Impeller and air outlet equipment

Abstract

The invention provides an impeller and air outlet equipment, and belongs to the technical field of household appliances. The impeller comprises a supporting plate, a plurality of first blades and a plurality of second blades. The multiple first blades and the multiple second blades are fixed to the supporting plate, the multiple first blades are arranged in the circumferential direction of the supporting plate, and at least one second blade is arranged between every two adjacent first blades. The length of the second blade is smaller than that of the first blade, and the distance between the head end of the first blade and the central axis of the impeller is smaller than that between the head end of the second blade and the central axis. A first air channel and a second air channel are formed between the first blade and the second blades on the two sides respectively, and the head end of the first air channel or the second air channel is wider than the tail end of the first air channel or the second air channel. Generation of vortexes can be restrained, airflow can flow out of the impeller as much as possible, and the air speed when the airflow flows out can be increased. In this way, the air outlet efficiency of the impeller can be high.

Description

Technical Field

[0001] This application relates to the field of home appliance technology, and in particular to an impeller and an air outlet device. Background Technology

[0002] The impeller is the core component of air supply equipment (such as bathroom heaters, fresh air systems, and air conditioners). The impeller draws air in from the air inlet, accelerates the airflow, and directs it to the air outlet, thus enabling the air supply equipment to blow air. The impeller consists of a support plate and multiple blades. The blades are arranged circumferentially and fixed to the support plate. When the impeller rotates, it draws air into the spaces between the blades and allows it to flow out along the blades.

[0003] However, the impellers in related technologies have low air output efficiency, so how to improve the air output efficiency of the impellers is a key problem that needs to be solved. Summary of the Invention

[0004] This application provides an impeller and an air outlet device, which can solve the technical problems existing in related technologies. The technical solution of the impeller and air outlet device is as follows.

[0005] In the first aspect, this application provides an impeller and an air outlet device that can solve the technical problems existing in the related art. The technical solution of the impeller and the air outlet device is as follows.

[0006] This application provides an impeller, which includes a support plate, a plurality of first blades, and a plurality of second blades; The plurality of first blades and the plurality of second blades are fixed to the support plate. The plurality of first blades are arranged circumferentially along the support plate. There is at least one second blade between two adjacent first blades. The length of the second blade is less than the length of the first blade. The distance between the tip of the first blade and the central axis of the impeller is less than the distance between the tip of the second blade and the central axis. A first air duct and a second air duct are formed between the first blade and the second blades on both sides, respectively, and the width of the first air duct or the second air duct at the beginning is greater than the width of the end.

[0007] In one possible implementation, the width of the first air duct or the second air duct gradually decreases along the direction from the tip to the tail of the first blade.

[0008] In one possible implementation, both the first blade and the second blade are arc-shaped, with the first air duct formed between the concave surface of the first blade and the convex surface of the second blade, and the second air duct formed between the convex surface of the first blade and the concave surface of the other second blade. Along the direction from the tip of the first blade to the tail, the width of the first air duct gradually decreases.

[0009] In one possible implementation, let the width of the tail end of the first air duct be L1 and the width of the tail end of the second air duct be L2, then 0.45 < L1 / L2 < 0.6.

[0010] In one possible implementation, on a plane perpendicular to the central axis, let the line connecting the tail end of the first blade to the central axis be the first line, the reference line perpendicular to the first line and passing through the tail end of the first blade be the first reference line, the line connecting the tail end of the second blade to the central axis be the second line, and the reference line perpendicular to the second line and passing through the tail end of the second blade be the second reference line. The angle between the tangent at the tail end of the first blade and the first reference line is α1, and the angle between the tangent at the tail end of the second blade and the second reference line is α2, then α1 > α2.

[0011] In one possible implementation, the width of the first air duct at the head end is equal to the width of the second air duct at the head end.

[0012] In one possible implementation, on a plane perpendicular to the central axis, the line connecting the tip of the first blade and the central axis is designated as the third line, a reference line perpendicular to the third line and passing through the tip of the first blade is designated as the third reference line, the line connecting the tip of the second blade and the central axis is designated as the fourth line, and a reference line perpendicular to the fourth line and passing through the tip of the second blade is designated as the fourth reference line. Let γ1 be the angle between the tangent at the tip of the first blade and the third reference line, and γ2 be the angle between the tangent at the tip of the second blade and the fourth reference line. Then 75° < γ1 < 85°, 75° < γ2 < 85°.

[0013] In one possible implementation, γ1 = γ2.

[0014] In one possible implementation, on a plane perpendicular to the central axis, let the arc length of the first blade be f1 and the arc length of the second blade be f2, then 12mm < f1 < 15mm, 0.551 <f2 / f1<0.65。

[0015] In one possible implementation, the end of the second blade away from the support plate has an inclined surface, and the distance between the inclined surface and the support plate gradually increases along the direction from the first end to the last end of the second blade.

