Impeller, centrifugal fan and range hood

Abstract

The invention relates to the technical field of household appliances, and provides an impeller, a centrifugal fan and a range hood, the impeller comprises a plurality of blades, the plurality of blades are annularly arranged, and the plurality of blades are non-uniformly distributed in the circumferential direction of the impeller; wherein the included angle between every two adjacent blades is obtained by modulating the position angle of the first blade in the impeller through a preset sine function, so that all the blades are periodically distributed in the circumferential direction of the impeller. The multiple blades are distributed in the circumferential direction of the impeller in a non-uniform periodic mode and are modulated mainly according to a sine function, namely, the included angle between the adjacent blades follows the change rule of the sine function. According to the obtained impeller, the aerodynamic performance is basically kept unchanged, the noise performance is greatly improved, and half-noise reduction and working noise can be reduced.

Description

Technical Field

[0001] This invention relates to the field of household appliance technology, and more particularly to impellers, centrifugal fans, and range hoods. Background Technology

[0002] Currently, the impellers used in centrifugal fans of range hoods on the market are basically uniformly plated sheet metal impellers. However, the aforementioned uniformly plated sheet metal impellers cause the peak values ​​of discrete noise to superimpose, which is detrimental to the operating noise and semi-cancellation noise of the range hood. Summary of the Invention

[0003] This invention aims to solve the technical problems existing in related technologies. To this end, this invention proposes an impeller that helps reduce semi-canceling noise and operating noise.

[0004] The present invention also proposes a centrifugal fan.

[0005] The present invention also proposes a range hood.

[0006] An impeller according to a first aspect of the present invention includes: Multiple blades, the multiple blades are arranged in a ring, and the multiple blades are non-uniformly distributed in the circumferential direction of the impeller; The included angle between two adjacent blades is obtained by modulating the position angle of the first blade in the impeller using a preset sine function, so that all the blades are periodically distributed along the circumference of the impeller.

[0007] According to an embodiment of the present invention, the impeller has multiple blades that are non-uniformly and periodically distributed in the circumferential direction, and are mainly modulated according to a sine function, that is, the angle between adjacent blades follows the variation law of a sine function. With the impeller obtained as described above, the aerodynamic performance remains essentially unchanged, while the noise performance is significantly improved, which is beneficial for reducing semi-cancelled noise and operating noise.

[0008] According to one embodiment of the present invention, the sine function is: memb_v=(idx1-1)×(360 / 60)+10×sin(RADIANS((idx1-1)×6×3))+lead_v; In this context, the rotation direction of the impeller is taken as the positive direction. The first blade is defined as the blade that intersects the positive direction of the impeller's central axis, and the position angle of the first blade is defined as 0 degrees. memb_v is the position angle of the i-th blade. idx1 is the number of the i-th blade, idx1=1,2,3,…,60. lead_v is the position angle of the first blade. RADIANS is a function that converts angles into radians.

[0009] According to one embodiment of the present invention, the impeller includes an upper disk, a lower disk, and a middle disk, wherein the upper disk, the middle disk, and the lower disk are arranged sequentially along the axial direction of the middle disk, and the middle disk is used to mount a motor; Multiple blades are arranged between the upper plate and the middle plate, and between the middle plate and the lower plate.

[0010] According to one embodiment of the present invention, the blade has a first arc segment and a second arc segment in the radial outward direction along the central disk; The outer diameter of the plurality of blades arranged between the upper plate and the middle plate, and between the middle plate and the lower plate, formed by the first arc segment is d1; the outer diameter of the plurality of blades arranged between the upper plate and the middle plate, and between the middle plate and the lower plate, formed by the second arc segment is d2. The ratio of d1 to d2 is 1 to 4.

[0011] According to one embodiment of the present invention, the inlet angle of the first arc segment is β1a, the outlet angle of the first arc segment is β1b, the inlet angle of the second arc segment is β2a, and the outlet angle of the second arc segment is β2b. Wherein, the value of β1a is in the range of 60 degrees to 70 degrees, the value of β1b is equal to the value of β2a, the value range of both β1b and β2a is 120 degrees to 130 degrees, and the value range of β2b is 160 degrees to 170 degrees.

