A sawtooth blade and axial flow fan for window machine using the same

Abstract

The present invention relates to the technical field of axial flow wind wheels, and in particular to a sawtooth blade and an axial flow wind wheel for a window machine using the same, wherein the sawtooth blade comprises a blade body and a guide portion protruding and connected to the outside of the blade body; the blade body is a sheet-like structure, and the peripheral contour of the blade body is formed by a blade root edge, a blade leading edge, a blade outer edge, and a blade trailing edge, wherein the blade root edge, the blade leading edge, the blade outer edge, and the blade trailing edge are all curved, and the connection points between the blade root edge, the blade leading edge, the blade outer edge, and the blade trailing edge are the front blade root, the front blade tip, the rear blade tip, and the rear blade root, respectively; the blade trailing edge is concavely provided with a plurality of saw teeth, and the width and height of the plurality of saw teeth are unequal; the blade outer edge is protruding and provided with a guide portion, and the width of the guide portion gradually increases. The present invention can solve the technical problem that the existing blades have airflow turbulence during use, which not only reduces the energy conversion efficiency but also generates relatively large noise.

Description

Technical Field

[0001] The present invention relates to the technical field of axial flow wind wheels, and in particular to a sawtooth blade and an axial flow wind wheel for a window machine using the sawtooth blade. Background Art

[0002] In equipment such as fans and air conditioners, blades are core components, and their structural design directly affects the performance of the equipment. Traditional blades have many problems during operation. On the one hand, vortices are easily generated at the trailing edge of the blade, causing turbulent airflow, which not only reduces energy conversion efficiency but also generates a lot of noise, affecting the user experience and the equipment usage environment. On the other hand, the airflow guidance effect at the outer edge of the blade is not good, resulting in an unsmooth air flow, unable to fully utilize the aerodynamic performance of the blade, and limiting the improvement of the overall performance of the equipment. As people's requirements for equipment performance continue to increase, there is an urgent need to optimize the design of the blade structure to solve the above problems and improve the overall performance of the equipment. Summary of the Invention

[0003] One of the purposes of the present invention is to propose a sawtooth blade, which solves the technical problem that the existing blades have turbulent airflow during use, which not only reduces the energy conversion efficiency but also generates a lot of noise, by optimizing the design of the blade shape.

[0004] One purpose of the present invention is to provide an axial flow impeller for a window machine, which uses the above-mentioned sawtooth blades to improve the overall performance of the equipment.

[0005] To achieve this object, the present invention adopts the following technical solutions:

[0006] A sawtooth blade comprises a blade body and a flow guide portion protruding and connected to the outer side of the blade body;

[0007] The blade body is a sheet-like structure, and the peripheral contour of the blade body is formed by the blade root edge, the blade leading edge, the blade outer edge and the blade trailing edge. The blade root edge, the blade leading edge, the blade outer edge and the blade trailing edge are all arranged in a curved shape, and the connection points between the blade root edge, the blade leading edge, the blade outer edge and the blade trailing edge are the front blade root, the front blade tip, the rear blade tip and the rear blade root respectively.

[0008] Define two points on the trailing edge of the blade as design point X and design point Y, wherein the design point X is located close to the rear blade root and the design point Y is located close to the rear blade tip. Define the edge between the design point X and the design point Y as a serrated edge, wherein the serrated edge is concavely provided with a plurality of serrations, and the width of the plurality of serrations is W. i and height H i The values ​​from the design point X to the design point Y are not equal;

[0009] Define a point on the outer edge of the blade as the design point Z, define the edge between the design point Z and the rear blade tip as the guide portion arrangement edge, the guide portion arrangement edge protrudes to set the guide portion, and the width of the guide portion is W 导流部 It gradually increases from the design point Z to the rear blade tip.

[0010] Preferably, the length of the curve of the trailing edge of the blade is defined as L 叶尾缘 , define the curve length of the zigzag arrangement edge as L 锯齿 , define the length of the curve from the design point X to the rear blade root as L1, define the length of the curve from the design point Y to the rear blade root as L2,

[0011] Among them, L 锯齿 ≤1 / 2L 叶尾缘 , L1≥2 / 5L 叶尾缘 , L2≤9 / 10L 叶尾缘 .

[0012] Preferably, the arrangement order of the plurality of saw teeth is defined to start from the design point X and end at the design point Y;

[0013] The width W of the plurality of saw teeth i Satisfy in the order described:

[0014] W i =A1sin(ω1N i -φ1)-A2sin(ω2N i -φ2)+DN i +E;

[0015] Among them, W i is the width of the i-th sawtooth, in mm;

[0016] N i is the i-th sawtooth;

[0017] A1 and A2 are amplitudes, 1<A1, A2<1.3, unit is mm;

[0018] ω1 and ω2 are frequencies, 0.5<ω1, ω2<2, in Hz;

[0019] φ1 and φ2 are initial phases, 0.1<φ1, φ2<0.7, unit is rad;

[0020] D is the coefficient of the first-order term, 0.1<D<0.5;

[0021] E is the translation amount, 9<E<10, unit is mm.