[0016] In one possible implementation, let ρ be the angle between the inclined plane and the plane perpendicular to the central axis, then 55° < ρ < 65°.

[0017] In one possible implementation, let the length of the tip of the second blade along the central axis be H1, and the length of the tip of the first blade along the central axis be H2, then 45mm

[0018] In one possible implementation, let D1 be the distance between the tip of the first blade and the central axis, and D2 be the distance between the end of the inclined surface away from the central axis and the central axis. Then 70mm <D1<75mm,78mm<D2<82mm。

[0019] In one possible implementation, the end of the second blade away from the support plate also has an arc surface and a straight surface, the arc surface being located between the inclined surface and the straight surface; The distance between the flat surface and the support plate is greater than the distance between the inclined surface and the support plate, and the arc surface protrudes in a direction away from the support plate.

[0020] Secondly, this application provides an air outlet device, which includes an impeller as described in any of the first aspects.

[0021] The technical solution provided in this application includes at least the following beneficial effects: This application provides an impeller in which, because the distances from the leading ends of the first and second blades to the central axis are different, airflow will not simultaneously flow through the leading ends of the first and second blades. This reduces noise generated by the airflow and suppresses impeller vibration and vortex generation. Furthermore, because the width of the leading end of the first or second air duct is greater than the width of the trailing end, the airflow is compressed as it flows through the first or second air duct. This ensures that the airflow always flows along the sidewalls of the first and second blades, preventing premature separation of the airflow from the sidewalls of the first and second blades, thereby suppressing vortex generation and allowing as much airflow as possible to exit from the first and second air ducts, which is beneficial for increasing the impeller's air volume. Moreover, because the airflow is compressed as it flows through the first or second air duct, the air pressure is increased, thereby increasing the airflow velocity. This results in higher impeller discharge efficiency.

[0022] It should be understood that the above general description and the following detailed description are exemplary and explanatory only, and do not limit this application. Attached Figure Description

[0023] ​The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application. In the drawings: Figure 1 This is a schematic diagram of the structure of an impeller shown in an embodiment of this application; Figure 2 This is a top view of an impeller shown in an embodiment of this application; Figure 3 This is a top view of an impeller shown in an embodiment of this application; Figure 4 This is a top view of an impeller shown in an embodiment of this application; Figure 5 This is a cross-sectional view of an impeller shown in an embodiment of this application; Figure 6 This is a partially enlarged view of an impeller shown in an embodiment of this application; Figure 7 This is a schematic diagram showing a comparison of wind speed between an impeller in this application and impellers in related technologies; Figure 8 This is a schematic diagram of an impeller structure shown in related technologies.

[0024] Legend: 1. Support plate 2. First blade; 201. First air duct; 202. Second air duct; 3. Second blade, 3a. inclined surface, 3b. curved surface, 3c. straight surface; 4. Fixing ring.

[0025] The accompanying drawings illustrate specific embodiments of this application, which will be described in more detail below. These drawings and descriptions are not intended to limit the scope of the concept in any way, but rather to illustrate the concept of this application to those skilled in the art through reference to particular embodiments. Detailed Implementation

[0026] To make the objectives, technical solutions, and advantages of this application clearer, the embodiments of this application will be described in further detail below with reference to the accompanying drawings.

[0027] The terminology used in the embodiments section of this application is for illustrative purposes only and is not intended to limit the application. Unless otherwise defined, the technical or scientific terms used herein should be understood in their ordinary sense by one of ordinary skill in the art to which this application pertains. The terms "first," "second," "third," and similar words used in the patent application specification and claims do not indicate any order, quantity, or importance, but are merely used to distinguish different components. Similarly, "an" or "a" and similar words do not indicate a quantity limitation, but rather indicate the presence of at least one. The terms "comprising" or "including" and similar words mean that the element or object preceding "comprising" or "including" encompasses the element or object listed following "comprising" or "including" and its equivalents, and do not exclude other elements or objects. The terms "connected" or "linked" and similar words are not limited to physical or mechanical connections, but can include electrical connections, whether direct or indirect. "Above," "below," "left," "right," etc., are used only to indicate relative positional relationships; when the absolute position of the described object changes, the relative positional relationship may also change accordingly.

[0028] The impeller is a core component of air supply equipment (such as bathroom heaters, fresh air systems, and air conditioners), used to deliver air to the air outlet of the equipment. In related technologies, the impeller includes a support plate and multiple blades. The blades are arranged circumferentially and fixed to the support plate. When the impeller rotates, it draws air into the spaces between the blades and allows it to flow out along the blades. All blades are identical in size and shape, and the width between any two adjacent blades is the same.