[0012] According to one embodiment of the present invention, the ratio of the chord length of the first arc segment to the chord length of the second arc segment is 2 to 3.

[0013] According to one embodiment of the present invention, the inner diameter of the inner peripheral edge of both the upper plate and the lower plate is a first inner diameter; The inner peripheral edges of the plurality of blades arranged between the upper disk and the middle disk, and between the middle disk and the lower disk, form a second inner diameter; Wherein, the second inner diameter is smaller than the first inner diameter.

[0014] According to one embodiment of the present invention, the outer diameter of the outer peripheral edges of both the upper plate and the lower plate is a first outer diameter; The outer peripheral edges of the plurality of blades arranged between the upper disk and the middle disk, and between the middle disk and the lower disk, form a second outer diameter; Wherein, the second outer diameter is smaller than the first outer diameter.

[0015] According to one embodiment of the present invention, a mounting platform is provided in the middle of the middle plate, the mounting platform being convex toward the direction of the upper plate, and the mounting platform being used to install and accommodate at least a portion of the structure of the motor.

[0016] According to one embodiment of the present invention, the mounting platform is provided with a plurality of air passage holes along the circumferential direction of the central plate and along its axial direction.

[0017] According to one embodiment of the present invention, the impeller further includes a bushing, the bushing being disposed on the central disk and fixedly connected to the central disk, the bushing being used to fix the relative position of the impeller and the motor shaft of the motor.

[0018] According to one embodiment of the present invention, the blade, the upper disk, the lower disk, the middle disk, and the bushing are configured as an integrally formed structure; Alternatively, the blade, the upper disk, the lower disk, the middle disk, and the bushing are configured as separate fixed connections.

[0019] According to a second aspect of the present invention, a centrifugal fan includes a volute and an impeller as described in the first aspect of the present invention, wherein the impeller is disposed within the volute.

[0020] According to a third aspect of the present invention, a range hood includes a frame and a centrifugal fan as described in the second aspect of the present invention, wherein the centrifugal fan is installed within the frame.

[0021] Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0022] To more clearly illustrate the technical solutions in the embodiments of the present invention or related technologies, the drawings used in the description of the embodiments or related technologies will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0023] Figure 1 This is one of the structural schematic diagrams of the impeller provided in the embodiments of the present invention, wherein Z is the central axis of the impeller and O is the center of the circle.

[0024] Figure 2 This is the second schematic diagram of the impeller structure provided in the embodiment of the present invention.

[0025] Figure 3 This is a schematic diagram of the angle distribution between adjacent blades corresponding to the sinusoidal function modulation provided in the embodiment of the present invention.

[0026] Figure 4 This is one of the cross-sectional schematic diagrams of the impeller provided in the embodiments of the present invention.

[0027] Figure 5 yes Figure 4 An enlarged schematic diagram of the structure at point A in the middle.

[0028] Figure 6 This is the third schematic diagram of the impeller structure provided in the embodiment of the present invention.

[0029] Figure 7 This is the second cross-sectional schematic diagram of the impeller provided in the embodiment of the present invention.

[0030] Figure label: 100, Blade; 110, First arc segment; 120, Second arc segment; 200, Upper plate; 300, Lower plate; 400, Middle plate; 410, Mounting platform; 411, Airflow hole; 500, Bushing; D10, First inner diameter; D20, Second inner diameter; D30, First outer diameter; D40, Second outer diameter; O, Center; Z, Central shaft. Detailed Implementation

[0031] The embodiments of the present invention will be described in further detail below with reference to the accompanying drawings and examples. The following examples are for illustrative purposes only and should not be construed as limiting the scope of the invention.

[0032] In the description of the embodiments of the present invention, it should be noted that the terms "center," "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing the embodiments of the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the embodiments of the present invention. In addition, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0033] In the description of the embodiments of the present invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "connected" and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of the present invention based on the specific circumstances.

