A dehumidifier impeller and a dehumidifier

Abstract

This application provides a dehumidifier impeller and a dehumidifier, wherein the dehumidifier impeller includes: a hub, through which a motor shaft is connected; a plurality of fan blades, one end of which is fixed to the hub and arranged around the edge of the hub; and a guide ring, which is fixedly connected to the other end of the fan blades relative to the hub, through which air is drawn into the dehumidifier impeller and flows out through the fan blades; wherein the fan blades are unevenly distributed around the edge of the hub, resulting in different angles and spacings between the fan blades, thereby reducing the noise peak when the dehumidifier impeller rotates. This application breaks periodic noise, disperses airflow pulses, and reduces noise peaks. The guide ring optimizes airflow distribution, reduces separation vortices, and improves aerodynamic efficiency. The two ends of the fan blades are fixed to the hub and the guide ring, forming a support structure, enhancing rigidity and reducing vibration, achieving synergistic optimization of noise reduction and efficiency.

Description

Technical Field

[0001] This application relates to the field of dehumidification technology, specifically to a dehumidifier impeller and a dehumidifier. Background Technology

[0002] A dehumidifier is an electrical appliance used to reduce the humidity of ambient air. It uses technologies such as condensation, adsorption, or electrochemistry to convert water vapor in the air into liquid water, which is then discharged, thereby regulating indoor humidity. Dehumidifiers have wide applications in homes, industries, and commercial settings. They can effectively inhibit mold growth, protect electronic devices from moisture damage, and significantly improve air quality, creating a healthier and more comfortable living and working environment for users.

[0003] In existing technologies, traditional condensing dehumidifiers use a compressor to drive refrigerant circulation, cooling the air below the dew point to achieve dehumidification. The noise primarily comes from three sources: mechanical vibration noise from the compressor, fluid dynamic noise from the refrigerant in the piping, and aerodynamic noise from the high-speed fan. This noise pollution is particularly severe when the equipment is running at night or in quiet environments, significantly impacting the user experience. While some manufacturers have achieved some noise reduction by adding sound insulation or improving the compressor's suspension, this often comes at the cost of sacrificing heat dissipation efficiency or increasing the equipment's size.

[0004] Therefore, existing technologies still need to be improved and developed. Utility Model Content

[0005] In view of the shortcomings of the prior art, the purpose of this invention is to provide a dehumidifier impeller and a dehumidifier, which aims to solve the noise problem of dehumidifiers in the prior art.

[0006] The technical solution to the above-mentioned technical problems in this application is as follows:

[0007] A dehumidifier impeller, wherein the dehumidifier impeller comprises:

[0008] Hub, through which the dehumidifier impeller is connected to the motor shaft;

[0009] A plurality of fan blades, one end of which is fixed to the hub and the fan blades are arranged around the edge of the hub;

[0010] A guide ring is fixedly connected to the other end of the fan blade relative to the hub. Air is drawn into the dehumidifier impeller from the guide ring and flows out through the fan blade.

[0011] The fan blades are unevenly distributed around the edge of the hub, resulting in different angles and spacing between the fan blades, in order to reduce the noise peak when the dehumidifier impeller rotates.

[0012] The dehumidifier impeller has a fan blade with an arc-shaped cross-section along its axial direction, including a first end facing the outside of the dehumidifier impeller and a second end facing the inside of the dehumidifier impeller. Based on the position of the fan blade on the hub, the angles of the first end and the second end with respect to the tangent change, so that the angles and spacing between the fan blades are different, thereby reducing the noise peak when the dehumidifier impeller rotates.

[0013] The dehumidifier impeller, wherein the included angle between the two fan blades satisfies the following condition:

[0014]

[0015] Where i is the number of fan blades arranged around the hub, θ i Let be the angle between the i-th fan blade and the (i+1)-th fan blade. The angle between the i-th fan blade and the (i+1)-th fan blade when the fan blades are evenly arranged around the hub is Δφ, and m are modulation parameters.

[0016] The dehumidifier impeller, wherein the fan blades are subject to the following constraints to meet the balance requirements of the fan blades:

[0017]

[0018] Where, θ z Let be the angle between the z-th fan blade and the (z+1)-th fan blade.