[0029] However, when the impeller is running, the internal airflow is simultaneously subjected to the Coriolis force generated by rotation, fluid viscosity, and adverse pressure gradient, thus generating eddies and easily causing boundary layer separation on the blade surface and within the air duct. Boundary layer separation refers to the detachment of the boundary layer that was originally flowing closely to the surface of an object from the surface. For example, when airflow flows along a blade, the airflow detaches from the blade surface. Furthermore, the evenly spaced blades in the impeller cause the velocity and pressure fields within the air duct to exhibit obvious circumferential pulsation characteristics, resulting in uneven airflow at the outlet, affecting the flow organization of the downstream air duct, and reducing the overall airflow utilization rate. Specifically, since all blades are of the same length, the air duct formed by adjacent blades has a uniform or approximately uniform cross-section in both the axial and circumferential directions. When the airflow develops from the tip to the tail of the blade, the local velocity increases slowly, failing to fully utilize the energy conversion potential under the centrifugal force field, resulting in some wasted kinetic energy. Ultimately, this manifests as insufficient overall airflow or the need to compensate by increasing the rotational speed, indirectly increasing energy consumption and noise.

[0030] Furthermore, due to the perfectly symmetrical geometry and arrangement of the impeller blades, the flow state within each duct is highly consistent, and the airflow separates synchronously at the blade trailing edges, forming regularly arranged vortices. These highly coherent vortices are periodically released circumferentially at the impeller outlet, causing significant pressure pulsations. This not only exacerbates mid-to-high frequency aerodynamic noise but also disrupts the airflow organization in the downstream ducts, affecting the overall air delivery uniformity and system matching performance. In addition, because the inlet angle of attack at the blade tip is constant circumferentially, while the actual incoming flow exhibits boundary layer thickness differences, excessively large positive or negative angles of attack occur at some duct inlets, easily leading to localized flow separation. This separation zone further develops into secondary flow and angular vortices, increasing flow losses and reducing the impeller's effective work capacity.

[0031] In view of the above-mentioned technical problems, embodiments of this application provide an impeller, such as... Figure 1 and Figure 2 As shown, the impeller includes a support plate 1, multiple first blades 2, and multiple second blades 3. The first blades 2 and second blades 3 are fixed to the support plate 1. The multiple first blades 2 are arranged sequentially along the circumference of the support plate 1, and at least one second blade 3 is located between any two adjacent first blades 2. The length of the second blade 3 is less than the length of the first blade 2, and the distance between the tip of the first blade 2 and the central axis A of the support plate 1 is less than the distance between the tip of the second blade 3 and the central axis A. Because the tips of the first blades 2 and 3 are at different distances from the central axis A, the airflow will not simultaneously flow through the tips of the first blades 2 and 3, thereby reducing noise generated by the airflow and suppressing impeller vibration and vortex generation.

[0032] Furthermore, a first air duct 201 and a second air duct 202 are formed between the first blade 2 and the second blades 3 on both sides, respectively, and the width of the first air duct 201 or the second air duct 202 at the beginning is greater than the width at the end.

[0033] The impeller is a multi-bladed centrifugal impeller. During operation, airflow enters the impeller along the axial direction of the support plate 1 and then flows out radially from the support plate 1. The leading end of each blade is the end closest to the central axis A, and the trailing end is the end furthest from the central axis A. The length of each blade is the distance between the leading and trailing ends. The width of the first air duct 201 at a certain point is the distance between the intersection of a circle centered on the central axis A and passing through that point, and the intersection of the first blade 2 and the second blade 3. Similarly, the width of the second air duct 202 at a certain point is the distance between the intersection of a circle centered on the central axis A and passing through that point, and the intersection of the first blade 2 and the second blade 3. For example, as... Figure 2As shown, the distance between points A1 and B1 is the width of the beginning of the first air duct 201, and the distance between points B1 and C1 is the width of the beginning of the second air duct 202. The distance between points A2 and B2 is the width of the end of the first air duct 201, and the distance between points B2 and C2 is the width of the end of the second air duct 202.

[0034] In some examples, the impeller also includes a retaining ring 4 located at the end of the first blade 2 away from the support plate 1 and opposite to the support plate 1. Multiple first blades 2 and multiple second blades 3 are fixed to the inner side of the retaining ring 4. This enhances the stability of the first blades 2 and second blades 3, preventing wobbling at the ends of the first blades 2 and second blades 3 away from the support plate 1 when the impeller rotates.