[0022] Preferably, the arrangement order of the plurality of saw teeth is defined to start from the design point X and end at the design point Y;

[0023] The height H of the plurality of saw teeth i Satisfy in the order described:

[0024] H i =A3N i 3 -B3N i 2 +C3N i +D3;

[0025] Among them, H i is the length of the i-th sawtooth, in mm;

[0026] N i is the i-th sawtooth;

[0027] A3 is the third phase coefficient, 0.05<A3<0.1;

[0028] B3 is the secondary phase coefficient, 0.5<B3<0.8;

[0029] C3 is the primary phase coefficient, 0.7<C3<1;

[0030] D3 is a constant, 2.5< D3<3.

[0031] Preferably, the guide portion is formed by enclosing a first guide edge, a second guide edge, a third guide edge and a fourth guide edge, and the first guide edge, the second guide edge, the third guide edge and the fourth guide edge are all arranged in a curved shape;

[0032] The curvature of the first guide edge is the same as that of the outer edge of the blade, and the first guide edge is overlapped and connected with the edge of the guide portion;

[0033] The fourth guide edge is arranged to overlap with an extension line of the blade trailing edge;

[0034] The included angle between the second guide edge and the outer edge of the blade is defined as γ;

[0035] Among them, 100°≤γ≤130°.

[0036] Preferably, the length of the curve defining the outer edge of the leaf is L 叶外缘 , define the curved length of the edge of the guide portion as L3;

[0037] Among them, 2 / 5L 叶外缘 ≤L3≤5 / 10L 叶外缘 .

[0038] An axial flow impeller for a window air conditioner, comprising a hub, a water ring, a connector and sawtooth blades, wherein the sawtooth blades are the sawtooth blades described above;

[0039] The plurality of sawtooth blades are spaced apart and distributed along the circumferential direction of the hub, and the root edges of the plurality of sawtooth blades are fixedly connected to the outer periphery of the hub;

[0040] The water pumping ring is coaxially arranged with the wheel hub, and the connecting members are respectively fixedly connected between the water pumping ring and the guide parts of the plurality of sawtooth blades. The connection direction of the connecting members is parallel to the axial direction of the water pumping ring, and the outer edges of the plurality of sawtooth blades are arranged obliquely with respect to the water pumping ring;

[0041] Define that the angle between the outer edge of the serrated blade and the water circle in axial plane projection is β;

[0042] Where β=30°.

[0043] Preferably, the length of the curve from the connection point between the connecting member and the guide portion to the fourth guide edge of the guide portion is defined as L4;

[0044] Among them, 12mm≤L4≤30mm.

[0045] Preferably, there is a radial gap between the water pumping ring and the third guide edge of the guide portion, and the radial gap distance between the water pumping ring and the third guide edge of the guide portion is defined as L5;

[0046] Among them, 6mm≤L5≤9mm.

[0047] Preferably, the edge from the front blade tip to the design point Z is defined as the airflow edge;

[0048] The length of the curve of the airflow edge is defined as L6;

[0049] The radial length between the airflow edge and the rotation axis of the hub is defined as L7;

[0050] Among them, L7≤(AL6 3 +BL6 2 +CL6+D) / 2, the unit of L6 and L7 is mm;

[0051] A is the cubic phase coefficient, -3E-05<A<-1E-05;

[0052] B is the secondary phase coefficient, 0.005<B<0.007;

[0053] C is the primary phase coefficient, -1.3<C<-1;

[0054] D is a constant, 418<D<420.

[0055] One of the above technical solutions has the following beneficial effects:

[0056] 1. In terms of noise reduction, the unevenly arranged multiple saw teeth disrupt the airflow shedding frequency, avoid the generation of concentrated noise, effectively reduce the operating noise of the equipment, and create a quiet environment for users.

[0057] 2. In terms of efficiency improvement, the air guide reduces airflow turbulence and optimizes airflow trajectory, reduces air flow resistance, improves energy conversion efficiency, enables the equipment to achieve stronger air delivery capacity under the same energy consumption, and improves work efficiency.

[0058] 3. In terms of service life, the smooth and orderly airflow reduces the impact and wear on the blades, extends the service life of the blades and even the entire equipment, and reduces maintenance costs. BRIEF DESCRIPTION OF THE DRAWINGS

[0059] Figure 1 It is a structural schematic diagram of a sawtooth blade of the present invention;

[0060] Figure 2 This is a schematic diagram of the design of the trailing edge of a sawtooth blade in the present invention;

[0061] Figure 3 This is a schematic diagram of the design of the outer edge of a sawtooth blade in the present invention;

[0062] Figure 4 This is a schematic structural diagram of an axial flow impeller for a window air conditioner using the above-mentioned sawtooth blades according to the present invention;

[0063] Figure 5 This is a schematic radial projection diagram of an axial flow impeller for a window air conditioner using the above-mentioned sawtooth blades according to the present invention;