[0019] The dehumidifier impeller, wherein the value is 1.2 and the value is 3.

[0020] The dehumidifier impeller has 51 fan blades arranged around the hub, with the first end at an angle of 149.7° to the tangent and the second end at an angle of 67.5° to the tangent.

[0021] The dehumidifier impeller, wherein the hub is a circular hub, and the wrap angle of the fan blades relative to the center of the hub is 3.3°.

[0022] The dehumidifier impeller, wherein the ratio of the radius of the second end relative to the center of the hub to the radius of the first end relative to the center of the hub in the fan blades is 0.88.

[0023] The dehumidifier impeller has a hub that protrudes axially to form a closed frustum, and the dehumidifier impeller is connected to the motor shaft through the frustum.

[0024] A dehumidifier comprising a dehumidifier impeller as described above.

[0025] The beneficial effects of this application are as follows:

[0026] This application discloses a dehumidifier impeller and a dehumidifier, comprising: a hub, through which the dehumidifier impeller is connected to a motor shaft; a plurality of fan blades, one end of which is fixed to the hub and arranged around the edge of the hub; and a guide ring, which is fixedly connected to the other end of the fan blades relative to the hub, through which air is drawn into the dehumidifier impeller and flows out through the fan blades. The fan blades are unevenly distributed around the edge of the hub, resulting in different angles and spacings between the blades, thereby reducing the noise peak value when the dehumidifier impeller rotates. In the technical solution of this application, the non-uniformly distributed fan blade layout effectively breaks the periodic noise generated by traditional equidistant fan blades, disperses airflow pulses, and reduces noise peak values ​​in specific frequency bands, dispersing noise energy across a wider frequency band. The synergy between the guide ring and the fan blades ensures a smooth intake airflow, optimizes the airflow distribution in the flow channel, reduces airflow separation and vortex phenomena, and improves the aerodynamic efficiency of the impeller while maintaining airflow volume. The fan blades are fixedly connected to the hub and guide ring at both ends, forming a stable triangular support structure. The guide ring, acting as a ring-shaped reinforcement, significantly improves the overall structural rigidity of the component, while the non-uniform load distribution effectively reduces the risk of resonance and decreases the vibration amplitude during operation. The dehumidifier impeller designed in this application can directly replace traditional dehumidifier impellers without altering the overall structure of the dehumidifier. It is suitable for dehumidifier products of different specifications and power levels and is compatible with various motor drive systems. While maintaining the basic functions of the dehumidifier impeller, this application achieves synergistic optimization of noise reduction performance and aerodynamic efficiency, providing an effective technical solution for improving the user experience of dehumidifier products. Attached Figure Description

[0027] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art 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 the structures shown in these drawings without creative effort.

[0028] Figure 1 This is a three-dimensional structural diagram of the dehumidifier impeller described in this application;

[0029] Figure 2 This is a schematic diagram comparing the dehumidifier impeller before and after adjustment as described in this application;

[0030] Figure 3 This is a front view of the dehumidifier impeller described in this application;

[0031] Figure 4This is an enlarged schematic diagram showing the angle between the first and second ends of the dehumidifier impeller described in this application;

[0032] Figure 5 This is a schematic diagram of the impeller wrap angle of the dehumidifier described in this application;

[0033] Figure 6 A comparison of the fan spectrum of the dehumidifier before and after optimization as described in this application;

[0034] The attached diagram lists the components represented by each number as follows:

[0035] Hub 100, fan blade 200, guide ring 300, first end 201 and second end 202. Detailed Implementation

[0036] This application provides a dehumidifier impeller and a dehumidifier. To make the objectives, technical solutions, and effects of this invention clearer and more explicit, the invention is further described in detail below. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.

[0037] To make the objectives, technical solutions, and effects of this invention clearer and more explicit, the invention is further described in detail below. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.

[0038] Furthermore, unless otherwise specified in the text, "a" and "described" can refer to a single or multiple items. If the embodiments of this invention involve descriptions such as "first," "second," etc., these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of indicated technical features. Therefore, a feature defined with "first" or "second" can explicitly or implicitly include at least one of those features. Additionally, the technical solutions of various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this invention.