[0035] The technical solution provided in this application embodiment, because the width of the first end of the first air duct 201 or the second air duct 202 is greater than the width of the tail end, the airflow is compressed when flowing in the first air duct 201 or the second air duct 202. This allows the airflow to always flow along the sidewalls of the first blade 2 and the second blade 3, preventing the airflow from separating prematurely from the sidewalls of the first blade 2 and the second blade 3, thereby suppressing the generation of vortices and allowing as much airflow as possible to be discharged from the first air duct 201 and the second air duct 202, which is beneficial to increasing the impeller's air volume. Furthermore, because the airflow is compressed when flowing in the first air duct 201 or the second air duct 202, the air pressure of the airflow can be increased, thereby increasing the airflow velocity. In this way, the impeller's air outlet efficiency is higher.

[0036] In some examples, the width of the first air duct 201 or the second air duct 202 gradually decreases along the direction from the leading end to the trailing end of the first blade 2. This allows the airflow to be gradually compressed within the first air duct 201 or the second air duct 202, avoiding abrupt changes in the airflow area and helping to reduce noise and eddy current generation.

[0037] The following is an exemplary description of the specific implementation methods of the first blade 2 and the second blade 3.

[0038] In some examples, such as Figure 2 As shown, both the first blade 2 and the second blade 3 are arc-shaped. A first air duct 201 is formed between the concave surface of the first blade 2 and the convex surface of the second blade 3, and a second air duct 202 is formed between the convex surface of the first blade 2 and the concave surface of the second blade 3. It can be understood that when the impeller rotates ( Figure 2 (The bold arrows in the text indicate the direction of impeller rotation during operation.) The concave surfaces of the first blade 2 and the second blade 3 are the windward sides, while the convex surfaces of the first blade 2 and the second blade 3 are the leeward sides. Because the length of the first blade 2 is greater than the length of the second pressure plate 3, the windward side of the first blade 2 can guide more airflow.

[0039] The width of the first air duct 201 gradually decreases along the direction from the leading end to the trailing end of the first blade 2. For example... Figure 2 As shown, the distance between A3 and B3 is smaller than the distance between A1 and B1, and the distance between A2 and B3 is smaller than the distance between A3 and B3. This allows the airflow velocity in the first duct 201 to gradually increase. That is, the airflow in the duct containing the windward side of the first blade 2 gradually accelerates. This facilitates the acceleration of more airflow in more impellers, thereby improving impeller efficiency.

[0040] In some examples, such as Figure 2 As shown, let the width of the tail end of the first air duct 201 be L1 and the width of the tail end of the second air duct 202 be L2, then 0.45 < L1 / L2 < 0.6. By setting L1 and L2 differently, the periodicity of the airflow field in the impeller is broken, which helps to weaken the formation of vortices, thereby increasing the air volume of the impeller and improving its air outlet efficiency. Furthermore, it also allows the pulse amplitude and frequency generated when the airflow exits through the first air duct 201 and the second air duct 202 to be different, which helps to reduce the noise generated during impeller operation. Therefore, by setting L1 and L2 differently, aerodynamic performance and acoustic characteristics can be further optimized.

[0041] Furthermore, setting 0.45 < L2 / L1 < 0.6 can prevent the tail end of the first air duct 201 from being too narrow and the tail end of the second air duct 202 from being too wide. If the tail end of the first air duct 201 is too narrow, the airflow velocity in the first air duct 201 will be too high, resulting in greater frictional losses and a smaller air volume at the tail end of the first air duct 201. If the tail end of the second air duct 202 is too wide, vortices will easily form at the tail end of the second air duct 202.

[0042] In related technologies, the tail ends of multiple blades of an impeller are parallel, causing the airflow to exit at the same angle from the tail ends of different blades. This results in significant noise and vibration in the impeller. Therefore, in the impeller provided in this application, the airflow directions are different when it exits from the first blade 2 and the second blade 3.

[0043] Specifically, in some examples, such as Figure 3As shown, on a plane perpendicular to the central axis A, the line connecting the tail end of the first blade 2 to the central axis A is the first line b1, and the reference line perpendicular to the first line b1 and passing through the tail end of the first blade 2 is the first reference line c1. The line connecting the tail end of the second blade 3 to the central axis A is the second line b2, and the reference line perpendicular to the second line b2 and passing through the tail end of the second blade 3 is the second reference line c2. The angle between the tangent a1 at the tail end of the first blade 2 and the first reference line c1 is α1, and the angle between the tangent a2 at the tail end of the second blade 3 and the second reference line c2 is α2. Therefore, α1 > α2.

[0044] Simulation experiments show that the impeller has a better air output effect when 160° < α1 < 165° and 155° < α2 < 163°.

[0045] In some examples, the width of the first air duct 201 at its inlet is equal to the width of the second air duct 202 at its inlet. This ensures that the air intake of the first air duct 201 and the second air duct 202 is approximately the same, which helps to maintain the dynamic balance of the impeller and makes the impeller less prone to noise and vibration.