[0034] In embodiments of the present invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0035] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0036] The following is combined Figure 1 - Figure 7 The impeller, centrifugal fan, and range hood of the present invention will be described in the embodiments thereof.

[0037] Understandably, referring to Figure 1 and Figure 2 In some examples of the present invention, the impeller includes a plurality of blades 100 arranged in a ring and the plurality of blades 100 are non-uniformly distributed in the circumference of the impeller; wherein the included angle between two adjacent blades 100 is obtained by modulating the position angle of the first blade 100 in the impeller with a preset sine function, so that all blades 100 are periodically distributed in the circumference of the impeller.

[0038] According to an embodiment of the present invention, the impeller has multiple blades 100 arranged in a non-uniform periodic distribution along its circumference, primarily modulated according to a sine function, meaning the angle between adjacent blades 100 follows a sine function variation pattern. With the impeller obtained as described above, the aerodynamic performance remains essentially unchanged, while noise performance is significantly improved, which is beneficial for reducing semi-cancelled noise and operating noise.

[0039] It is understood that, in some examples of this invention, the sine function is: memb_v=(idx1-1)×(360 / 60)+10×sin(RADIANS((idx1-1)×6×3))+lead_v; Here, taking the impeller's rotation direction as the positive direction, the first blade 100 is defined as the blade 100 that intersects the positive direction of the impeller's central axis Z, and the position angle of the first blade 100 is defined as 0 degrees; memb_v is the position angle of the i-th blade 100; idx1 is the number of the i-th blade 100, idx1=1,2,3,…,60; lead_v is the position angle of the first blade 100; RADIANS is a function that converts angles to radians.

[0040] It can be understood that the above-mentioned modulated sine function is divided into three parts. The first term on the right represents the position angle of each blade 100 under uniform distribution. The second term represents the incremental adjustment of the position of each uniformly distributed blade 100. The third term represents the position of the first blade 100. Among them, the second term is the most critical, as it determines the period of the blade 100 distribution and the amplitude of the angle between adjacent blades 100.

[0041] Using the above formulas, the impeller design must ensure its dynamic balance to guarantee the safe and stable operation of the centrifugal fan. The key to the non-uniform design of the blades 100 is to ensure both a uniform spatial distribution of the impeller mass to maintain dynamic balance and a non-uniform circumferential distribution of the blades 100 to reduce sound wave superposition. Therefore, the non-uniform blades 100 of this invention are periodically distributed circumferentially, primarily modulated according to a sine function, so that the angle between adjacent blades 100 follows a sine function variation pattern.

[0042] By changing the included angle between adjacent blades 100, the included angle between adjacent blades 100 is distributed according to a sine law. And by optimizing the parameters such as the period and amplitude of the sine function, a sinusoidal distributed multi-blade centrifugal fan impeller with significant noise reduction effect is obtained.

[0043] Reference Figure 3 As shown in the figure, the angular distribution between adjacent blades 100 corresponding to the sinusoidal function modulation used in this invention is illustrated. The total number of blades is 60, and the position of blade 100 is adjusted every 6 degrees, corresponding to a total of 3 sinusoidal function periods. Experiments show that the non-uniformly distributed impeller obtained according to this method maintains essentially the same aerodynamic performance while significantly improving noise performance. The A-weighted semi-cancelled noise decreases from 64 dB to 62.9 dB, and the operating noise decreases from 64 dB to 63.4 dB, demonstrating a significant noise reduction effect.

[0044] Understandably, referring to Figure 1 and Figure 2, in some examples of the present invention, the impeller includes an upper disk 200, a lower disk 300, and a middle disk 400. Along the axial direction of the middle disk 400, the upper disk 200, the middle disk 400, and the lower disk 300 are arranged in sequence, and the middle disk 400 is used for installing the motor; wherein, a plurality of blades 100 are arranged between the upper disk 200 and the middle disk 400, and between the middle disk 400 and the lower disk 300.