[0039] In existing technologies, traditional condensing dehumidifiers use a compressor to drive refrigerant circulation, cooling the air below the dew point to achieve dehumidification. The noise primarily comes from three sources: mechanical vibration noise from the compressor, fluid dynamic noise from the refrigerant in the piping, and aerodynamic noise from the high-speed fan. This noise pollution is particularly problematic when the equipment is running at night or in quiet environments, severely impacting the user experience. While some manufacturers have achieved some noise reduction by adding sound insulation or improving the compressor's suspension, this often comes at the cost of sacrificing heat dissipation efficiency or increasing the equipment's size.

[0040] In view of the above-mentioned problems in the prior art, this application provides a dehumidifier impeller and a dehumidifier, wherein the dehumidifier impeller includes a hub 100, a plurality of fan blades 200 and a guide ring 300.

[0041] In one feasible embodiment of this application, such as Figure 1 As shown, the dehumidifier impeller is interference-fitted to the motor shaft 110 via the hub 100, ensuring stable power transmission while effectively suppressing radial runout during operation. Several fan blades 200 are arranged asymmetrically radially along the circumference of the dehumidifier impeller, breaking the noise generation pattern of traditional symmetrical fan blades and effectively dispersing noise energy. One end of each fan blade 200 is fixed to the hub 100, and the other end is connected to the inner edge of the guide ring 300. In a feasible embodiment of this application, each fan blade 200 is integrally connected to the outer edge of the hub 100 and the inner edge of the guide ring 300 through injection molding. This integral molding manufacturing process ensures the reliability of the connection between components and avoids imbalance problems that may be caused by assembly errors. In another feasible embodiment of this application, each fan blade 200 is interference-fitted to the outer edge of the hub 100 and the inner edge of the guide ring 300, ensuring the reliability of power transmission and realizing a stable structure of hub-impeller-guide ring. The synergistic effect among the three enhances the dynamic rigidity of the overall structure and reduces the vibration amplitude during high-speed operation. This application, through its tight connection structure, eliminates the connection gaps present in traditional assembly methods, effectively reducing eddy noise generated when airflow passes through these gaps. This achieves synergistic optimization of aerodynamic performance, noise control, and structural strength, providing an effective solution for improving the performance of dehumidifiers. The guide ring 300 serves as an airflow guiding component, drawing air into the dehumidifier impeller from the guide ring 300 and allowing it to flow out through the fan blades 200, forming a continuous and stable airflow channel. The guide ring 300 also provides additional structural reinforcement to the entire dehumidifier impeller through its annular structure, improving the reliability of the dehumidifier impeller. Simultaneously, the annular structure of the guide ring 300 provides circumferential constraint to the fan blades 200, effectively suppressing vibration deformation during high-speed rotation.

[0042] In one feasible embodiment of this application, each fan blade 200 is fixedly connected to the outer edge of the hub 100 and the inner edge of the guide ring 300 by a reinforcing rib structure. The reinforcing rib forms a triangular support structure at the root of the fan blade, which enables the fan blade to maintain shape stability under aerodynamic loads and significantly improves the bending strength and deformation resistance of the fan blade.

[0043] Specifically, such as Figure 1As shown, the fan blades 200 are non-uniformly distributed along the circumference of the hub 100. By precisely calculating the installation angle of each fan blade 200 and the spacing between adjacent fan blades 200, a specific phase difference is formed among the fan blades 200. This unique asymmetrical layout effectively disrupts the periodic pressure pulsations generated by traditional uniformly distributed fan blades, causing the pressure fluctuations generated by each fan blade 200 during rotation to cancel each other out. This redistributes the noise energy originally concentrated in a specific frequency band to a wider frequency range, thereby significantly reducing the noise peak generated in a specific frequency band when the wind turbine rotates, while maintaining good aerodynamic performance. The connection relationship between the components has been optimized, achieving the optimal configuration of the airflow path while ensuring structural strength, providing a quieter and more efficient solution.

[0044] Furthermore, in the above embodiments, such as Figure 3 As shown, the fan blade 200 has an arc-shaped structure with a specific curvature along the axial section of the dehumidifier impeller. The arc-shaped section can more effectively guide the airflow and reduce airflow separation on the fan blade surface. The fan blade 200 includes a first end 201 facing the outer side of the dehumidifier impeller and a second end 202 facing the inner side of the dehumidifier impeller. The first end 201 is fixedly connected to the inner edge of the guide ring 300. The two ends of the fan blade 200 are fixedly connected to the guide ring 300 and the hub 100, respectively, forming a stable triangular support structure and enhancing the overall rigidity.

