Dehumidifier wind wheel and dehumidifier

Abstract

The invention provides a dehumidifier wind wheel and a dehumidifier, and the dehumidifier wind wheel comprises a hub which is connected with a motor shaft through the hub; one end of each fan blade is fixed on the hub, and the fan blades are arranged around the edge of the hub; the flow guide ring is fixedly connected with the other ends of the fan blades relative to the hub, and air is sucked into the dehumidifier wind wheel from the flow guide ring and flows out through the fan blades; wherein the fan blades are non-uniformly distributed around the edge of the hub, so that the angles and the distances between the fan blades are different, and the noise peak value during rotation of the dehumidifier wind wheel is reduced. Periodic noise is broken, airflow pulses are dispersed, and the noise peak value is reduced. The flow guide ring optimizes airflow distribution, reduces separation vortexes, and improves aerodynamic efficiency. The two ends of the fan blades are fixed to the hub and the flow guide ring to form a supporting structure, rigidity is enhanced, vibration is reduced, and collaborative optimization of noise reduction and efficiency is achieved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of dehumidification, in particular to a dehumidifier fan wheel and a dehumidifier. BACKGROUND

[0002] A dehumidifier is an electrical appliance used to reduce the humidity of the environment. It converts water vapor in the air into liquid water through condensation, adsorption or electrochemistry, etc., so as to achieve the purpose of adjusting indoor humidity. Dehumidifiers have wide application value in family, industry, commerce and other scenarios. They can not only effectively inhibit the growth of mold and protect electronic devices from moisture erosion, but also significantly improve air quality and create a healthier and more comfortable living and working environment for users.

[0003] In the prior art, traditional condensing dehumidification drives refrigerant circulation through a compressor to cool the air below the dew point to achieve dehumidification. The noise mainly comes from three aspects: one is the mechanical vibration noise of the compressor when it works; the second is the fluid dynamic noise of the refrigerant in the pipeline; the third is the aerodynamic noise generated by the high-speed fan. Especially when the equipment is running at night or in a quiet environment, such noise pollution seriously affects the user experience. Although some manufacturers have achieved certain noise reduction effect by adding sound insulation cotton or improving the suspension method of the compressor, but often at the cost of sacrificing the heat dissipation efficiency or increasing the size of the equipment.

[0004] Therefore, the prior art still needs to be improved and developed. SUMMARY

[0005] In view of the shortcomings of the prior art, the purpose of the present application is to provide a dehumidifier fan wheel and a dehumidifier, which aims to solve the noise problem of the dehumidifier in the prior art.

[0006] The technical solution of the present application to solve the above technical problems is as follows:

[0007] A dehumidifier fan wheel, wherein the dehumidifier fan wheel comprises:

[0008] a hub, the dehumidifier fan wheel is connected to the motor shaft through the hub;

[0009] a plurality of fan blades, one end of the fan blade is fixed on the hub, and the fan blade is arranged around the edge of the hub;

[0010] a flow guide ring, the flow guide ring is fixedly connected to the other end of the fan blade relative to the hub, air is sucked into the dehumidifier fan wheel from the flow guide ring and flows out through the fan blade;

[0011] wherein the fan blades are unevenly distributed around the edge of the hub, so that the angles and spacings between the fan blades are different, to reduce the noise peak value when the dehumidifier fan wheel rotates.

[0012] The dehumidifier fan wheel, wherein the fan blades are arc-shaped along the axial section of the dehumidifier fan wheel, including a first end facing the outside of the dehumidifier fan wheel and a second end facing the inside of the dehumidifier fan wheel, the angle of the first end and the second end with the tangent changes based on the position of the fan blades on the hub, so that the angle and spacing between the fan blades are different, reducing the noise peak when the dehumidifier fan wheel rotates.

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

[0014]

[0015] Wherein, i is the number of fan blades arranged around the hub, θ i is the included angle between the i-th fan blade and the i+1-th fan blade, is the included angle between the i-th fan blade and the i+1-th fan blade when the fan blades are uniformly arranged around the hub, and Δφ and m are modulation parameters.

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

[0017]

[0018] Wherein, θ z is the included angle between the z-th fan blade and the z+1-th fan blade.

[0019] The dehumidifier fan wheel, wherein the value of m is 1.2, and the value of n is 3.

[0020] The dehumidifier fan wheel, wherein 51 fan blades are arranged around the hub, the angle of the first end with the tangent is 149.7°, and the angle of the second end with the tangent is 67.5°.