[0064] Figure 6 This is a schematic axial projection diagram of an axial flow impeller for a window air conditioner using the above-mentioned sawtooth blades according to the present invention;

[0065] Figure 7 yes Figure 5 A local enlarged view of point a in the middle;

[0066] Figure 8 The airflow distribution diagram of the axial flow impeller for the window air conditioner using the above-mentioned serrated blades and the non-serrated blades;

[0067] In the accompanying drawings: blade root edge 1, blade leading edge 2, blade outer edge 3, blade trailing edge 4, front blade root 5, front blade tip 6, rear blade tip 7, rear blade root 8, serrations 9, guide part 10, first guide edge 101, second guide edge 102, third guide edge 103, fourth guide edge 104, hub 100, water ring 200, connecting part 300, serrated blade 400. DETAILED DESCRIPTION

[0068] The technical solution of the present invention will be further described below with reference to the accompanying drawings and through specific implementation methods.

[0069] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "axial", "radial", "circumferential" and the like to indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0070] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of the technical features being referred to. Thus, a feature specified as "first" or "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, unless otherwise specified, "plurality" means two or more.

[0071] In the description of the present invention, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood broadly. For example, they may refer to fixed connections, detachable connections, or integral connections; they may refer to direct connections, indirect connections through an intermediary, or internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on the specific circumstances.

[0072] A sawtooth blade comprises a blade body and a guide portion 10 protruding and connected to the outer side of the blade body;

[0073] The blade body is a sheet-like structure, and the peripheral contour of the blade body is formed by a blade root edge 1, a blade leading edge 2, a blade outer edge 3, and a blade trailing edge 4. The blade root edge 1, the blade leading edge 2, the blade outer edge 3, and the blade trailing edge 4 are all arranged in a curved shape. The connection points between the blade root edge 1, the blade leading edge 2, the blade outer edge 3, and the blade trailing edge 4 are the front blade root 5, the front blade tip 6, the rear blade tip 7, and the rear blade root 8, respectively.

[0074] Define two points on the trailing edge 4 as design point X and design point Y, wherein the design point X is located close to the rear blade root 8 and the design point Y is located close to the rear blade tip 7. Define the edge between the design point X and the design point Y as a serrated edge, wherein the serrated edge is concavely provided with a plurality of serrations 9, and the width W of the plurality of serrations 9 is i and height H iThe values ​​from the design point X to the design point Y are not equal;

[0075] Define a point on the outer edge 3 of the blade as the design point Z, define the edge between the design point Z and the rear blade tip 7 as the guide portion arrangement edge, the guide portion arrangement edge protrudes to set the guide portion 10, and the width W of the guide portion 10 导流部 It gradually increases from the design point Z to the rear blade tip 7.

[0076] like Figure 1-3 As shown, when the air flows through the serrated blade 400, the special design of the serration arrangement edge on the trailing edge 4 plays a key role. i and height H i The uneven serrations 9, which are not equal from design point X to design point Y, complicate and disperse the airflow separation process at the trailing edge 4. Because the different sizes of serrations 9 create differential disturbances in the airflow, they disrupt the laminar boundary layer, causing the airflow to break off in discrete patterns, effectively suppressing the formation and development of vortices and significantly reducing airflow turbulence.

[0077] When the airflow flows through the guide portion 10 protruding from the outer edge 3 of the blade, its length is limited to the edge of the guide portion, and its width W is 导流部 The shape gradually increases from the design point Z to the rear blade tip 7, so that the airflow entering the blade area can be guided more accurately. 导流部 As the angle of the blade increases, the guiding effect of the guide portion 10 on the airflow is gradually enhanced, and the turbulent airflow can be gradually sorted into a smoother and more orderly flow state, guiding the airflow to pass through the blade body along the optimized trajectory.

[0078] It should be noted that the blade body described in the serrated blade is a sheet-like structure, including a flat shape, a twisted shape and other conventional shapes.

[0079] Therefore, the serrations 9 and the guide portion 10 on the serrated blade 400 cooperate with each other, making the energy exchange between the blade and the airflow more efficient, thereby achieving efficient air transportation.

[0080] In summary, through the optimized design of the blade shape, the serrated blade 400 brings about many significant beneficial effects:

[0081] 1. In terms of noise reduction, the unevenly arranged multiple saw teeth 9 disrupt the airflow shedding frequency, avoid the generation of concentrated noise, effectively reduce the operating noise of the equipment, and create a quiet environment for users.

[0082] 2. In terms of efficiency improvement, the air guide portion 10 reduces air flow turbulence and optimizes air flow trajectory, reduces air flow resistance, improves energy conversion efficiency, enables the equipment to achieve stronger air delivery capacity under the same energy consumption, and improves work efficiency.

[0083] 3. In terms of service life, the smooth and orderly airflow reduces the impact and wear on the blades, extends the service life of the blades and even the entire equipment, and reduces maintenance costs.