[0045] Specifically, in one embodiment of this application, such as Figure 2As shown, the darker areas represent uniformly distributed fan blades, while the lighter areas represent optimized, non-uniformly distributed fan blades. The angle θ is the angle between any two adjacent fan blades 200 in the same arrangement. Based on the position of the fan blades 200 on the hub 100, the angles of the first end 201 and the second end 202 with the tangent change, resulting in different angles and spacings between the fan blades 200 in the dehumidifier impeller of this application compared to an impeller with uniformly arranged blade spacing and angles. This asymmetrical layout effectively disperses noise energy and reduces the noise peak during dehumidifier impeller rotation by disrupting the periodicity of noise. The structural features of the fan blades 200 employ aerodynamic optimization design. The cross-section of the fan blades 200 is airfoil-shaped, with a noticeably thickened area in the middle that gradually thins towards the edges, forming a streamlined profile. Therefore, the connection between the root of each fan blade 200 and the hub 100 is a gradually thickened design, forming a smooth stress transition area. This design ensures connection strength while avoiding stress concentration. This overall structural layout achieves a dual improvement in noise reduction and structural reliability without adding extra components. The top of the fan blade 200 maintains a continuous curvature connection with the inner edge of the guide ring 300. The optimization of the relationship between the guide ring 300, the fan blade 200, and the hub 100, and the matching of the arcuate profile of the fan blade 200 with the inner edge of the guide ring 300, makes the airflow transition smoother and reduces the generation of vortices.

[0046] Furthermore, in one feasible embodiment of this application, such as Figure 4 As shown, the angle between the i-th fan blade and the (i+1)-th fan blade satisfies the following condition:

[0047]

[0048] Where i is the number of fan blades arranged around the hub 100, θ i Let be the angle between the i-th fan blade and the (i+1)-th fan blade. The angle between the i-th fan blade and the (i+1)-th fan blade when the fan blades are evenly arranged around the hub 100 is Δφ, and m are modulation parameters.

[0049] Specifically, based on Figure 1The dehumidifier impeller structure shown in this application utilizes a sinusoidal modulation of the installation angle of each fan blade 200 to create a periodic variation in the blade spacing. Compared to a uniformly distributed blade arrangement, the fan blades in this dehumidifier impeller form a specific phase difference distribution, optimizing the spatial arrangement. The modulated fan blades 200 maintain their original connection with the hub 100 and the guide ring 300, ensuring the overall structural reliability remains unaffected. Furthermore, by breaking the fixed noise frequency of the traditional uniformly distributed fan blades 200, the noise energy is dispersed over a wider frequency band, significantly reducing the peak rotational noise. Sinusoidal modulation only changes the circumferential installation angle of the fan blades. By mathematically modeling and modulating the spatial distribution of the fan blades 200, the dehumidifier's outlet noise spectrum is smoother and the auditory experience is more comfortable without altering the hardware structure. This design is fully compatible with existing technologies and can be directly applied to traditional impeller molds without additional processing costs. Meanwhile, the sinusoidal modulation method achieves noise reduction while essentially maintaining the original aerodynamic performance, with minimal loss of airflow and pressure. Overall, this technology optimizes the spatial distribution of the fan blades through precise mathematical modeling, achieving a significant improvement in noise performance without altering the hardware structure, thus providing users with a better experience.

[0050] Furthermore, in the above embodiments, the fan blade 200 is subject to the following constraints to meet the balance requirements of the fan blade:

[0051]

[0052] After trigonometric transformation,

[0053]

[0054] Conclusion:

[0055]

[0056] Where, θ z The angle between the z-th fan blade and the (z+1)-th fan blade means that the setting of a single fan blade in the dehumidifier impeller described in this application is not only limited by the adjacent fan blades, but also takes into account the angle settings of all other fan blades, so as to ensure that all fan blades in the dehumidifier impeller work together to achieve a noise reduction effect.