[0046] In some examples, such as Figure 3 As shown, on a plane perpendicular to axis A, let the line connecting the tip of the first blade 2 and the central axis A be the third line m1, and the reference line perpendicular to the third line m1 and passing through the tip of the first blade 2 be the third reference line n1. Let the line connecting the tip of the second blade 3 and the central axis A be the fourth line m2, and the reference line perpendicular to the fourth line m2 and passing through the tip of the second blade 3 be the fourth reference line n2. Let the angle between the tangent d1 at the tip of the first blade 2 and the third reference line n1 be γ1, and the angle between the tangent d1 at the tip of the second blade 3 and the fourth reference line n2 be γ2. Then, 75° < γ1 < 85°, 75° < γ2 < 85°. Simulation experiments show that when 75° < γ1 < 85° and 75° < γ2 < 85°, the impeller's airflow performance is better. If γ1 and γ2 are too large, the airflow will have a greater impact on the windward surfaces of the first blade 2 and the second blade 3, thus easily generating significant noise. If γ1 and γ2 are too small, the airflow is prone to flow separation at the windward surfaces of the first blade 2 and the second blade 3, resulting in low impeller output efficiency.

[0047] In some examples, γ1 = γ2. This ensures that the airflow inlet angles at the tips of the first blade 2 and the second blade 3 are approximately the same. This helps to make the impeller run more smoothly and reduces noise and vibration.

[0048] For example, γ1=γ2=75°.

[0049] In some examples, such as Figure 4As shown, on a plane perpendicular to the central axis A, let the arc radius of the first blade 2 be R1 and the arc radius of the second blade 2 be R2, then R1 > R2.

[0050] Exemplarily, 9 mm < R1 < 9.5 mm, 5 mm < R2 < 5.5 mm. If R1 and R2 are too large, the side walls of the first blade 2 and the second blade 3 will be close to straight, making the air flow unable to smoothly transition between the first blade 2 and the second blade 3, and prone to air flow loss. If R1 and R2 are too small, vortices are likely to occur in the air flow between the first blade 2 and the second blade 3.

[0051] In some examples, as Figure 3 shown, on a plane perpendicular to the central axis A, let the angle between the line connecting the leading end of the first blade 2 and the central axis A and the line connecting the trailing end of the second blade 3 and the central axis A be β, that is, the angle between the third line m1 and the fourth line m1 is β, then 5° < β < 8°, so that the air outlet efficiency of the impeller is relatively high.

[0052] If β is too small, it means that the distance between the first blade 2 and the second blade 3 is too close, resulting in the first air duct 201 and the second air duct 202 being too narrow. When the air flow passes through the first air duct 201 and the second air duct 202, large frictional losses will occur, reducing the air outlet efficiency of the impeller and prone to generating relatively large noise.

[0053] If β is too large, it means that the distance between the first blade 2 and the second blade 3 is too far, resulting in the first air duct 201 and the second air duct 202 being too wide. When the air flow passes through the first air duct 201 and the second air duct 202, vortices are likely to occur, resulting in a relatively low air outlet efficiency of the impeller.

[0054] Exemplarily, β = 5.625°.

[0055] In some examples, the windward side and the leeward side of the first blade 2 are parallel, and the thickness of the first blade 2 is about 1.2 mm. The windward side and the leeward side of the second blade 3 are parallel, and the thickness of the second blade 3 is about 1.2 mm. In this way, the thickness of the first blade 2 and the second blade 3 can be relatively uniform, having good structural strength.

[0056] In some examples, the first blade 2 has rounded corners at both its leading and trailing ends on a plane perpendicular to the central axis A, with a radius of approximately 0.5 mm. The rounded corner at the leading end of the first blade 2 provides a gentler guiding effect for the airflow, allowing it to adhere to the surface of the first blade 2 and reducing the likelihood of flow separation. It also reduces the impact of the airflow on the leading end of the first blade 2, thereby reducing noise. The rounded corner at the trailing end of the first blade 2 reduces the generation of vortices, which is beneficial for improving the impeller's exhaust efficiency. Furthermore, this allows for a larger contact area between the airflow entering and exiting the first blade 2, enabling more thorough acceleration and pressurization on the surface of the first blade 2, which helps to suppress flow separation and thus reduces noise and vibration.

[0057] Similarly, in some examples, on a plane perpendicular to the central axis A, the first and last ends of the second blade 3 have rounded corners, and the radius of the rounded corners is approximately 0.5 mm.

[0058] In some examples, the impeller includes 32 first blades 2 and 32 second blades 3, with one second blade 3 between every two adjacent first blades 2.

[0059] As mentioned above, the impeller provided in this application is a centrifugal impeller. When the impeller is working, a portion of the airflow enters the first air duct 201 and the second air duct 202 along the axial direction of the support plate 1, and then flows out along the radial direction of the support plate 1. Therefore, the airflow efficiency of the impeller can be improved by increasing the amount of airflow entering the impeller along the axial direction.