[0045] The impeller adopts a three-layer structure of an upper disk 200, a middle disk 400, and a lower disk 300. The middle disk 400 integrates the motor installation position. A plurality of blades 100 are distributed between the upper and lower disks 300 and the middle disk 400, effectively improving the structural stability and the motor assembly accuracy. At the same time, the layout of the blades 100 is optimized, improving the fluid dynamic performance and the operation efficiency.

[0046] Specifically, referring Figure 4 and Figure 5 , in some examples of the present invention, along the radially outward direction of the middle disk 400, the blade 100 has a first arc 110 and a second arc 120.

[0047] It should be noted that, to define the variation law of the radius R at the tangent point of the two arcs and the blade angle β at the corresponding position, let: ; ; In the formula: are respectively named the intermediate circle coefficient and the blade angle coefficient, is the impeller radius corresponding to the tangent point of the first arc 110 and the second arc 120, is the blade setting angle corresponding to the tangent point of the two arcs, is the inner diameter of the impeller, is the outer diameter of the impeller, is the blade inlet angle, [[ID=�4]] is the blade outlet angle. Different combinations of the two coefficients result in different double arcs, and the formed blade flow channels also change accordingly, thereby achieving the control of the flow. It should be noted that, in this embodiment, the above takes a value of 0.2, takes a value of 0.3.

[0048] Based on the above formula, the parameters of the two arcs are determined as follows: Referring Figure 4 and Figure 5In this embodiment, the outer diameter formed by the multiple blades 100 arranged between the upper plate 200 and the middle plate 400, and between the middle plate 400 and the lower plate 300 at the first arc 110 is d1, and the outer diameter formed by the multiple blades 100 arranged between the upper plate 200 and the middle plate 400, and between the middle plate 400 and the lower plate 300 at the second arc 120 is d2; wherein, the ratio of d1 to d2 is 1 to 4.

[0049] With the above settings, the blade 100 adopts a double arc form. Looking outward from the radial direction of the center line of the middle disk 400, it consists of a first arc 110 and a second arc 120. By adjusting the ratio of the two arcs, the flow separation in the flow channel of the first arc 110 can be reduced, thereby improving aerodynamic efficiency.

[0050] Specifically, refer to Figure 5 In some examples of the present invention, the inlet angle of the first arc 110 is β1a, the outlet angle of the first arc 110 is β1b, the inlet angle of the second arc 120 is β2a, and the outlet angle of the second arc 120 is β2b; wherein, the value of β1a is in the range of 60 degrees to 70 degrees, the value of β1b is equal to the value of β2a, the value of both β1b and β2a is in the range of 120 degrees to 130 degrees, and the value of β2b is in the range of 160 degrees to 170 degrees.

[0051] With the above settings, the inlet and outlet angles of the two arcs have been carefully optimized, which can effectively reduce the resistance and local scouring during the flue gas flow process.

[0052] Specifically, in some examples of the present invention, the ratio of the chord length of the first arc 110 to the chord length of the second arc 120 is 2:3. By adopting the above setting and controlling the ratio of the chord length of the first arc 110 to the chord length of the second arc to be 2:3, a reasonable velocity gradient and pressure distribution can be formed in the impeller flow channel, thereby improving the operational stability and impeller durability under flue gas conditions.

[0053] Specifically, in some examples of the present invention, the upper plate 200 and the lower plate 300 are both hollow components, the inner diameters of the upper plate 200 and the lower plate 300 are configured to be equal, and the outer diameters of the upper plate 200 and the lower plate 300 are configured to be equal.

[0054] Specifically, refer to Figure 4 and Figure 6 In some examples of the present invention, the inner diameter of the inner peripheral edge of both the upper plate 200 and the lower plate 300 is a first inner diameter D10; the inner peripheral edges of a plurality of blades 100 arranged between the upper plate 200 and the middle plate 400, and between the middle plate 400 and the lower plate 300, form a second inner diameter D20; wherein, the second inner diameter D20 is smaller than the first inner diameter D10.

[0055] It can be understood that the upper plate 200 and the lower plate 300 are hollow discs with equal thickness, which serve to fix the blade 100. The upper plate 200 and the lower plate 300 have the same inner diameter, that is, the inner diameter of both is 211.2mm.