[0057] Specifically, the technical solution provided in this application establishes a dynamic balance model of the fan blade system through trigonometric function operations. The core of this mathematical model lies in using trigonometric identities to transform the complex force situation of the fan blades into solvable equilibrium equations. The formula derivation process first establishes a relationship with θ... iThe relationship between the cosine and sine functions of the angle (2), through trigonometric transformation (3), finally yields the tangent function expression with clear physical meaning. The installation angle θ of each fan blade 200... i Satisfying the derived equilibrium condition (4), the phase difference between all the fan blades 200 is controlled by trigonometric function relationships, and the system as a whole satisfies the dynamic equilibrium equations of centrifugal force vector sum (∑F=0) and torque sum (∑M=0) to achieve equilibrium. When the fan blades 200 rotate, the radial forces generated by all the fan blades 200 cancel each other out, so no net unbalanced force is generated when the wind turbine rotates, preventing bearing wear and machine vibration caused by unidirectional force. In addition, the centrifugal torques generated by each fan blade 200 are balanced with each other, avoiding the swaying caused by torque imbalance of the wind turbine, and ensuring dynamic stability during rotation. This design method based on mathematical modeling has significant advantages over traditional empirical design, ensuring that the force on each fan blade 200 is evenly distributed, avoiding local stress concentration, reducing noise while reducing the mechanical wear of the fan blades 200, and extending the service life of the fan blades 200. By achieving dynamic balance during rotation, the vibration and noise generated by the mechanical movement of the fan blades 200 during rotation are reduced, while ensuring the stability of the system during high-speed operation.

[0058] Furthermore, in another embodiment of this application, the modulation parameter Δφ in formula (4) is 1.2, and m is 3. These two key parameters work together to achieve the optimized design of the fan blade system. Structurally, the connection angle between the first end 201 of the fan blade 200 and the guide ring 300, and the fitting angle between the second end 202 and the hub 100, are both controlled by a unified mathematical relationship, forming a closed-loop constraint chain. This design, through a specific combination of parameters, makes the angle parameters at both ends of each fan blade 200 interconnected, ensuring that the connection angle between the first end 201 and the guide ring 300, and the fitting angle between the second end 202 and the hub 100, are always in the optimal matching state, ensuring that the system achieves optimal fluid guidance characteristics while satisfying mechanical balance.

[0059] Specifically, θ zThe angle parameter between the z-th and z+1-th fan blades directly affects the fluid guidance characteristics of a single fan blade 200, the airflow coupling effect between adjacent fan blades 200, and the torque balance of all fan blades 200 in the overall system. During modulation amplitude optimization, on the one hand, Δφ = 1.2 balances the noise reduction requirements of non-uniform distribution with the maintenance of structural strength, keeping the installation angle variation of the fan blades 200 within the optimal range. While ensuring the noise reduction effect of the non-uniform distribution of the fan blades 200, it avoids stress concentration problems caused by excessive angle differences, maintaining structural reliability. On the other hand, the integer value of m = 3 is based on acoustic optimization principles. Through third harmonic modulation, the single-frequency noise generated by the traditional uniform fan blades 200 is dispersed into broadband noise with the third harmonic as its core, effectively reducing the noise energy density in the human ear-sensitive frequency band (800-2000Hz). Third harmonic modulation makes the noise spectrum exhibit wide bandwidth and low peak values, resulting in a smoother spectrum. Furthermore, the fan blades 200 are arranged in a symmetrical distribution with 3 cycles per revolution, which facilitates angle calibration and production inspection during mold processing, significantly improving the feasibility of the manufacturing process and increasing production efficiency and product consistency.

