0.724.

[0061] The distance between the opening of the second serration 210 and the farthest point along the direction from the leading edge 11 to the trailing edge 12 of the blade 10 is the tooth depth L2 of the second serration 210, and the opening size of the second serration 210 in the extending direction of the trailing edge 12 of the blade 10 is the tooth height d2 of the second serration 210. When the ratio between the tooth depth L2 and the tooth height d2 of the second serration 210 is 1.1, the density of the second serrations 210 distributed on the second serration segment 200 is relatively small, and the stability of the blade 10 is good; the torque reduction obtained by the blade 10 at the second serration segment 200 is small, and the power consumption is large. When the ratio between the tooth depth L2 and the tooth height d2 of the second serration 210 is 1.5, the density of the second serrations 210 distributed on the second serration segment 200 is relatively large, and the stability of the blade 10 is poor; the torque reduction obtained by the blade 10 at the second serration segment 200 is large, and the power consumption is small. In practical applications, a balance can be struck between the stability of the blade 10 and the magnitude of torque reduction / power consumption. For example, but not limited to, L2:d2 = 1.3. It is preferable that 2 to 4 second serrations 210 can be arranged on the second serrated section 200, for example, 3 second serrations 210 can be arranged on the second serrated section 200.

[0062] The distance between the opening of the third serration 310 and the farthest point along the direction from the leading edge 11 to the trailing edge 12 of the blade 10 is the tooth depth L3 of the third serration 310. The opening size of the third serration 310 in the extension direction of the trailing edge 12 of the blade 10 is the tooth height d3 of the third serration 310. When the ratio between the tooth depth L3 and the tooth height d3 of the third serration 310 is 0.5, the density of the third serrations 310 distributed on the third serration 310 is relatively small, which is convenient for processing; the blade 10 provides less interference in the third serration section 300, the obtained air volume is small, and the noise is large. When the ratio between the tooth depth L3 and the tooth height d3 of the third serration 310 is 0.7, the density of the third serrations 310 distributed on the third serration 310 is relatively large, which is more difficult to process; the blade 10 provides more interference in the third serration section 300, the obtained air volume is large, and the noise is small. In practical applications, a balance can be struck between the ease of manufacturing the blades and the airflow / noise levels. For example, but not limited to, L3:

[0063] d3 = 0.595. It is preferable that 8 to 12 third serrations 310 can be arranged on the third serration segment 300, for example, 10 third serrations 310 can be arranged on the third serration segment 300.

[0064] In one possible implementation, the midline of the two-dimensional airfoil of the blade 10 is a free curve 400, and the free curve 400 intersects the conventional single circular arc line M of the blade in an X-shape or Y-shape. This arrangement significantly reduces the operating speed of the ventilation equipment and increases the outlet angle on the trailing edge 12 side of the blade 10, thereby increasing the air volume of the ventilation equipment.

[0065] It should be noted that the single arc line M is the single arc mid-shape line of the traditional blade 10. When the single arc mid-shape line adopts a large placement angle design, the curvature of the line decreases rapidly, the flow of the blade 10 surface becomes worse, and the power of the blade 10 increases rapidly while increasing the air volume, which is difficult to control.

[0066] Based on this, this application proposes a blade 10 with a medium-sized free curve 400. The free curve 400 of this blade 10 intersects with the conventional single circular arc M in an X-shape or Y-shape. For example... Figures 5 to 8 As shown, Figure 5 and Figure 6 The middle section shows the case where the free curve 400 intersects the traditional single circular arc M in an X-shape. Figure 7 and Figure 8The free-form curve 400 intersects the traditional single circular arc M in a Y-shape. The two-dimensional airfoil of this blade 10 adopts the free-form curve 400 midline, ensuring good contact and airflow guidance between the blade 10's front half near the leading edge 11 and the airflow. Simultaneously, the exit angle of the blade 10 gradually increases in the rear half after the intersection, enhancing its work capacity and significantly suppressing the substantial deterioration of its power while increasing airflow, thus achieving the maximum airflow increase rate at the same power. It should be noted that the leading edge 11 of the blade 10 refers to the side of the blade 10 facing the hub 40 after it is installed in the impeller 1, and this leading edge 11 extends along the axial direction of the impeller 1. Airflow flows from the leading edge 11 of the blade 10 towards its trailing edge 12.