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

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

[0023] The dehumidifier fan wheel, wherein the center of the hub is protruded along the axial direction to form a closed truncated cone, and the dehumidifier fan wheel is connected with the motor shaft through the truncated cone.

[0024] A dehumidifier, comprising the dehumidifier fan wheel as described above.

[0025] The beneficial effects of the present application are:

[0026] The application discloses a dehumidifier air wheel and a dehumidifier, which comprise a hub, the dehumidifier air wheel is connected with a motor shaft through the hub, a plurality of fan blades, one end of the fan blade is fixed on the hub, and the fan blade is arranged around the edge of the hub, and a flow guide ring, the flow guide ring is fixedly connected with the other end of the fan blade relative to the hub, air is sucked into the dehumidifier air wheel from the flow guide ring and flows out through the fan blade, wherein the fan blades are unevenly distributed around the edge of the hub, so that the angles and spacings between the fan blades are different, so as to reduce the noise peak value when the dehumidifier air wheel rotates. In the technical scheme of the application, the fan blade layout is unevenly distributed, the periodic noise generated by the traditional equidistant fan blades is effectively broken, the airflow pulse can be dispersed and the noise peak value of a specific frequency band can be reduced, the noise energy is dispersed to a wider frequency band. The cooperation of the flow guide ring and the fan blade ensures the smooth introduction of the inlet airflow, optimizes the distribution state of the airflow in the flow channel, reduces the airflow separation and vortex phenomenon, maintains the air volume and improves the aerodynamic efficiency of the air wheel. The two ends of the fan blade are fixedly connected with the hub and the flow guide ring respectively, forming a stable triangular support structure, the flow guide ring serves as a ring-shaped reinforcing piece and significantly improves the structural rigidity of the whole assembly, and the uneven load distribution effectively reduces the resonance risk and reduces the vibration amplitude during operation. The dehumidifier air wheel designed in the application can directly replace the traditional dehumidifier air wheel, without changing the overall structure of the dehumidifier, and is suitable for dehumidifier products of different specifications and power levels and compatible with various motor driving systems. While maintaining the basic function of the dehumidifier air wheel, the application realizes the cooperative optimization of the noise reduction performance and the aerodynamic efficiency, and provides an effective technical solution for improving the use experience of the dehumidifier product. BRIEF DESCRIPTION OF DRAWINGS

[0027] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the prior art, the following will briefly introduce the drawings needed to be used in the embodiments or prior art description. Obviously, the drawings in the following description only show some embodiments of the present application, and those skilled in the art can also obtain other drawings according to the structures shown in the drawings without any creative labor.

[0028] Figure 1 It is a schematic view of the three-dimensional structure of the dehumidifier air wheel described in the present application.

[0029] Figure 2 It is a comparison schematic view of the dehumidifier air wheel before and after modulation described in the present application.

[0030] Figure 3 It is a front view of the dehumidifier air wheel described in the present application.

[0031] Figure 4The angle amplification schematic view of the first end and the second end of the air wheel of the dehumidifier described in the application;

[0032] Figure 5 The angle amplification schematic view of the air wheel of the dehumidifier described in the application;

[0033] Figure 6 The air wheel frequency spectrum comparison before and after optimization of the air wheel of the dehumidifier described in the application;

[0034] In the drawings, the components represented by each reference numeral are listed as follows:

[0035] The hub 100, the fan blade 200, the flow guide ring 300, the first end 201, and the second end 202. DETAILED DESCRIPTION

[0036] The application provides a dehumidifier and an air wheel thereof. To make the purpose, technical solutions and effects of the application more clear and explicit, the application is further described in detail below. It should be understood that the specific embodiments described herein are only used to explain the application and not to limit the application.

[0037] To make the purpose, technical solutions and effects of the application more clear and explicit, the application is further described in detail below. It should be understood that the specific embodiments described herein are only used to explain the application and not to limit the application.

[0038] In addition, unless the article is specifically limited in the text, "one" and "the" can refer to a single or multiple. If the description of "first", "second" and the like is involved in the embodiments of the application, the description of "first", "second" and the like is only for the purpose of description, and cannot be understood as indicating or implying the relative importance of the indicated technical features or implicitly indicating the number of the indicated technical features. Therefore, the features limited by "first", "second" can explicitly or implicitly include at least one of the features. In addition, the technical solutions of each embodiment can be combined with each other, but it must be based on the realization of ordinary skilled in the art. When the combination of technical solutions appears contradictory or unachievable, it should be considered that the combination of technical solutions does not exist and is not within the protection scope required by the application.