[0084] To further illustrate, the curve length of the trailing edge 4 is defined as L 叶尾缘 , define the curve length of the zigzag arrangement edge as L 锯齿 , define the length of the curve from the design point X to the rear blade root 8 as L1, define the length of the curve from the design point Y to the rear blade root 8 as L2,

[0085] Among them, L 锯齿 ≤1 / 2L 叶尾缘 , L1≥2 / 5L 叶尾缘 , L2≤9 / 10L 叶尾缘 .

[0086] On the one hand, the curve length of the serrated edge is limited and associated with the curve length of the blade trailing edge 4. On the other hand, the distribution range of the serrated edge is limited and associated with the design positions of the design point X and the design point Y respectively. The combination of the two limits makes the distribution position of the serrated edge avoid the flange area of ​​the blade trailing edge 4. Figure 2 As shown, if L1<2 / 5L 叶尾缘 , then the design point X, i.e. the sawtooth 9, is too close to the rear blade root 8, where the air volume is small and the effect is not obvious. If L2>9 / 10L 叶尾缘 , the design point Y, i.e., the serration 9, is too close to the rear blade tip 7, which is the flange area of ​​the blade trailing edge 4. The presence of the serration 9 in the flange area of ​​the blade trailing edge 4 will affect the original noise reduction function of the flange.

[0087] To further illustrate, the arrangement order of the plurality of saw teeth 9 is defined to start from the design point X and end at the design point Y;

[0088] The width W of the plurality of saw teeth 9 is i Satisfy in the order described:

[0089] W i =A1sin(ω1N i -φ1)-A2sin(ω2N i -φ2)+DN i +E;

[0090] Among them, W i is the width of the i-th sawtooth 9, in mm;

[0091] N i is the i-th sawtooth 9;

[0092] A1 and A2 are amplitudes, 1<A1, A2<1.3, unit is mm;

[0093] ω1 and ω2 are frequencies, 0.5<ω1, ω2<2, in Hz;

[0094] φ1 and φ2 are initial phases, 0.1<φ1, φ2<0.7, unit is rad;

[0095] D is the coefficient of the first-order term, 0.1<D<0.5;

[0096] E is the translation amount, 9<E<10, unit is mm.

[0097] like Figure 2 As shown, by limiting the width of the plurality of saw teeth 9 according to the arrangement order, the number of the plurality of saw teeth 9 is also limited, specifically as follows:

[0098] A1 and A2 are amplitudes, 1<A1 and A2<1.3. If A1 is too small, a single sawtooth 9 is too narrow, while if A2 is too large, a single sawtooth 9 is too wide, which increases or decreases the number of sawtooths 9 arranged at the same position. Both are not conducive to the breakup of the shedding vortex and the reduction of noise.

[0099] ω1 and ω2 are frequencies, 0.5<ω1 and ω2<2. If ω1 is too small, the width of a single sawtooth 9 will have a high repetition rate, causing differentiated disturbances to the airflow. If ω2 is too large, the width of a single sawtooth 9 will have a low repetition rate, and it will be unable to withstand the impact and wear of the airflow.

[0100] φ1 and φ2 are initial phases, 0.1<φ1 and φ2<0.7. If φ1 is too small, the serrated edge will move toward the rear blade root 8, while if φ2 is too large, the serrated edge will move toward the rear blade tip 7, affecting the flanging of the blade trailing edge 4.

[0101] D is a linear coefficient, 0.1<D<0.5, if D is too small, the width of the saw teeth 9 will change similarly, and if D is too large, the width of the saw teeth 9 will continue to increase.

[0102] E is the translation amount, 9<E<10. If E is too small, the width of all saw teeth 9 will be reduced, and if E is too large, the width of all saw teeth 9 will be increased, which will affect the number of saw teeth 9 within the same range.

[0103] To further illustrate, the arrangement order of the plurality of saw teeth 9 is defined to start from the design point X and end at the design point Y;

[0104] The height H of the plurality of saw teeth 9 is i Satisfy in the order described:

[0105] H i =A3N i 3 -B3N i 2 +C3N i +D3;

[0106] Among them, H i is the length of the i-th sawtooth 9, in mm;

[0107] N i is the i-th sawtooth 9;

[0108] A3 is the third phase coefficient, 0.05<A3<0.1;

[0109] B3 is the secondary phase coefficient, 0.5<B3<0.8;

[0110] C3 is the primary phase coefficient, 0.7<C3<1;

[0111] D3 is a constant, 2.5< D3<3.

[0112] like Figure 2 As shown, due to the curvilinear shape of the blade trailing edge 4, the saw teeth 9 on both sides of the sawtooth arrangement edge are similar in height, while the saw teeth 9 in the middle of the sawtooth arrangement edge have a large difference in height. If the height H of the plurality of saw teeth 9 is i If the coefficients in the limiting relationship are too large or too small, the heights of the saw teeth 9 on both sides and in the middle of the sawtooth arrangement edge will be offset, affecting the arrangement shape of the saw teeth 9 on the sawtooth arrangement edge.