[0060] Furthermore, in another feasible embodiment of this application, such as Figure 4As shown, 51 fan blades 200 are arranged in a three-dimensional spatial array around the hub 100. The leading and trailing edges of each fan blade 200 form a continuous spatially twisted surface, optimizing the airflow angle of attack. The spatially twisted fan blade surface makes the airflow pressure distribution along the spanwise direction more uniform, reducing end vortex losses. The 51 fan blades 200 are periodically distributed in the circumferential direction with a phase parameter of m=3. The angle between the first end 201 and the tangent is 149.7°, and the angle between the second end 202 and the tangent is 67.5°. These two key angle parameters form a self-compensating mechanism through a balance equation. The 149.7° guide angle of the first end 201 of the fan blade 200 forms a progressive airflow channel with the inner edge of the guide ring 300, effectively reducing intake turbulence. The connection angle between the second end 202 and the hub 100 is enhanced by a gradually thickened design to increase structural strength and bending stiffness, forming a stable triangular support system. The 51 fan blades 200, under a phase control parameter of m=3, form 17 groups of characteristic units. Each group contains 3 fan blades 200 distributed with a specific phase difference, maintaining overall mass symmetry while dispersing noise energy through third harmonic modulation. A 149.7° guide angle allows the intake airflow to accelerate smoothly along the curved surface of the fan blades 200, reducing boundary layer separation losses and enhancing aerodynamic efficiency. A 67.5° hub 100 connection angle optimizes the torque transmission path, decomposing centrifugal force into axial and tangential components, reducing the radial load on the hub 100 bearing, and thus suppressing vibration. The main noise frequency generated by the 51 fan blades 200 under m=3 modulation shifts, effectively avoiding frequencies sensitive to the human ear and achieving noise reconstruction. All structural optimizations are completed without altering the basic connection method, demonstrating a synergistic improvement in aerodynamic, acoustic, and mechanical performance, while maintaining consistent airflow performance.

[0061] Furthermore, in another embodiment of this application, the hub 100 is a circular hub, and the wrap angle of the fan blade 200 relative to the center of the hub 100 is 3.3°. The wrap angle is the spatial angle between the centerline of the root of a single fan blade 200 and the radial reference line of the hub 100, that is, the angle formed by connecting the first end 201 and the second end 202 of the fan blade 200 to the rotation center, essentially a dynamic compensation angle formed by geometric pre-setting during the installation of the fan blade 200. Structurally, each fan blade 200 surrounds the central angle range occupied by the centerline of the hub 100, that is, the central angle between the projection points of the air intake edge and the air exhaust edge of each fan blade 200 on the circumference of the hub 100 is 3.3°. This specific wrap angle design achieves multiple optimization effects through innovative structural arrangement.

[0062] Specifically, the contact surface between the root of the fan blade 200 and the hub 100 adopts a bidirectional involute curved surface fit, with the middle part of the fit area thickened and the sides gradually thinning. This gradual structure ensures both connection strength and smooth load transfer. The 3.3° wrap angle forms a wedge fit with the positioning groove of the hub 100, reasonably dispersing centrifugal force tangentially and radially, reducing stress concentration and making the connection more stable. In terms of aerodynamic performance, the 3.3° wrap angle allows the fan blade 200 to naturally form a forward-leaning airflow angle after installation, allowing the airflow to adhere more smoothly to the curved surface of the fan blade 200 and reducing flow separation losses. Simultaneously, the 149.7° fit angle with the guide ring 300 forms a spatial torsional flow channel, creating a stable dynamic balance system of hub-fan blade-guide ring, generating a self-stabilizing effect during rotation. In terms of structural layout, the 3.3° wrap angle ensures that the 51 fan blades 200 are arranged uniformly and compactly in the circumferential direction, forming a non-radial force transmission path and decomposing the centrifugal force into tangential and radial components. The profile of each fan blade 200 maintains a continuous spatial curved surface transition from the hub 100 to the guide ring 300. The distance between the air inlet edge and the air outlet edge on the circumference of the hub 100 is calculated to ensure that an optimal airflow channel is formed between adjacent fan blades 200. This arrangement ensures sufficient flow area while avoiding airflow interference or flow separation. The smooth transition of airflow is achieved through precise wrap angle control. The wrap angle allows the fan blades 200 to achieve optimal arrangement within a limited circumferential space, avoiding airflow interference caused by overly dense arrangement and preventing flow separation caused by overly sparse arrangement. Furthermore, controlling the wrap angle parameter ensures an ideal phase relationship between adjacent fan blades 200, effectively suppressing periodic pressure pulsations that may occur during rotation. Moreover, this optimized wrap angle design enables the entire wind turbine system to achieve optimal flow coefficient and pressure recovery characteristics while maintaining structural compactness. Through the design of a 3.3° wrap angle, while maintaining the basic structural characteristics of the hub 100, the positioning accuracy of the fan blades 200 is ensured, and angle optimization achieves a synergistic improvement in aerodynamic performance and mechanical reliability.