[0067] In one possible implementation, in the direction from the leading edge 11 to the trailing edge 12 of the blade 10, the angle between the line connecting the starting point of the free curve 400 and the center point of the impeller 1 and the line connecting the ending point of the free curve 400 and the center point of the impeller 1 is γ. The angle between the line connecting the starting point of the free curve 400 and the center point of the impeller 1 and the line connecting the intersection point O of the free curve 400 and the conventional single circular arc M and the center point of the impeller 1 is γ1, where γ1:γ ranges from 0.6 to 0.85. This configuration optimizes the aerodynamic efficiency and flow characteristics of the blade 10, while significantly reducing the operating speed of the ventilation equipment and increasing the outlet angle of the blade 10.

[0068] like Figures 5 to 8 As shown, the angle between the starting point of the free curve 400 and its intersection with the traditional single circular arc M is γ1, and the angle between the starting points of the free curve 400 is γ. When the ratio of the angle between the starting point of the free curve 400 and its intersection with the traditional single circular arc M is γ1 to the angle between the starting points of the free curve 400 and γ is 0.6, the free curve 400 and the traditional single circular arc M form an X-shaped intersection layout. The intersection point between the free curve 400 and the traditional single circular arc M is closer to the middle section of the blade 10. The area in the latter half of the blade 10 profile near the trailing edge 12 that increases the outlet angle of the blade 10 is larger, resulting in a larger increase in air volume. When the ratio of the angle γ1 between the starting point of the free curve 400 and its intersection with the conventional single circular arc M to the angle γ between the starting point of the free curve 400 and the conventional single circular arc M is 0.85, the free curve 400 and the conventional single circular arc M form a Y-shaped intersection layout. The intersection point between the free curve 400 and the conventional single circular arc M is closer to the trailing edge 12 of the blade 10. The area in the latter half of the blade profile where the blade 10's exit angle is increased is smaller, resulting in a smaller increase in airflow. In practical applications, a balance can be struck between the blade 10's exit angle area and the airflow volume. For example, but not limited to, γ1:γ = 0.75.

[0069] In one possible implementation, the ratio of γ1:γ gradually decreases along the first direction Z. This setting can further increase the exit angle at the trailing edge 12 of the blade 10, increase the airflow, and curb the deterioration of the blade 10's power.

[0070] In one possible implementation, multiple blades 10 are provided, and the multiple blades 10 are arranged non-equidistantly in the circumferential direction of the impeller 1, wherein the distribution pattern of the multiple blades 10 satisfies the sinusoidal modulation theory. This arrangement can effectively improve the peak noise of the blades 10 and reduce the bounce of the total noise value and power consumption data.

[0071] like Figure 9 and Figure 10 As shown, the sinusoidal modulation theory is φ1=φ+A*sin(Nφ), where the modulation cycle number N=2, the modulation amplitude A=0.09, φ1 is the angle of the non-equidistant blades 10, and φ is the angle of the equidistant blades 10. For example, in one example, there are 7 blades 10, and the interval angles between the 7 blades 10 are 56.5°, 44.2°, 49.6°, 59.5°, 49.6°, 44.2°, and 56.5°, respectively. The air intake and noise of the ventilation equipment composed of the above-mentioned 7-blade 10 layout and the ordinary equidistant 7-blade 10 ventilation equipment were tested, and the structures are shown in Table 1.

[0072] Table 1 Experimental test results

[0073]

[0074]

[0075] It is evident that arranging multiple blades at non-equidistant intervals can effectively improve the peak noise of ventilation equipment and is less likely to cause a rebound in the total noise level and power consumption data.

[0076] In one possible implementation, the trailing edge 12 of the blade 10 is gradually widened in the first direction Z.

[0077] In this embodiment, by tilting the trailing edge 12 of the blade 10 and making it expand in a trumpet shape along the first direction Z, the chord length of the blade 10 near the impeller 1 chassis 30 is reduced, while the chord length of the blade 10 near the impeller 1 cover 20 is increased. Since more airflow from the blade 10 exits from the side near the impeller 1 chassis 30 and less from the side near the impeller 1 cover 20, improving the chord length of the blade 10 in the radial direction effectively improves the uniformity and smoothness of the outflow from the blade 10 in the first direction Z, reduces the airflow pressure difference of the blade 10 in the first direction Z, and reduces the noise generated by the blade 10. At the same time, compared with the blade 10 with a constant aspect ratio design, the blade 10 with a variable chord length can effectively reduce the torque of the impeller 1, reduce the power loss of the impeller 1, improve the aerodynamic performance of the impeller 1, and improve the user experience and satisfaction.