[0113] It should be noted that the parameters of the saw teeth 9 on the sawtooth blade are all measured under axial projection, such as Figure 2 and Figure 5 shown.

[0114] To further illustrate, the guide portion 10 is formed by a first guide edge 101, a second guide edge 102, a third guide edge 103 and a fourth guide edge 104, wherein the first guide edge 101, the second guide edge 102, the third guide edge 103 and the fourth guide edge 104 are all arranged in a curved shape;

[0115] The curvature of the first guide edge 101 is the same as that of the blade outer edge 3 , and the first guide edge 101 is overlapped and connected with the guide portion arrangement edge;

[0116] The fourth guide edge 104 is arranged to overlap with the extension line of the blade trailing edge 4;

[0117] The included angle between the second guide edge 102 and the blade outer edge 3 is defined as γ;

[0118] Among them, 100°≤γ≤130°.

[0119] like Figure 3 As shown, when the airflow enters the guide portion 10 area, the special structures of the guide edges of the guide portion 10 work together. First, the curvature of the curve of the first guide edge 101 is consistent with the guide portion arrangement edge on the blade outer edge 3 and overlaps and connects. The fourth guide edge 104 overlaps with the extension line of the blade tail edge 4. This precise structural connection enables the airflow to smoothly and naturally transition to the inside of the guide portion 10. Secondly, the angle γ of 100°-130° between the second guide edge 102 and the blade outer edge 3 can form a perfect guide space within this range. When the airflow flows through, the angle γ prompts the airflow to flow along a specific trajectory, avoiding the formation of strong vortices in the airflow locally due to too small an angle, causing additional noise and energy loss; at the same time, it prevents the angle from being too large, causing the effective guiding area of ​​the guide portion 10 to be reduced, weakening the guiding effect on the airflow. Under the synergistic effect of the guide edge curves of the guide part 10, the airflow is further combed and regularized, flowing out of the blade in a more stable and orderly state, significantly reducing the interaction resistance between the airflow and the blade, greatly improving the energy exchange efficiency between the blade and the airflow, and realizing efficient air transportation.

[0120] To further illustrate, the length of the curve of the leaf outer edge 3 is defined as L 叶外缘 , define the curved length of the edge of the guide portion as L3;

[0121] Among them, 2 / 5L 叶外缘 ≤L3≤5 / 10L 叶外缘 .

[0122] like Figure 3 As shown, when the airflow reaches the guide portion 10 area of ​​the blade outer edge 3, the curve length L3 of the guide portion arrangement edge is at 2 / 5L 叶外缘 ≤L3≤5 / 10L 叶外缘 The range of L3 ensures the reasonable distribution of the air guide 10 on the blade outer edge 3. If L3 is too small, the air guide 10 will be limited in scope and unable to fully play its role in guiding and combing the airflow. Insufficient structural distribution will also affect the overall strength of the blade, causing deformation under the impact of airflow. If L3 is too large, exceeding the reasonable range, it will interfere with other blade components during installation, affecting the blade's installation adaptability.

[0123] Therefore, within this reasonable range, the guide portion 10 can not only fully guide the airflow by virtue of its sufficient length and range, and then use the specific angle γ between the aforementioned second guide edge 102 and the outer edge 3 of the blade to comb the turbulent airflow into a smooth and orderly state, thereby reducing the airflow resistance; it can also ensure the structural strength of the blade, so that the blade remains stable under high-speed rotation and the action of airflow, ensuring that the blade and the airflow efficiently complete energy exchange and realize efficient air transportation.

[0124] An axial flow impeller for a window air conditioner includes a hub 100, a water ring 200, a connector 300, and sawtooth blades 400. The sawtooth blades 400 are the sawtooth blades 400 described above.

[0125] The plurality of sawtooth blades 400 are spaced apart and distributed along the circumferential direction of the hub 100 , and the root edges 1 of the plurality of sawtooth blades 400 are fixedly connected to the outer periphery of the hub 100 ;

[0126] The water ring 200 is coaxially arranged with the hub 100. The connecting members 300 are fixedly connected between the water ring 200 and the guide portions 10 of the plurality of sawtooth blades 400. The connection direction of the connecting members 300 is parallel to the axial direction of the water ring 200. The outer edges 3 of the plurality of sawtooth blades 400 are arranged obliquely with respect to the water ring 200.

[0127] Define that the angle between the outer edge 3 of the sawtooth blade 400 and the water ring 200 in axial plane projection is β;

[0128] Where β=30°.

[0129] like Figure 4-7 As shown, when the window air conditioner is started, the motor drives the hub 100 to rotate at high speed, causing the multiple serrated blades 400 fixed to it to rotate accordingly, generating a powerful air-driving force. The serrated teeth 9 on the trailing edge 3 of the serrated blades 400 disrupt the laminar boundary layer of the airflow during rotation, discretizing the previously concentrated vortices, weakening their intensity and reducing airflow turbulence. The guide 10 on the outer edge 3 of the blade utilizes a unique curve design and angled configuration to precisely guide and organize the airflow, ensuring a more stable and orderly flow through the blades.