[0056] More specifically, in this embodiment, the difference between the first inner diameter D10 and the second inner diameter D20 is 26 mm.

[0057] It should be noted that in this embodiment, the second inner diameter D20 refers to the diameter of the circumference corresponding to the starting point of the blade 100 profile.

[0058] With the above structural arrangement, the upper plate 200 and lower plate 300 form a relatively large flow channel inlet with a first inner diameter D10, while the flow channel enclosed by the blades 100 has a second inner diameter D20, which is smaller than the first inner diameter D10. After the airflow flows in through the first inner diameter D10, it passes through a gradually narrowing transition region before entering the blades 100, achieving a natural increase in flow velocity and smooth convergence of streamlines. This design effectively reduces airflow impact and separation at the inlet, reduces the generation of turbulence and eddies, and allows the airflow to enter the working area of ​​the blades 100 more evenly, thereby reducing flow resistance and energy loss, improving the aerodynamic efficiency and operational stability of the impeller, and is particularly suitable for working environments prone to wear and deposition, such as those with dusty flue gas.

[0059] Specifically, refer to Figure 4 and Figure 6 In some examples of the present invention, the outer diameter of the outer periphery of both the upper plate 200 and the lower plate 300 is a first outer diameter D30; the outer periphery of a plurality of blades 100 arranged between the upper plate 200 and the middle plate 400, and between the middle plate 400 and the lower plate 300, forms a second outer diameter D40; wherein the second outer diameter D40 is smaller than the first outer diameter D30.

[0060] This can be understood as the upper plate 200 and the lower plate 300 having the same outer diameter, that is, both of them have an outer diameter of 237.6mm.

[0061] More specifically, in this embodiment, the difference between the first outer diameter D30 and the second outer diameter D40 is 1 mm.

[0062] It should be noted that in this embodiment, the second outer diameter D40 refers to the diameter of the circumference corresponding to the end point of the blade 100 profile.

[0063] By setting the outer diameter of both the upper plate 200 and the lower plate 300 to the first outer diameter D30, and making the second outer diameter D40 formed by the multiple blades 100 smaller than the first outer diameter D30, the radial profile of the multiple blades 100 in the entire circumferential direction can always be within the projection range of the upper plate 200 and the lower plate 300, thereby ensuring that the blades 100 do not protrude from the upper plate 200 and the lower plate 300 in the entire circumferential direction. This structure avoids airflow disturbance and local scouring caused by the exposed ends of the blades 100, helps to maintain the continuity of the flow field around the impeller, reduces operating noise and wear risk, and improves the stability and safety of the whole machine operation. It is especially suitable for working environments containing particulate matter, such as flue gas.

[0064] It should be noted that the aforementioned second outer diameter D40 can also be understood as the outer diameter d2 of the second arc 120.

[0065] Understandably, referring to Figure 7 In some examples of the present invention, a mounting platform 410 is provided in the middle of the middle plate 400. The mounting platform 410 protrudes in the direction of the upper plate 200 and is used to mount and accommodate at least part of the structure of the motor.

[0066] With the above-mentioned configuration, the middle plate 400 has a raised structure in the center, namely the mounting platform 410, which provides ample space for the installation of the motor and thus forms a double-suction impeller structure. The middle plate 400 has a rotating design, which not only serves to fix the blades 100, but also separates the blades 100 between the upper plate 200 and the middle plate 400, and between the middle plate 400 and the lower plate 300. This is conducive to balancing air intake and exhaust, and improving the impeller's operating efficiency and structural stability under flue gas and other working conditions.

[0067] Specifically, refer to Figure 7 In some examples of the present invention, along the circumferential direction of the central plate 400, the mounting platform 410 is provided with a plurality of air passage holes 411 along its axial direction. It can be understood that the wall surface of the mounting platform 410 is provided with a plurality of air passage holes 411, and along the axial direction of the central plate 400, the air passage holes 411 connect the opposite sides of the central plate 400.