[0078] In addition, the trailing edge 12 of the blade 10 near the bottom surface is provided with a large first serration 110, which further reduces the chord length of the trailing edge 12 of the blade 10 near the bottom surface, further reduces the torque of the blade 10, further reduces the power consumption of the blade 10, and further enhances the aerodynamic performance of the blade 10.

[0079] Secondly, this application also provides an impeller 1, comprising: a hub 40; a chassis 30 disposed on the outer periphery of the hub 40; a wheel cover 20 disposed concentrically opposite to the chassis 30; and blades 10 as described above, disposed between the chassis 30 and the wheel cover 20, with the top surface of the blades 10 facing the wheel cover 20. Thus, by configuring blades 10 with a trailing edge 12 composed of at least three different tooth profiles on the impeller 1, the torque experienced by the impeller 1 during operation is reduced, the power consumption of the impeller 1 is reduced, the noise generated by the impeller 1 during operation is reduced, and the airflow of the impeller 1 is increased.

[0080] In one possible implementation, the wheel cover 20 includes an axially connected arcuate portion 21 and a straight portion 22, with the arcuate portion 21 facing the chassis 30 and the straight portion 22 tangent to the arcuate portion 21 at its connection point. This segmented design of the wheel cover 20 enhances the impeller 1's guidance of airflow, thereby reducing losses caused by significant downstream airflow deflections, increasing airflow volume, reducing power consumption, and decreasing noise.

[0081] Compared to conventional fan blades without a flow-guiding structure at the end of the traditional wheel cover 20 profile, the airflow exiting the fan blades encounters a 90° airflow deflection channel after passing through the heat exchanger. This creates a matching problem between the fan blade outlet angle and the downstream airflow deflection channel. Based on this, this application proposes a flow profile design where the wheel cover 20 consists of a straight section and a conical arc section. Specifically, an upward-curving straight section for flow guidance is added to the end of the arc-shaped portion 21 of the wheel cover 20. Figure 11 and Figure 12As shown. In this way, the airflow direction can be guided inside the fan blades, reducing losses caused by large deflections of downstream airflow, increasing air volume, reducing power consumption, and improving noise.

[0082] In one possible implementation, in the first direction Z, the height of the wheel cover 20 is SH1, and the height of the straight portion 22 is SH2, wherein the ratio of SH2 to SH1 is 0.08 to 0.4; and / or, the curvature of the arcuate portion 21 is 0.15 to 0.35; and / or, the angle of the end of the arcuate portion 21 away from the straight portion 22 is α, satisfying the condition: 45° ≤ α ≤ 60°. This configuration simultaneously achieves both the airflow guiding performance of the wheel cover 20 and the increase in the airflow of the impeller 1.

[0083] like Figure 12 As shown, the total height of the impeller cover 20 in the first direction Z is SH1, the height of the straight section 22 in the first direction Z is SH2, and the total height of the arc-shaped section 21 in the first direction Z is (SH1-SH2). When the ratio of the height of the straight section 22 SH2 to the height of the impeller cover 20 SH1 is 0.08, the guiding length of the straight section 22 is small, the radial clearance between the straight section 22 and the blade 10 is large, and the volumetric loss increases. When the ratio of the height of the straight section 22 SH2 to the height of the impeller cover 20 SH1 is 0.4, the guiding length of the straight section 22 is large, the layout space of the arc-shaped section 21 is small, the guiding characteristics of the impeller cover 20 deteriorate, and the airflow loss also increases. In practical use, a better comprehensive value can be selected between the guiding performance and volumetric loss of the impeller 1. For example, but not limited to, SH2:SH1 = 0.256.

[0084] When the curvature of the arc-shaped section 21 is 0.15, the degree of curvature of the arc-shaped section 21 is relatively small, the guiding effect of the impeller cover 20 on the impeller airflow is relatively weak, and the downstream airflow loss is relatively large. When the curvature of the arc-shaped section 21 is 0.35, the degree of curvature of the arc-shaped section 21 is relatively large, and the impeller cover 20 compresses more blade area, which is not conducive to the work-capable function of the blade 10. In practical use, the airflow guiding characteristics of the impeller cover 20 should be balanced with minimizing the encroachment on the blade 10 area. For example, but not limited to, the curvature rho of the arc-shaped section 21 is 0.25.