[0130] Furthermore, the water pumping ring 200 is coaxially arranged with the hub 100, and the connecting member 300 firmly connects the water pumping ring 200 with the guide portion 10 along the axial direction of the water pumping ring 200. This structure not only enhances the overall rigidity of the wind wheel, but also enables the water collecting trough on the water pumping ring 200 to effectively collect and discard condensed water when the wind wheel rotates.

[0131] From an axial perspective, the guide 10 reduces the distance between the blade outer edge 3 and the water ring 200, resulting in more even stress distribution on the connector 300 and improved connection strength, ensuring the rotor can withstand higher speeds. The large, concave serrations 9 on the blade trailing edge 4 continuously break up shed vortices at high speeds, offsetting the increased noise caused by the increased speed and ensuring the rotor operates efficiently and quietly.

[0132] From the radial projection, the outer edge 3 of the sawtooth blade 400 is inclined at an angle of 30° with the water ring 200. This angle design enables the blade to drive the condensed water to move on the surface of the water ring 200 while promoting the air flow.

[0133] In summary, the innovative design of the axial flow impeller for this window air conditioner brings the following significant technical advantages:

[0134] 1. Noise reduction: The serrated blades 400 effectively break up eddies, reduce operating noise and optimize sound quality. They can maintain a quiet environment even at high speeds, meeting users' needs for a comfortable experience.

[0135] 2. In terms of structural strength and lifespan, the coordinated design of the water ring 200, the connector 300 and the serrated blades 400 enhances the strength of key parts, reduces the risk of damage to the blades due to high-speed rotation and airflow impact, extends the service life of the wind wheel, and reduces the frequency and cost of equipment maintenance.

[0136] 3. Performance Improvement: The higher structural strength allows the impeller to operate at higher speeds. Combined with the aerodynamically optimized serrated blades 400, this increases the fan's working area, boosting impeller air volume and accelerating air circulation and heat exchange efficiency within the window air conditioner, enabling rapid cooling or heating. Furthermore, the water ring 200 effectively utilizes condensed water, improving the air conditioning system's energy efficiency. This aligns with energy conservation and environmental protection trends, enhances product market competitiveness, and provides a new direction for window air conditioner technology upgrades.

[0137] To further illustrate, the length of the curve from the connection point between the connecting member 300 and the guide portion 10 to the fourth guide edge 104 of the guide portion 10 is defined as L4;

[0138] Among them, 12mm≤L4≤30mm.

[0139] like Figure 7 As shown, precise control of the length L4, which is associated with the connection between the connector 300 and the air guide 10, ensures the stability and reliability of the connection between the air guide 10 and the connector 300. If L4 is less than 12 mm, the connection area between the air guide 10 and the connector 300 is too short to withstand the centrifugal force and airflow forces during high-speed rotation of the wind rotor, which can easily lead to loosening or even breakage of the connection. If L4 is greater than 30 mm, the connection structure between the air guide 10 and the water ring 200 is too loose, affecting the overall rigidity of the wind rotor and potentially changing the airflow path in the air guide 10 area, reducing the airflow guidance effect.

[0140] At the appropriate L4 length, the connector 300 can firmly connect the guide part 10 and the water ring 200, so that the water ring 200 can collect condensed water while ensuring the stable operation of the serrated blades 400, and maintain the efficient guidance of the airflow by the guide part 10, ensuring that the wind wheel can still achieve efficient and stable air delivery and condensed water utilization at high speed.

[0141] To further illustrate, there is a radial gap between the water ring 200 and the third guide edge 103 of the guide portion 10 , and the radial gap distance between the water ring 200 and the third guide edge 103 of the guide portion 10 is defined as L5;

[0142] Among them, 6mm≤L5≤9mm.

[0143] like Figure 7 As shown, precisely defining the radial gap between the water ring 200 and the third guide edge 103 of the guide portion 10 plays a key role in the stable operation and performance of the wind rotor. If L5 is less than 6mm, the water ring 200 and the third guide edge 103 are too close, which can easily cause airflow interference and even component friction during high-speed rotation of the wind rotor, increasing operating resistance and generating additional noise and wear. If L5 is greater than 9mm, the gap is too large, causing airflow leakage and turbulence in this area, weakening the effective guidance of the guide portion 10, reducing air delivery efficiency, and hindering the collection and removal of condensate by the water ring 200.

[0144] At a suitable length of L5, it can ensure that the water ring 200 and the guide part 10 do not interfere with each other and maintain the normal function of their respective functions. The water ring 200 can smoothly collect and throw away the condensed water, and the guide part 10 can efficiently comb the airflow; it can also make the connecting part 300 stably connect the guide part 10 and the water ring 200, ensuring that the wind wheel can achieve efficient and stable air transportation and condensed water utilization at high speed.