[0068] With the above configuration, multiple airflow holes 411 are provided on the wall of the mounting platform 410. These holes penetrate the central plate 400 along the impeller axis, connecting the flow channels on both sides of the central plate 400. This design promotes airflow exchange and pressure balance between the two sides during the operation of the double-suction impeller, improving airflow uniformity and operational stability. Furthermore, external air can flow through the airflow holes 411 into the motor mounting area, achieving continuous ventilation and heat dissipation for the motor, reducing temperature rise, and extending motor lifespan. This design is particularly suitable for high-load, high-temperature environments such as those involving flue gas.

[0069] More specifically, in some examples of the present invention, the air passage 411 is in the shape of a trapezoidal structure.

[0070] The air passage 411 is designed as a trapezoidal structure, which can make the airflow within the passage smoother while ensuring sufficient flow area, reducing local resistance and eddies caused by abrupt changes in cross-section, thereby improving ventilation efficiency and heat dissipation.

[0071] Of course, in other examples, the air passage 411 can also be designed as a circular structure, a rectangular structure, etc.

[0072] Reference Figure 6 In some examples of this invention, the number of airflow holes 411 is five. Practical verification has shown that using five airflow holes 411 achieves a good balance between air intake on both sides of the double-suction impeller and motor heat dissipation. However, the number of holes is not limited to this; it can be flexibly adjusted to other numbers according to the specific requirements of impeller size, motor power, and flue gas conditions to further optimize airflow organization and heat dissipation performance, ensuring that the system remains stable and efficient under different operating conditions.

[0073] Understandably, referring to Figure 7 In some examples of the present invention, the impeller further includes a bushing 500, which is disposed on and fixedly connected to the central disk 400. The bushing 500 is used to fix the relative position of the impeller and the motor shaft of the motor.

[0074] By adopting the above configuration, by adding a bushing 500 fixed to the central plate 400, the impeller and the motor shaft can be reliably connected, ensuring their coaxiality and transmission stability, reducing operating vibration and wear, while simplifying the assembly structure and improving the overall mechanical strength and service life.

[0075] Specifically, in some examples of the present invention, the blade 100, upper disk 200, lower disk 300, middle disk 400 and bushing 500 are configured as an integrally formed structure.

[0076] By designing the blade 100, upper plate 200, lower plate 300, middle plate 400, and bushing 500 into an integrated molding structure, the assembly gaps and weak points between the components are eliminated, significantly improving the overall rigidity and strength of the impeller and reducing the risk of deformation and cracking under high-load flue gas conditions. At the same time, the production process is simplified, the number of parts and assembly steps are reduced, production efficiency and structural consistency are improved, and the reliability and durability of operation are enhanced.

[0077] Alternatively, in some other examples, the blade 100, upper plate 200, lower plate 300, middle plate 400, and bushing 500 are configured as separate fixed connections.

[0078] The blade 100, upper plate 200, lower plate 300, middle plate 400 and bushing 500 are fixedly connected in a split manner. Different materials or processing techniques can be selected according to the stress and functional requirements of each part to achieve targeted optimization and improve the wear resistance, high temperature resistance or corrosion resistance of key parts. At the same time, it is convenient for production, maintenance and replacement and fault repair, reducing the overall maintenance cost and enhancing the adaptability and maintainability of the structure under complex flue gas conditions.

[0079] It is understood that in this embodiment, the bushing 500 is disposed inside the middle plate 400, and the bushing 500 and the middle plate 400 are fixedly connected to each other. By fixing it to the middle plate 400, refer to... Figure 1 The middle plate 400 has a center hole with the center O as the center, which is the center of the mounting platform 410. The bushing 500 is embedded in the center hole, and the side of the bushing 500 near the lower plate 300 has a keyway. The side of the bushing 500 near the upper plate 200 extends to be flush with the motor shaft.

[0080] It should be noted that in this embodiment, the center O of the aforementioned middle disk 400 coincides with the central axis Z of the impeller.