[0039] In the prior art, the traditional condensing dehumidification drives the refrigerant circulation by the compressor to cool the air below the dew point to realize dehumidification. The noise mainly comes from three aspects: one is the mechanical vibration noise of the compressor when it works; the second is the fluid dynamic noise of the refrigerant in the pipeline; the third is the aerodynamic noise generated by the high-speed fan. Especially when the equipment runs at night or in a quiet environment, such noise pollution seriously affects the user experience. Although some manufacturers realize certain noise reduction effect by adding sound insulation cotton or improving the suspension method of the compressor, but often at the expense of heat dissipation efficiency or increase the size of the equipment.

[0040] Based on the above problems in the prior art, the application provides a dehumidifier air wheel and a dehumidifier.

[0041] In an embodiment of the application, as shown in Figure 1 The dehumidifier air wheel is connected to the motor shaft 110 through the hub 100 to ensure the stability of power transmission and effectively inhibit the radial runout during operation. The plurality of fan blades 200 are arranged in a non-symmetrical radial manner along the circumference of the dehumidifier air wheel, breaking the noise generation mode of the 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 flow guide ring 300. In an embodiment of the application, each fan blade 200 is integrally connected to the outer edge of the hub 100 and the inner edge of the flow guide ring 300 through an injection molding process. The integrated manufacturing process ensures the reliability of the connection between the components and avoids the imbalance problem caused by assembly errors. In another embodiment of the application, each fan blade 200 is connected to the outer edge of the hub 100 and the inner edge of the flow guide ring 300 through interference connection, ensuring the reliability of power transmission and realizing the stable structure of the hub-air wheel-flow guide ring. The synergistic effect between the three enhances the dynamic rigidity of the overall structure, reducing the vibration amplitude during high-speed operation. The application eliminates the connection gaps in the traditional assembly method through a tight connection structure, effectively reduces the vortex noise generated when air flows through these gaps, and realizes the synergistic optimization of aerodynamic performance, noise control and structural strength, providing an effective solution for performance improvement of the dehumidifier. The flow guide ring 300 serves as an air flow guide component. Air is sucked into the dehumidifier air wheel from the flow guide ring 300 and flows out through the fan blades 200, forming a continuous and stable air flow channel. The flow guide ring 300 also provides additional structural reinforcement for the entire dehumidifier air wheel through its annular structure, improving the reliability of the dehumidifier air wheel. At the same time, the annular structure of the flow guide ring 300 provides circumferential constraint for the fan blades 200, effectively inhibiting vibration deformation during high-speed rotation.

[0042] In an embodiment of the application, each fan blade 200 is fixedly connected to the outer edge of the hub 100 and the inner edge of the flow guide ring 300 through a reinforcing rib structure. The reinforcing rib forms a triangular support structure at the root of the fan blade, keeping the fan blade stable under the action of aerodynamic load and significantly improving the bending strength and deformation resistance of the fan blade.

[0043] Specifically, as shown in Figure 1As shown, the fan blades 200 are arranged in a non-uniform distribution in the circumferential direction of the hub 100. By precisely calculating the installation angle of each fan blade 200 and the spacing between adjacent fan blades 200, each fan blade 200 forms a specific phase difference. This unique asymmetric layout effectively destroys the periodic pressure pulsation generated by the traditional uniform distribution of fan blades, so that the pressure fluctuations generated by each fan blade 200 when rotating interfere with and cancel each other out. The noise energy originally concentrated in a specific frequency band is redistributed to a wider frequency range, thereby significantly reducing the noise peak generated by the wind wheel when rotating in a specific frequency band, while maintaining good aerodynamic performance. The connection relationship between each component is optimized to ensure structural strength while optimizing the configuration of the airflow path, providing a quieter and more efficient solution.