[0145] To further illustrate, the edge from the front blade tip 6 to the design point Z is defined as the airflow edge;

[0146] The length of the curve of the airflow edge is defined as L6;

[0147] The radial length between the airflow edge and the rotation axis of the hub 100 is defined as L7;

[0148] Among them, L7≤(AL6 3 +BL6 2 +CL6+D) / 2, the unit of L6 and L7 is mm;

[0149] A is the cubic phase coefficient, -3E-05<A<-1E-05;

[0150] B is the secondary phase coefficient, 0.005<B<0.007;

[0151] C is the primary phase coefficient, -1.3<C<-1;

[0152] D is a constant, 418<D<420.

[0153] like Figure 5 As shown, in order to make the sawtooth blade 400 and the guide portion 10 transition smoothly, the coefficients should not be too large or too small, otherwise, the outer edge 3 of the sawtooth blade 400 will suddenly turn, which is not conducive to airflow.

[0154] In order to further demonstrate the performance of the serrated blades 400 of the present invention when applied to the axial flow impeller for a window air conditioner, a non-serrated blade was used as a comparative example to obtain performance test results and airflow distribution diagrams of the two under the same test conditions.

[0155] The wind wheel performance test results are shown in the following table, and the airflow distribution diagram is shown in the following table. Figure 8 shown.

[0156]

[0157] It can be seen from the results of the wind wheel performance test that as the speed increases, the axial flow wind wheel for window machine using either non-serrated blades or serrated blades will generate increasingly louder noise, but at the same speed, the noise generated by the axial flow wind wheel for window machine using serrated blades will be lower than that of the axial flow wind wheel for window machine using non-serrated blades.

[0158] Depend on Figure 8 As shown in the airflow distribution diagram, when the airflow passes through the trailing edge of the blade without serrations, the airflow gathers and sheds vortices at the trailing edge, which leads to an increase in the noise increment, such as Figure 8 As shown in (b) in the figure, when the airflow passes through the trailing edge 4 of the serrated blade 400, the larger and concave serrations 9 on the trailing edge 4 process the airflow, breaking the laminar boundary layer and converting the concentrated vortex into discrete small vortices, thus reducing the vortex intensity and offsetting the noise increase caused by the increase in speed, ensuring that the wind wheel operates efficiently while maintaining low noise. Figure 8 As shown in (a).

[0159] In summary, the sawtooth blades 400 of the present invention are applied to the axial flow impeller for the window fan, which can improve the overall performance of the equipment.

[0160] The technical principles of the present invention have been described above with reference to specific embodiments. These descriptions are intended solely to illustrate the principles of the present invention and are not to be construed in any way as limiting the scope of protection of the present invention. Based on the explanations herein, those skilled in the art will be able to devise other specific embodiments of the present invention without inventive effort, and such equivalent variations or substitutions are intended to be encompassed within the scope of the claims of this application.

Claims

1. A sawtooth blade (400), characterized in that: It comprises a blade body and a flow guide portion (10) protruding and connected to the outer side of the blade body; The blade body is a sheet-like structure, and the peripheral contour of the blade body is formed by the blade root edge (1), the blade leading edge (2), the blade outer edge (3) and the blade trailing edge (4). The blade root edge (1), the blade leading edge (2), the blade outer edge (3) and the blade trailing edge (4) are all arranged in a curved shape, and the connection points between the blade root edge (1), the blade leading edge (2), the blade outer edge (3) and the blade trailing edge (4) are the front blade root (5), the front blade tip (6), the rear blade tip (7) and the rear blade root (8) in sequence. Two points on the trailing edge (4) of the blade are defined as a design point X and a design point Y, wherein the design point X is located close to the rear blade root (8) and the design point Y is located close to the rear blade tip (7). The edge between the design point X and the design point Y is defined as a sawtooth arrangement edge, wherein the sawtooth arrangement edge is concavely provided with a plurality of saw teeth (9), and the width W of the plurality of saw teeth (9) is i and height H i The values ​​from the design point X to the design point Y are not equal; A certain point on the outer edge (3) of the blade is defined as a design point Z, and the edge between the design point Z and the rear blade tip (7) is defined as a guide portion arrangement edge, wherein the guide portion arrangement edge protrudes to set the guide portion (10), and the width W of the guide portion (10) is 导流部 It gradually increases from the design point Z to the rear blade tip (7); The length of the curve of the trailing edge (4) of the blade is defined as L 叶尾缘 , define the curve length of the zigzag arrangement edge as L 锯齿 , define the length of the curve from the design point X to the rear blade root (8) as L1, define the length of the curve from the design point Y to the rear blade root (8) as L2, Among them, L 锯齿 ≤1 / 2L 叶尾缘 , L1≥2 / 5L 叶尾缘 , L2≤9 / 10L 叶尾缘 ; The guide portion (10) is formed by enclosing a first guide edge (101), a second guide edge (102), a third guide edge (103) and a fourth guide edge (104); the first guide edge (101), the second guide edge (102), the third guide edge (103) and the fourth guide edge (104) are all arranged in a curved shape; The curvature of the first guide edge (101) is the same as the curvature of the blade outer edge (3), and the first guide edge (101) is overlapped and connected with the guide portion arrangement edge; The fourth guide edge (104) is arranged to overlap with an extension line of the blade trailing edge (4); The angle between the second guide edge (102) and the blade outer edge (3) is defined as γ; Among them, 100°≤γ≤130°.