[0060] In some examples, such as Figure 5 and Figure 6 As shown ( Figure 6 for Figure 5 (Partial enlarged view) The end of the second blade 3 away from the support plate 1 has an inclined surface 3a. Along the direction from the first end to the last end of the second blade 3, the distance between the inclined surface 3a and the support plate 1 gradually increases. In this way, the inclined surface 3a of the second blade 3 can reduce the obstruction of the air intake between two adjacent first blades 2, thereby increasing the air intake volume between two adjacent first blades 2.

[0061] The first end of the inclined plane 3a is the first end of the second blade 3, that is, the inclined plane 3a starts to tilt from the first end of the second blade 3.

[0062] In some examples, such as Figure 6As shown in the figure, let the angle between the inclined plane 3a and the plane perpendicular to the central axis A be ρ, then 55° < ρ < 65°. If ρ is too small, the second blade 3 will block the incoming air between two adjacent first blades 2, which is not conducive to increasing the air intake between the two first blades 2. If ρ is too large, the length of the leading end of the second blade 3 along the direction of the central axis A will be too small, making it difficult to effectively guide the air flow at the leading end of the second blade 3.

[0063] Exemplarily, ρ = 60°.

[0064] In some examples, such as Figure 5 As shown in the figure, let the length of the leading end of the second blade 3 along the direction of the central axis A be H1, and the length of the leading end of the first blade 2 along the direction of the central axis A be H2, then 45mm < H1 < 55mm, 60mm < H2 < 65mm. Here, the lengths of the leading ends of the first blade 2 and the second blade 3 are restricted by the overall height of the impeller, so the lengths of H1 and H2 cannot be too large.

[0065] In some examples, such as Figure 4 As shown in the figure, let the distance between the leading end of the first blade 2 and the central axis A be D1. As Figure 5 As shown in the figure, the distance between the end of the second guiding section 42 close to the central axis A and the central axis A is D2, then 70mm < D1 < 75mm, 78mm < D2 < 82mm. If D1 and D2 are too small, the flow path of the air flow on the first blade 2 and the second blade 3 will be too small, resulting in a too short acceleration path for the air flow, making it easy for the air flow to generate flow separation and eddies on the surfaces of the first blade 2 and the second blade 3, thus reducing the air outlet efficiency. If D1 and D2 are too large, the frictional loss generated by the air flow on the surfaces of the first blade 2 and the second blade 3 will be large, reducing the air outlet efficiency of the impeller.

[0066] In some examples, such as Figure 3 As shown in the figure, let the distance between the trailing end of the first blade 2 and the central axis A be D3, and the distance between the trailing end of the second blade 3 and the central axis A be D4, then 0.85 < D1 / D3 < 0.95, 0.8 < D2 / D4 < 0.9. If D1 / D3 and D2 / D4 are too small, the lengths of the first blade 2 and the second blade 3 will be too long. If D1 / D3 and D2 / D4 are too large, the lengths of the first blade 2 and the second blade 3 will be too short. As analyzed above, if the lengths of the first blade 2 and the second blade 3 are too short or too long, the air outlet efficiency of the impeller will be reduced.

[0067] Exemplarily, D1 / D3 = 0.9, D2 / D4 = 0.85.

[0068] In some examples, such as Figure 6As shown, the end of the second blade 3 away from the support plate 1 also has a cambered surface 3b and a flat surface 3c, and the cambered surface 3b is located between the inclined surface 3a and the flat surface 3c. The distance between the flat surface 3c and the support plate 1 is greater than the distance between the inclined surface 3a and the support plate 1, and the cambered surface 3b protrudes in the direction away from the support plate 1. In this way, a smooth transition can be achieved between the inclined surface 3a and the flat surface 3c, which is beneficial to reducing the noise generated by the air flow at the end of the second blade 3 away from the support plate 1.

[0069] Exemplarily, as Figure 5 shown, let the radius of the cambered surface 3b be R3, then 1.5mm < R3 < 2.5mm. For example, R3 = 2mm.

[0070] In some examples, as Figure 4 shown, in a plane perpendicular to the central axis A, let the arc length of the first blade 2 be f1 and the arc length of the second blade 3 be f2, then 12mm < f1 < 15mm, and 0.55 < f2 / f1 < 0.65. If f1 is too small, the flow path of the air flow on the first blade 2 will be too small, resulting in a too short acceleration path of the air flow, making it easy for the air flow to generate flow separation and eddy currents on the surface of the first blade 2, thus reducing the air outlet efficiency of the air flow. If f1 is too large, the frictional loss generated by the air flow on the surface of the first blade 2 will be large, thus reducing the air outlet efficiency of the impeller. Exemplarily, f1 = 14mm.