[0044] Further, in the above embodiment, as shown, Figure 3 The fan blade 200 has a specific curvature in the axial cross-section of the dehumidifier wind wheel. The arc-shaped cross-section can more effectively guide the airflow and reduce airflow separation on the surface of the fan blade. The fan blade 200 includes a first end 201 facing the outside of the dehumidifier wind wheel and a second end 202 facing the inside of the dehumidifier wind wheel. The first end 201 is fixedly connected to the inner edge of the flow guide ring 300, and the two ends of the fan blade 200 are fixedly connected to the flow 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 the present application, as shown, Figure 2As shown, the dark part is the uniformly distributed fan blade, and the light part is the non-uniformly distributed fan blade optimized in design. The angle θ is the included angle between every two adjacent fan blades 200 under the same arrangement. Based on the position of the fan blade 200 on the hub 100, the angle between the first end 201 and the second end 202 and the tangent changes, so that the angle and the spacing between the fan blades 200 in the dehumidifier fan wheel of the application are different from the wind wheel with uniformly arranged fan blade spacing and angle. This asymmetric layout effectively disperses noise energy and reduces the noise peak value when the dehumidifier fan wheel rotates by destroying the periodic characteristics of noise. The structural features of the fan blade 200 are aerodynamically optimized. The cross section of the fan blade 200 is airfoil-shaped, and the middle part of the fan blade 200 has a thickened area, which gradually thins towards the two side edges, forming a streamlined profile. Therefore, the root of each fan blade 200 and the connection of the hub 100 are designed to gradually thicken, forming a smooth stress transition area. Such a design not only ensures the connection strength, but also avoids stress concentration. This overall structural layout realizes the dual improvement of noise reduction effect and structural reliability without adding additional components. The top of the fan blade 200 is continuously curved and connected with the inner edge of the flow guide ring 300. The flow guide ring 300, the fan blade 200 and the hub 100 are optimized. The arc profile of the fan blade 200 cooperates with the inner edge of the flow guide ring 300 to make the air flow transition more smooth, reducing vortex generation.

[0046] Further, in one possible embodiment of the application, as shown in Figure 4 The included angle between the i-th fan blade and the i+1-th fan blade satisfies the condition:

[0047]

[0048] Wherein, i is the number of fan blades arranged around the hub 100, θ i is the included angle between the i-th fan blade and the i+1-th fan blade, is the included angle between the i-th fan blade and the i+1-th fan blade when the fan blades are uniformly arranged around the hub 100, and Δφ and m are modulation parameters.

[0049] Specifically, based on Figure 1The technical scheme of the application is characterized in that the installation angle of each said fan blade 200 is modulated by sine, so that the spacing between the fan blades is periodically changed. Compared with the uniformly distributed fan blades, the fan blades in the dehumidifier wheel form a specific phase difference distribution, and the spatial arrangement is optimized. The modulated said fan blade 200 keeps the original connection mode with the hub 100 and the flow guide ring 300, so as to ensure the reliability of the overall structure. The fixed noise frequency of the traditional uniformly distributed said fan blade 200 is broken, the noise energy is dispersed into a wider frequency band, and the peak value of the rotating noise is significantly reduced. The sine modulation only changes the circumferential installation angle of the fan blade, and the spatial distribution of the said fan blade 200 is modulated by mathematical modeling. Without changing the hardware structure, the noise spectrum of the dehumidifier is smoother, and the auditory experience is more comfortable. The design is fully compatible with the existing technology, and can be directly applied to the traditional wheel mold without additional processing cost. At the same time, the sine modulation method basically maintains the original aerodynamic performance while achieving the noise reduction effect, and the loss of air volume and air pressure is very small. Overall, the technology optimizes the spatial distribution of the fan blade through precise mathematical modeling, and significantly improves the noise performance without changing the hardware structure, so as to bring better user experience.

[0050] Further, in the above embodiment, the said fan blade 200 is subject to the following conditions to meet the balance requirement of the said fan blade:

[0051]

[0052] After trigonometric transformation,

[0053]

[0054] It is obtained that:

[0055]

[0056] Wherein, θ z The angle between the zth fan blade and the z+1th fan blade, that is, the setting of a single fan blade in the dehumidifier wheel of the application is not only limited by the adjacent fan blades, but also takes into account the angle setting of all other fan blades, so as to ensure that all fan blades in the dehumidifier wheel realize the noise reduction effect cooperatively.

[0057] Specifically, the technical scheme provided by the application establishes a dynamic balance model of the fan blade system through trigonometric function operation. The core of the mathematical model is to use trigonometric identity transformation to convert the complex fan blade stress condition into a solvable balance equation. The formula derivation process first establishes a relationship between θ iThe cosine and sine function relationship of angle (2) is derived into the tangent function expression with explicit physical meaning through the trigonometric transformation (3). The installation angle θ of each said fan blade 200 i The phase difference between all said fan blades 200 is controlled through the trigonometric function relationship to meet the derived balance condition (4), and the whole system meets the dynamic balance equation of the centrifugal force vector sum (∑F=0) and the moment sum (∑M=0) to reach the balance. When the said fan blades 200 rotate, the radial forces generated by all said fan blades 200 cancel each other out, so that no net unbalanced force is generated when the wind wheel rotates, preventing bearing wear and machine vibration caused by one-way force. In addition, the centrifugal moments generated by each said fan blade 200 are balanced with each other, avoiding the swing caused by the torque imbalance of the wind wheel, and ensuring the dynamic stability during rotation. This design method based on mathematical modeling has a significant advantage over traditional empirical design, ensuring that the stress of each said fan blade 200 is evenly distributed, avoiding local stress concentration, reducing mechanical wear of said fan blade 200 while reducing noise, and prolonging the service life of said fan blade 200. By achieving dynamic balance during rotation, the vibration and noise generated by the mechanical movement of said fan blade 200 during rotation are reduced, while the stability of the system during high-speed operation can be ensured.