[0085] When the angle α between the profile of the end of the curved section 21 furthest from the straight section 22 and the vertical direction is 45°, it indicates that the concavity of the curved section 21 is relatively large, resulting in better airflow guidance characteristics at the outlet, but the blade 10 occupies a larger area. When the angle α between the profile of the end of the curved section 21 furthest from the straight section 22 and the vertical direction is 60°, it indicates that the concavity of the curved section 21 is relatively small, resulting in relatively poor airflow guidance characteristics at the outlet, but the blade 10 occupies a smaller area. For example, but not limited to, α = 53°.

[0086] In one possible implementation, the diameter of the chassis 30 is D1 in the radial direction of the impeller 1, and the diameter of the wheel cover 20 is D2, wherein the ratio of D2 to D1 is between 1.02 and 1.1. This arrangement limits the tilt amplitude of the trailing edge 12 of the blade 10, ensuring it is at a suitable tilt angle, guaranteeing airflow uniformity in the first direction Z of the trailing edge 12 of the blade 10, improving the aerodynamic performance of the blade 10, and suppressing noise generation.

[0087] like Figure 2 and Figure 13 As shown, the diameter of the chassis 30 in the radial direction of the impeller 1 is D1, and the diameter of the wheel cover 20 in the radial direction of the impeller 1 is D2, wherein the diameters of the wheel cover 20 and the chassis 30 are different. When the ratio of the diameter of the wheel cover 20 to the diameter of the chassis 30 is 1.02, the size of the wheel cover 20 is almost the same as that of the chassis 30, the spanwise work capacity modulation performance of the blade 10 is weak, the trailing edge 12 of the blade 10 is relatively steep, the tilt angle of the trailing edge 12 of the blade 10 relative to the axis of the impeller 1 is small, the chord length of the blade 10 does not change much, the torque reduction of the blade 10 is small, the power consumption is large, and the noise is large. When the ratio of the diameter of the wheel cover 20 to the diameter of the chassis 30 is 1.1, the size difference between the wheel cover 20 and the chassis 30 is significant, resulting in strong work-energy modulation performance of the blades 10 in the spanwise direction. The trailing edge 12 of the blades 10 is relatively flat, with a large tilt angle relative to the axis of the impeller 1, leading to a large variation in the chord length of the blades 10, a significant reduction in torque, lower power consumption, and lower noise. In practical applications, a balance can be struck between the work-energy modulation performance of the impeller 1 in the spanwise direction and the reduction in torque / power consumption / noise level. For example, but not limited to, D2:D1 = 1.043.

[0088] like Figure 14 As shown, in a third aspect, this application also provides a ventilation device, characterized in that it includes a housing 2, an impeller 1 as described above, and a motor 3. The impeller 1 is rotatably disposed within the housing 2, and the motor 3 is disposed at the rotation center shaft of the hub 40 of the impeller 1. By driving the motor 3 to rotate, the impeller 1 is driven to rotate. The purpose of the impeller 1 is to allow airflow to pass through a heat exchanger, thereby enabling the airflow to exchange heat with the refrigerant in the heat exchanger, thus achieving a cooling or heating effect. The specific structure of the impeller 1 is as described in the above embodiments. Since this ventilation device adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be elaborated here. For example, but not limited to, this ventilation device can be an air conditioner, which can be applied to an embedded ceiling fan.

[0089] It should be understood that the terminology used herein is for the purpose of describing particular exemplary embodiments only and is not intended to be limiting. Unless the context clearly indicates otherwise, the singular forms “a,” “an,” and “described” as used herein may also include the plural forms. The terms “comprising,” “including,” “containing,” and “having” are inclusive and therefore indicate the presence of the stated features, steps, operations, elements, and / or components, but do not exclude the presence or addition of one or more other features, steps, operations, elements, components, and / or combinations thereof. The method steps, processes, and operations described herein are not construed as requiring them to be performed in a particular order described or illustrated unless the order of performance is explicitly indicated. It should also be understood that additional or alternative steps may be used.