[0071] If f2 / f1 is too large, the arc lengths of the first blade 2 and the second blade 3 will be relatively close, making it easy for the air flow to flow through the leading ends of the first blade 2 and the second blade 3 simultaneously, which is not conducive to reducing the noise of the impeller. If f2 / f1 is too small, the arc length of the second blade 3 will be too short, resulting in a too short acceleration path of the air flow, making it easy for the air flow to generate flow separation and eddy currents on the surface of the second blade 3, thus reducing the air outlet efficiency of the air flow.

[0072] In some examples, as Figure 3 shown, the trailing ends of the plurality of first blades 2 and the trailing ends of the plurality of second blades 3 are located on the same circumference, so as to ensure the consistency of the overall starting shape of the impeller and the adaptability of the assembly.

[0073] Exemplarily, as Figure 4 shown, let the diameter of the circumference where the trailing ends of the plurality of first blades 2 and the trailing ends of the plurality of second blades 3 are located be φ, then 165mm < φ < 173mm. It can be understood that φ is affected by the overall circumferential dimension of the impeller, so it cannot be too small or too large.

[0074] In some examples, the impeller may further include a third blade. The impeller includes multiple groups of blades arranged uniformly in the circumferential direction, and each group of blades includes a first blade 2, a second blade 3, and a third blade. The first blade 2, the second blade 3, and the third blade in each group of blades can be arranged in various ways. For example, the first blade 2, the second blade 3, and the third blade are arranged in sequence in the circumferential direction, or the first blade 2, the third blade, and the second blade 3 are arranged in sequence in the circumferential direction, etc. The embodiments of the present application do not make specific limitations in this regard.

[0075] The present application has carried out simulation and comparison on the impeller in the present application, the impellers in related technologies, and the impellers in related technologies. The simulation data is shown in Table 1, Table 2, and Figure 7 as shown.

[0076] Among them, the impeller in the present application has 32 first blades 2 and 32 second blades 3, and simultaneously satisfies 0.45 < L1 / L2 < 0.6, 160° < α1 < 165°, 155° < α2 < 163°, γ1 = γ2 = 75°, 9mm < R1 < 9.5mm, 5mm < R2 < 5.5mm, β = 5.625°, the thicknesses of both the first blade 2 and the second blade 3 are 1.2mm, ρ = 60°, 45mm < H1 < 55mm, 60mm < H2 < 65mm, 70mm < D1 < 75mm, 78mm < D2 < 82mm, D1 / D3 = 0.9, D2 / D4 = 0.85, R3 = 2mm, f1 = 14mm, 0.55 < f2 / f1 < 0.65, 65mm < φ < 173mm. As Figure 8 shown, the impeller in the related technology has a wheel disc 100, main blades 200, and auxiliary blades 300. Multiple main blades 200 are fixed to the wheel disc 100 and are evenly distributed in the circumferential direction. Multiple auxiliary blades 300 are fixed to the wheel disc 100 and are evenly distributed in the circumferential direction. Multiple main blades 200 surround the auxiliary blades 300, that is, multiple auxiliary blades 300 are located inside multiple main blades 200. Let the height of the main blade 200 along the axial direction of the wheel disc 100 be H3, and the height of the auxiliary blade 300 along the axial direction of the wheel disc 100 be H4, and H4 = 0.1H3. Let the distance between the leading end of the main blade 200 and the axis of the wheel disc 100 be r1, and the distance between the leading end of the auxiliary blade 300 and the axis of the wheel disc 100 be r2, and r2 / r1 = 0.05 - 0.5.

[0077] As shown in Table 1, at the same rotational speed, the air volume, relative speed, and maximum wind speed of the impeller in the present application are all improved compared to those of the impeller in the related technology.

[0078] Table 1

[0079] As shown in Table 2 and Figure 7As shown, the wind speed of the impeller in this application and the impeller in related technologies were compared at different times. From Table 2 and... Figure 7 As can be seen, the impeller operates for 1-5 seconds during its startup phase, during which the wind speed gradually increases. After 5 seconds, the impeller enters a stable phase, where the wind speed remains relatively constant. During both the startup and stable phases, the wind speed of the impeller in this application is greater than that of impellers in related technologies.

[0080] Table 2

[0081] Therefore, based on the above analysis, it can be concluded that the impeller provided in this application has a large air outlet efficiency.

[0082] This application also provides an air outlet device, which includes the impeller as described above.

[0083] The air outlet equipment can be a bathroom heater, a fresh air system, or an indoor unit of an air conditioner. The air outlet equipment has an air inlet and an air outlet. When the impeller is working, it can draw in air through the air inlet and then expel the airflow through the air outlet.

[0084] The above description is merely an optional embodiment of this application and is not intended to limit this application. Any modifications, equivalent substitutions, improvements, etc., made within the principles of this application should be included within the protection scope of this application.