[0081] With the above configuration, the bushing 500 is fitted into the center hole of the middle plate 400 and fixedly connected to it, so that the middle plate and the bushing form a rigid whole, which not only ensures the coaxiality of the motor shaft and the middle plate 400, but also improves the transmission stability. One end of the bushing 500 is provided with a keyway, which can reliably transmit torque and prevent slippage, while the other end extends to be flush with the motor shaft, which facilitates assembly and balanced force distribution. At the same time, the structure is compact, which helps to reduce the overall size of the machine.

[0082] It should be noted that the motor is a DC copper wire motor with a design speed of 1000 rpm and a rated power of 500W.

[0083] It is understood that the function of the bushing 500 is to fix the impeller on the motor shaft so that the impeller and the motor shaft rotate at the same angular velocity. The bushing 500 and the middle disk 400 of this invention are 3D printed as a whole. If sheet metal process is used, the bushing 500 and the middle disk 400 are fixed by riveting. It should also be noted that the integrated 3D printing process can use high-temperature resistant materials such as nylon, the blade 100 has good line retention, and it is convenient to perform three-dimensional modeling of the blade 100 and support various arrangement forms. The blade 100 distributed according to the sinusoidal law used in this invention can significantly reduce the peak value of discrete noise and has a significant reduction effect on A-weighted operating noise and semi-cancelled noise.

[0084] When using metal materials, a traditional insert-type process, i.e., a split-type fixed connection, can be adopted. The blades 100 between the upper plate 200 and the middle plate 400, and the blades 100 between the lower plate 300 and the middle plate 400, can be combined into a single part model for production. This part only needs to have its length adjusted to meet the assembly requirements of different positions, while maintaining the same structural features. The upper plate 200, middle plate 400, lower plate 300, and bushing 500 are processed as independent parts. The thickness of each part should be set according to its function and stress requirements, and controlled using different processing parameters. This approach reduces the number of parts, simplifies the process flow, and simultaneously ensures assembly accuracy and the mechanical properties of each component.

[0085] It is understood that in some examples of the present invention, the centrifugal fan includes a volute and the aforementioned impeller, with the impeller disposed within the volute. Of course, the centrifugal fan also includes other components such as a motor, wherein the volute guides the airflow and forms the required flow channel, and the motor drives the impeller to rotate at high speed, thereby generating airflow pressure and flow rate.

[0086] In some examples of this invention, the range hood includes a frame and a centrifugal fan with the aforementioned impeller, the centrifugal fan being mounted within the frame. The frame supports the entire fan assembly and the main structure of the range hood, and works in conjunction with other components to form a complete fume collection and emission system. This combined structure ensures efficient aerodynamics while also guaranteeing stable operation of the equipment and robust installation of the entire unit.

[0087] Of course, in other examples, the range hood also includes other components of the housing, such as an air intake filter.

[0088] It should be noted that in some examples of this invention, based on market research and the demand from households for small-sized, high-airflow, and low-noise range hoods, and within a small frame size (350mm x 309mm x 440mm), to further reduce semi-cancellation noise and operating noise, and based on the principle of reducing the superposition of phase differences from aerodynamic noise sources, an impeller with unequally spaced blades 100 modulated by a sine function was designed. The included angle between adjacent blades 100 is arranged according to a sine law. Using 60 blades 100 as a benchmark, orthogonal experiments were conducted on the period and amplitude of the sine function, and a sine distribution impeller with significant noise reduction effect was selected. According to the measured results, compared with an equidistant impeller of the same size, the semi-cancellation noise of the 3D-printed unequally spaced impeller decreased from 64dB to 62.9dB, and the operating noise decreased from 64dB to 63.4dB. Overall, the noise reduction effect is significant.

[0089] Finally, it should be noted that the above embodiments are only for illustrating the present invention and not for limiting the present invention. Although the present invention has been described in detail with reference to the embodiments, those skilled in the art should understand that various combinations, modifications, or equivalent substitutions of the technical solutions of the present invention do not depart from the spirit and scope of the technical solutions of the present invention and should be covered within the protection scope of the present invention.