[0063] Furthermore, in another feasible embodiment of this application, such as Figure 5 As shown, in the fan blade 200, the ratio of the radius of the second end 202 relative to the center of the hub 100 to the radius of the first end 201 relative to the center of the hub 100 is 0.88, creating a tapered three-dimensional flow channel space between the outer circumferential surface of the hub 100 and the inner edge of the guide ring 300. This tapered layout allows the radial cross-section of the fan blade 200 from the guide ring 300 to the hub 100 to present a continuous and smooth transition, which not only optimizes the radial flow path of the airflow but also achieves a gradient distribution of structural strength through a specific radius ratio, avoiding the generation of local vortices.

[0064] Specifically, the second end of the fan blade 200 is connected to the outer circumferential surface of the hub 100 using a three-dimensional curved surface fit. The connection area adopts a gradually changing thickness design, smoothly transitioning from the side of the hub 100 to the middle of the fan blade. This ensures a sufficient working radius at the end of the guide ring 300 to achieve good aerodynamic performance, while reducing centrifugal stress by appropriately shortening the radial dimension at the end of the hub 100. This specific proportional relationship optimizes the bending moment distribution at the root of the fan blade 200, making the load transfer more uniform, ensuring uniform distribution of contact pressure, and significantly reducing stress concentration at the connection point of the hub 100. The tapered geometry allows the airflow to maintain a smooth transition from the end of the guide ring 300 to the end of the hub 100 as it flows over the surface of the fan blade 200, ensuring airflow adhesion. This geometric construction optimizes the pressure distribution of the airflow on the fan blade surface and effectively suppresses boundary layer separation. In terms of structural reliability, the radius-to-radius ratio of 0.88 ensures that the fan blade 200 has sufficient rigidity to resist aerodynamic excitation forces, while optimizing the mass distribution reduces the dynamic imbalance of rotating components. This calculated geometric proportion achieves an optimal balance between aerodynamic efficiency, structural strength, and manufacturing feasibility while maintaining structural compactness.

[0065] Furthermore, in one feasible embodiment of this application, such as Figure 1 As shown, the dehumidifier impeller is connected to the motor shaft via the frustum, achieving an efficient connection between the dehumidifier impeller and the motor shaft. The center of the hub 100 extends axially to form a closed frustum structure. The top of the frustum is provided with an annular positioning stop, forming an axial positioning reference with the shoulder of the motor shaft, avoiding the imbalance caused by traditional key connections. In another feasible embodiment of this application, a reinforcing rib structure is arranged in the transition area between the root of the frustum and the main body of the hub 100. The reinforcing rib structure effectively disperses stress concentration during torque transmission and improves the fatigue life of the connection part. Overall, the closed frustum structure brings the overall center of gravity of the impeller closer to the motor support point, reducing the cantilever moment and thus significantly improving the dynamic stability during high-speed rotation.

[0066] Specifically, such as Figure 1 As shown, the frustum is a solid frustum. This solid frustum structure significantly improves the hub's rigidity modulus and effectively avoids common excitation frequency ranges. Simultaneously, the continuous mass distribution eliminates interface fretting in traditional assembled structures, reducing vibration noise. The solid structure has more regular modal shapes, and combined with the streamlined shape of the frustum transition zone, it greatly reduces periodic excitation during rotation, thus reducing airflow separation noise. Figure 6As shown, this design, while maintaining constant aerodynamic efficiency, not only eliminates abnormal noise in specific frequency bands but also reduces the overall noise level by approximately 0.6 dB. This noise reduction effect achieved through structural optimization has long-term stability and, compared to traditional soundproofing methods, can fundamentally solve the noise problem.

[0067] Furthermore, this application also provides a dehumidifier that includes the aforementioned dehumidifier impeller.