Claims

1. An impeller, characterized in that, The impeller includes a support plate (1), a plurality of first blades (2) and a plurality of second blades (3); The plurality of first blades (2) and the plurality of second blades (3) are fixed to the support plate (1). The plurality of first blades (2) are arranged circumferentially along the support plate (1). There is at least one second blade (3) between two adjacent first blades (2). The length of the second blade (3) is less than the length of the first blade (2). The distance between the tip of the first blade (2) and the central axis (A) of the impeller is less than the distance between the tip of the second blade (3) and the central axis (A). A first air duct (201) and a second air duct (202) are formed between the first blade (2) and the second blades (3) on both sides, respectively. The width of the first air duct (201) or the second air duct (202) at the beginning is greater than the width at the end.

2. The impeller according to claim 1, characterized in that, Along the direction from the first end to the tail end of the first blade (2), the width of the first air duct (201) or the second air duct (202) gradually decreases.

3. The impeller according to claim 2, characterized in that, Both the first blade (2) and the second blade (3) are arc-shaped. The first air duct (201) is formed between the concave surface of the first blade (2) and the convex surface of the second blade (3), and the second air duct (202) is formed between the convex surface of the first blade (2) and the concave surface of the other second blade (3). Along the direction from the first end of the first blade (2) to the tail end, the width of the first air duct (201) gradually decreases.

4. The impeller according to any one of claims 1-3, characterized in that, wherein... The width of the tail end of the first air duct (201) is L1, and the width of the tail end of the second air duct (202) is L2, then 0.45 < L1 / L2 < 0.

6.

5. The impeller according to claim 1, characterized in that, On a plane perpendicular to the central axis (A), let the line connecting the tail end of the first blade (2) and the central axis (A) be the first connecting line (b1), the reference line perpendicular to the first connecting line (b1) and passing through the tail end of the first blade (2) be the first reference line (c1), the line connecting the tail end of the second blade (3) and the central axis (A) be the second connecting line (b2), and the reference line perpendicular to the second connecting line (b2) and passing through the tail end of the second blade (3) be the second reference line (c2). Let α1 be the angle between the tangent (a1) at the tail end of the first blade (2) and the first reference line (c1), and α2 be the angle between the tangent (a2) at the tail end of the second blade (3) and the second reference line (c2). Then α1 > α2.

6. The impeller according to claim 1, characterized in that, The width of the first air duct (201) at the head end is equal to the width of the second air duct (202) at the head end.

7. The impeller according to claim 1, characterized in that, On a plane perpendicular to the central axis (A), let the line connecting the first end of the first blade (2) and the central axis (A) be the third line (m1), the reference line perpendicular to the third line (m1) and passing through the first end of the first blade (2) be the third reference line (n1), the line connecting the first end of the second blade (3) and the central axis (A) be the fourth line (m2), and the reference line perpendicular to the fourth line (m2) and passing through the first end of the second blade (3) be the fourth reference line (n2). Let γ1 be the angle between the tangent (d1) at the beginning of the first blade (2) and the third reference line (n1), and γ2 be the angle between the tangent (d1) at the beginning of the second blade (3) and the fourth reference line (n2). Then 75°<γ1<85°, 75°<γ2<85°.

8. The impeller according to claim 7, characterized in that, γ1=γ2.

9. The impeller according to any one of claims 1-3, characterized in that, The second blade (3) has an inclined surface (3a) at one end away from the support plate (1). The distance between the inclined surface (3a) and the support plate (1) gradually increases along the direction from the head end to the tail end of the second blade (3).

10. The impeller according to claim 9, characterized in that, it is provided that... If the angle between the inclined plane (3a) and the plane perpendicular to the central axis (A) is ρ, then 55° < ρ < 65°.

11. The impeller according to claim 9, characterized in that, Let H1 be the length of the first end of the second blade (3) along the central axis (A), and H2 be the length of the first end of the first blade (2) along the central axis (A). Then 45mm <H1<55mm,60mm<H2<65mm。 12. The impeller according to claim 9, characterized in that, Let D1 be the distance between the tip of the first blade (2) and the central axis (A), and D2 be the distance between a point on the inclined plane (3a) away from the support plate (1) and the central axis (A). Then 70mm <D1<75mm,78mm<D2<82mm。 13. The impeller according to claim 9, characterized in that, The second blade (3) also has an arc surface (3b) and a straight surface (3c) at the end away from the support plate (1), the arc surface (3b) being located between the inclined surface (3a) and the straight surface (3c); The distance between the flat surface (3c) and the support plate (1) is greater than the distance between the inclined surface (3a) and the support plate (1), and the arc surface (3b) protrudes in a direction away from the support plate (1).

14. An air outlet device, characterized in that, The air outlet device includes an impeller as described in any one of claims 1-13.

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