2. The sawtooth blade (400) according to claim 1, characterized in that: Defining an arrangement order of the plurality of saw teeth (9) starting from the design point X and ending at the design point Y; The width W of the plurality of saw teeth (9) i Satisfy in the order described: <h2 style=";text-align:left;direction:ltr">W<h2 style=";text-align:left;direction:ltr"> i <h2 style=";text-align:left;direction:ltr"> =A1sin(ω1N<h2 style=";text-align:left;direction:ltr"> i <h2 style=";text-align:left;direction:ltr"> -φ1)-A2sin(ω2N<h2 style=";text-align:left;direction:ltr"> i <h2 style=";text-align:left;direction:ltr"> -φ2)+DN<h2 style=";text-align:left;direction:ltr"> i <h2 style=";text-align:left;direction:ltr"> +E Among them, W i is the width of the i-th sawtooth (9), in mm; N i is the i-th sawtooth (9); A1 and A2 are amplitudes, 1<A1, A2<1.3, unit is mm; ω1 and ω2 are frequencies, 0.5<ω1, ω2<2, in Hz; φ1 and φ2 are initial phases, 0.1<φ1, φ2<0.7, unit is rad; D is the coefficient of the first-order term, 0.1<D<0.5; E is the translation amount, 9<E<10, unit is mm.

3. The sawtooth blade (400) according to claim 1, characterized in that: Defining an arrangement order of the plurality of saw teeth (9) starting from the design point X and ending at the design point Y; The height H of the plurality of saw teeth (9) i Satisfy in the order described: H i =A3N i 3 -B3N i 2 +C3N i +D3 Among them, H i is the length of the i-th saw tooth (9), in mm; N i is the i-th sawtooth (9); A3 is the third phase coefficient, 0.05<A3<0.1; B3 is the secondary phase coefficient, 0.5<B3<0.8; C3 is the primary phase coefficient, 0.7<C3<1; D3 is a constant, 2.5< D3<3.

4. The sawtooth blade (400) according to claim 1, characterized in that: Define the length of the curve of the leaf outer edge (3) as L 叶外缘 , define the curved length of the edge of the guide portion as L3; Among them, 2 / 5L 叶外缘 ≤L3≤5 / 10L 叶外缘 .

5. An axial flow fan for a window machine, characterized in that: It comprises a hub (100), a water ring (200), a connecting piece (300) and a sawtooth blade (400), wherein the sawtooth blade (400) is a sawtooth blade (400) according to any one of claims 1 to 4; The plurality of sawtooth blades (400) are spaced apart and distributed along the circumferential direction of the hub (100), and the blade root edges (1) of the plurality of sawtooth blades (400) are fixedly connected to the outer periphery of the hub (100); The water pumping ring (200) is coaxially arranged with the hub (100), and the connecting members (300) are respectively fixedly connected between the water pumping ring (200) and the guide portions (10) of the plurality of sawtooth blades (400), the connecting direction of the connecting member (300) is parallel to the axial direction of the water pumping ring (200), and the outer edges (3) of the plurality of sawtooth blades (400) are arranged obliquely with respect to the water pumping ring (200); It is defined that, in axial plane projection, the angle between the outer edge (3) of the sawtooth blade (400) and the water ring (200) is β; Where β=30°.

6. The axial flow impeller for a window machine according to claim 5, characterized in that: The length of the curve from the connection point between the connecting member (300) and the guide portion (10) to the fourth guide edge (104) of the guide portion (10) is defined as L4; Among them, 12mm≤L4≤30mm.

7. The axial flow impeller for a window machine according to claim 5, characterized in that: There is a radial gap between the water pumping ring (200) and the third guide edge (103) of the guide portion (10), and the radial gap distance between the water pumping ring (200) and the third guide edge (103) of the guide portion (10) is defined as L5; Among them, 6mm≤L5≤9mm.

8. The axial flow impeller for a window machine according to claim 5, characterized in that: The edge from the front blade tip (6) to the design point Z is defined as the airflow edge; The length of the curve of the airflow edge is defined as L6; The radial length between the airflow edge and the rotation axis of the hub (100) is defined as L7; Among them, L7≤(AL6 3 +BL6 2 +CL6+D) / 2, the unit of L6 and L7 is mm; A is the cubic phase coefficient, -3E-05<A<-1E-05; B is the secondary phase coefficient, 0.005<B<0.007; C is the primary phase coefficient, -1.3<C<-1; D is a constant, 418<D<420.

Images