Claims

1. An impeller, characterized in that, include: Multiple blades, the multiple blades are arranged in a ring, and the multiple blades are non-uniformly distributed in the circumferential direction of the impeller; The included angle between two adjacent blades is obtained by modulating the position angle of the first blade in the impeller using a preset sine function, so that all the blades are periodically distributed along the circumference of the impeller.

2. The impeller according to claim 1, characterized in that, The sine function is: memb_v=(idx1-1)×(360 / 60)+10×sin(RADIANS((idx1-1)×6×3))+lead_v; In this context, the rotation direction of the impeller is taken as the positive direction. The first blade is defined as the blade that intersects the positive direction of the impeller's central axis, and the position angle of the first blade is defined as 0 degrees. memb_v is the position angle of the i-th blade. idx1 is the number of the i-th blade, idx1=1,2,3,…,60. lead_v is the position angle of the first blade. RADIANS is a function that converts angles into radians.

3. The impeller according to any one of claims 1 to 2, characterized in that, The impeller includes an upper plate, a lower plate, and a middle plate. The upper plate, the middle plate, and the lower plate are arranged sequentially along the axial direction of the middle plate. The middle plate is used to mount the motor. Multiple blades are arranged between the upper plate and the middle plate, and between the middle plate and the lower plate.

4. The impeller according to claim 3, characterized in that, Along the radial outward direction of the central disk, the blade has a first arc segment and a second arc segment; The outer diameter of the plurality of blades arranged between the upper plate and the middle plate, and between the middle plate and the lower plate, formed by the first arc segment, is d1; the outer diameter of the plurality of blades arranged between the upper plate and the middle plate, and between the middle plate and the lower plate, formed by the second arc segment, is d2. The ratio of d1 to d2 is 1 to 4.

5. The impeller according to claim 4, characterized in that, The inlet angle of the first arc segment is β1a, the outlet angle of the first arc segment is β1b, the inlet angle of the second arc segment is β2a, and the outlet angle of the second arc segment is β2b. Wherein, the value of β1a is in the range of 60 degrees to 70 degrees, the value of β1b is equal to the value of β2a, the value range of both β1b and β2a is 120 degrees to 130 degrees, and the value range of β2b is 160 degrees to 170 degrees.

6. The impeller according to claim 4, characterized in that, The ratio of the chord length of the first arc segment to the chord length of the second arc segment is 2 to 3.

7. The impeller according to claim 3, characterized in that, The inner diameter of the inner periphery of both the upper plate and the lower plate is the first inner diameter; The inner peripheral edges of the plurality of blades arranged between the upper disk and the middle disk, and between the middle disk and the lower disk, form a second inner diameter; Wherein, the second inner diameter is smaller than the first inner diameter.

8. The impeller according to claim 3, characterized in that, The outer diameter of the outer periphery of both the upper plate and the lower plate is the first outer diameter; The outer peripheral edges of the plurality of blades arranged between the upper disk and the middle disk, and between the middle disk and the lower disk, form a second outer diameter; Wherein, the second outer diameter is smaller than the first outer diameter.

9. The impeller according to claim 3, characterized in that, The middle plate is provided with a mounting platform in the middle, which protrudes towards the upper plate. The mounting platform is used to install and accommodate at least part of the structure of the motor.

10. The impeller according to claim 9, characterized in that, Along the circumference of the central plate, the mounting platform is provided with a plurality of air passage holes along its axial direction.

11. The impeller according to claim 3, characterized in that, The impeller also includes a bushing, which is disposed on the central disk and fixedly connected to the central disk. The bushing is used to fix the relative position of the impeller and the motor shaft of the motor.

12. The impeller according to claim 11, characterized in that, The blade, the upper disk, the lower disk, the middle disk, and the bushing are configured as an integrally formed structure; Alternatively, the blade, the upper disk, the lower disk, the middle disk, and the bushing are configured as separate fixed connections.

13. A centrifugal fan, characterized in that, It includes a volute and an impeller as described in any one of claims 1 to 12, wherein the impeller is disposed within the volute.

14. A range hood, characterized in that, It includes a frame and the centrifugal fan as described in claim 13, wherein the centrifugal fan is installed within the frame.

Images