[0068] In summary, this application discloses a dehumidifier impeller and a dehumidifier, comprising: a hub, through which the dehumidifier impeller is connected to a motor shaft; a plurality of fan blades, one end of which is fixed to the hub and arranged around the edge of the hub; and a guide ring, which is fixedly connected to the other end of the fan blades relative to the hub, through which air is drawn into the dehumidifier impeller and flows out through the fan blades; wherein the fan blades are unevenly distributed around the edge of the hub, resulting in different angles and spacings between the fan blades, thereby reducing the noise peak when the dehumidifier impeller rotates. In the technical solution of this application, the non-uniformly distributed fan blade layout effectively breaks the periodic noise generated by traditional equidistant fan blades, disperses airflow pulses, reduces noise peaks in specific frequency bands, and distributes noise energy across a wider frequency band. The synergy between the guide ring and the fan blades ensures a smooth intake airflow, optimizes the airflow distribution within the flow channel, reduces airflow separation and vortex phenomena, and improves the aerodynamic efficiency of the impeller while maintaining airflow volume. The hub and guide ring are fixedly connected to both ends of the fan blades, forming a stable triangular support structure. The guide ring, acting as a ring-shaped reinforcement, significantly improves the overall structural rigidity of the component, while the non-uniform load distribution effectively reduces the risk of resonance and decreases vibration amplitude during operation. The impeller designed in this application can directly replace traditional impellers without altering the overall structure of the dehumidifier. It is suitable for dehumidifier products of different specifications and power levels and is compatible with various motor drive systems. While maintaining the basic functions of the impeller, this application achieves synergistic optimization of noise reduction performance and aerodynamic efficiency, providing an effective technical solution for improving the user experience of dehumidifier products.

[0069] It should be understood that the application of the present invention is not limited to the examples above. Those skilled in the art can make improvements or modifications based on the above description, and all such improvements and modifications should fall within the protection scope of the appended claims.

Claims

1. A dehumidifier fan wheel, characterized by, The dehumidifier impeller includes: Hub, through which the dehumidifier impeller is connected to the motor shaft; A plurality of fan blades, one end of which is fixed to the hub and the fan blades are arranged around the edge of the hub; A guide ring is fixedly connected to the other end of the fan blade relative to the hub. Air is drawn into the dehumidifier impeller from the guide ring and flows out through the fan blade. The fan blades are unevenly distributed around the edge of the hub, resulting in different angles and spacings between the fan blades, in order to reduce the noise peak when the dehumidifier impeller rotates.

2. The dehumidifier fan wheel of claim 1, wherein, The fan blades have an arc-shaped cross-section along the axial direction of the dehumidifier impeller, including a first end facing the outside of the dehumidifier impeller and a second end facing the inside of the dehumidifier impeller. Based on the position of the fan blades on the hub, the angles of the first end and the second end with respect to the tangent change, so that the angles and spacing between the fan blades are different, thereby reducing the noise peak when the dehumidifier impeller rotates.

3. The dehumidifier fan wheel of claim 2, wherein, The included angle between the two fan blades satisfies the following condition: Where i is the number of fan blades arranged around the hub, θ i Let be the angle between the i-th fan blade and the (i+1)-th fan blade. The angle between the i-th fan blade and the (i+1)-th fan blade when the fan blades are evenly arranged around the hub is Δφ, and m are modulation parameters.

4. The dehumidifier fan wheel of claim 3, wherein, The fan blades are subject to the following constraints to meet their balance requirements: where θ z is the angle between the zth and z+1th fan blades.

5. The dehumidifier fan wheel of claim 4, wherein, It takes the value 1.2 and the value 3.

6. The dehumidifier fan wheel of claim 4, wherein, Fifty-one fan blades are arranged around the hub, with the first end at an angle of 149.7° to the tangent and the second end at an angle of 67.5° to the tangent.

7. The dehumidifier fan wheel of claim 4, wherein, The hub is a circular hub, and the angle of the fan blade relative to the center of the hub is 3.3°.

8. The dehumidifier fan wheel of claim 7, wherein, In the fan blade, the ratio of the radius of the second end relative to the center of the hub to the radius of the first end relative to the center of the hub is 0.

88.

9. The dehumidifier fan wheel of claim 8, wherein, The center of the hub protrudes axially to form a closed truncated cone, and the dehumidifier impeller is connected to the motor shaft through the truncated cone.

10. A dehumidifier, characterized by It includes a dehumidifier impeller as described in any one of claims 1-9.

Images