[0090] Although terms such as first, second, third, etc., may be used in this document to describe multiple elements, components, regions, layers, and / or segments, these elements, components, regions, layers, and / or segments should not be limited by these terms. These terms may be used only to distinguish one element, component, region, layer, or segment from another. Unless the context clearly indicates otherwise, terms such as "first," "second," and other numerical terms used herein do not imply order or sequence. Therefore, the first element, component, region, layer, or segment discussed below may be referred to as the second element, component, region, layer, or segment without departing from the teachings of the exemplary embodiments.

[0091] The above description is merely a specific embodiment of this application, enabling those skilled in the art to understand or implement this application. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of this application. Therefore, this application is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features claimed herein.

Claims

1. A vane, characterized in that The blade has a top surface and a bottom surface arranged opposite to each other. The trailing edge of the blade is provided with a first serrated segment, a second serrated segment and a third serrated segment in sequence along a first direction from the bottom surface to the top surface. The size of the first serrated tooth of the first serrated segment is larger than the size of the second serrated tooth of the second serrated segment, and the size of the second serrated tooth of the second serrated segment is larger than the size of the third serrated tooth of the third serrated segment. In the first direction, the total height of the blade is h, the height of the first serrated segment is h1, and the height of the second serrated segment is h2, wherein the range of h1:h is 0.15~0.25, and the range of (h2+h1):h is 0.3~0.

5.

2. The blade of claim 1, wherein The height of the first saw tooth is d1, and the tooth depth of the first saw tooth is L1, wherein L1:d1 ranges from 0.6 to 0.8; and / or, The height of the second saw tooth is d2, and the tooth depth of the second saw tooth is L2, wherein L2:d2 ranges from 1.1 to 1.5; and / or, The height of the third saw tooth is d3, and the tooth depth of the third saw tooth is L3, wherein the range of L3:d3 is 0.5~0.

7.

3. The blade of claim 1, wherein The midline of the two-dimensional airfoil of the blade is a free curve, and the free curve intersects the single circular arc in an X-shape or Y-shape.

4. The blade according to claim 3, characterized in that, In the direction from the leading edge to the trailing edge of the blade, the angle between the line connecting the starting point of the free curve and the center point of the impeller and the line connecting the ending point of the free curve and the center point of the impeller is γ, and the angle between the line connecting the starting point of the free curve and the center point of the impeller and the line connecting the intersection of the free curve and the single circular arc and the center point of the impeller is γ1, wherein γ1:γ ranges from 0.6 to 0.

85.

5. The blade according to claim 4, characterized in that, The ratio of γ1 to γ ​​gradually decreases along the first direction.

6. The blade according to claim 1, characterized in that, The blades are provided in multiples, and the multiple blades are arranged non-equidistantly in the circumferential direction of the impeller, wherein the distribution pattern of the multiple blades satisfies the sinusoidal modulation theory.

7. The blade according to claim 1, characterized in that, In the first direction, the trailing edge of the blade is gradually widened.

8. An impeller, characterized in that, include: Wheel hub; The chassis is located on the outer periphery of the wheel hub; Wheel covers are concentrically positioned opposite to the chassis. as well as The blade as described in any one of claims 1 to 7 is disposed between the chassis and the wheel cover, with the top surface of the blade facing the wheel cover.

9. The impeller according to claim 8, characterized in that, The wheel cover includes an axially connected arc-shaped portion and a straight portion, the arc-shaped portion being disposed towards the chassis, and the connection between the straight portion and the arc-shaped portion being tangent.

10. The impeller according to claim 9, characterized in that, In the first direction, the height of the wheel cover is SH1, and the height of the straight portion is SH2, wherein the ratio of SH2 to SH1 is 0.08 to 0.4; and / or, The curvature of the arc-shaped portion is 0.15~0.35; and / or, The angle of the end of the arc-shaped portion away from the straight portion is α, and it satisfies the following condition: 45°≤α≤60°.

11. The impeller according to claim 8, characterized in that, In the radial direction of the impeller, the diameter of the chassis is D1, and the diameter of the wheel cover is D2, wherein the ratio of D2 to D1 is 1.02 to 1.

1.

12. A ventilation device, characterized in that, It includes a housing, an impeller as described in any one of claims 8 to 11, and a motor, wherein the impeller is rotatably disposed within the housing, and the motor is disposed at the rotational center axis of the impeller hub.

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