[0058] Further, in another embodiment of the present application, the modulation parameter Δφ in formula (4) is 1.2, and m is 3. These two key parameters work together to achieve the optimal design of the fan blade system. In terms of structure, the connection angle of the first end 201 of the said fan blade 200 with the said flow guide ring 300 and the cooperation angle of the second end 202 with the said hub 100 are all regulated by the unified mathematical relationship, forming a closed loop constraint chain. This design, through specific parameter combination, makes the two end angle parameters of each fan blade 200 related to each other, ensuring that the connection angle of the first end 201 with the said flow guide ring 300 and the cooperation angle of the second end 202 with the said hub 100 are always in the optimal matching state, ensuring that the system meets the mechanical balance while achieving the best fluid guiding characteristics.

[0059] Specifically, θ zAs the angle parameter between the fan blade of the z-th piece and the fan blade of the z+1-th piece, it directly affects the fluid guiding characteristics of the single fan blade 200, the air flow coupling effect between adjacent fan blades 200, and the torque balance state of all fan blades 200 in the overall system. When the modulation amplitude is optimized, on the one hand, Δφ = 1.2 balances the non-uniform distribution of noise reduction demand and the maintenance of structural strength, so that the installation angle change of the fan blade 200 is controlled within the optimal range, while ensuring the non-uniform distribution of the fan blade 200 noise reduction effect, it avoids the stress concentration problem caused by too large angle difference, and maintains the structural reliability. On the other hand, the integer value of m = 3 is based on the principle of acoustic optimization, and through the third harmonic adjustment, the single frequency noise generated by the traditional uniform fan blade 200 is dispersed into a wide frequency noise with the third harmonic as the core, effectively reducing the noise energy density in the sensitive frequency band (800-2000Hz) of human ear, the third harmonic modulation makes the noise spectrum present the characteristics of wide frequency band and low peak value, and the spectrum is more smooth. In addition, the fan blade 200 layout forms a symmetrical distribution of every 3 periods, which is convenient for angle scaling and production detection during mold processing, significantly improves the feasibility of manufacturing process, and improves the production efficiency and product consistency.

[0060] Further, in another possible embodiment of the present application, as Figure 4As shown, 51 pieces of the fan blades 200 are arranged to form a three-dimensional spatial array structure around the hub 100. The leading edge and the trailing edge of each piece of the fan blade 200 form a continuous spatially twisted surface, which optimizes the angle of attack of the airflow. The spatially twisted fan blade surface makes the pressure distribution of the airflow along the span more uniform, reducing the end vortex loss. Among them, 51 pieces of the fan blades 200 are periodically distributed in the circumferential direction with a phase parameter m = 3. The angle between the first end 201 and the tangential direction is 149.7°, and the angle between the second end 202 and the tangential direction is 67.5°. The two key angle parameters form a self-compensation mechanism through a balance equation. The 149.7° flow guide angle of the first end 201 of the fan blade 200 forms a gradual airflow channel with the inner edge of the flow guide ring 300, effectively reducing the intake turbulence; the connection angle between the second end 202 and the hub 100 is designed to gradually thicken to enhance the structural strength and bending stiffness, forming a stable triangular support system. 51 pieces of the fan blades 200 form 17 characteristic units under the phase control parameter m = 3, each group containing 3 pieces of the fan blades 200 distributed with a specific phase difference, which not only maintains the overall mass symmetry, but also disperses noise energy through three harmonic modulation. The 149.7° flow guide angle makes the intake airflow accelerate smoothly along the surface of the fan blade 200, reducing the boundary layer separation loss and enhancing the aerodynamic efficiency. The 67.5° connection angle of the hub 100 optimizes the torque transmission path, decomposes the centrifugal force into axial and tangential components, reduces the radial load of the hub 100 bearing, and thus suppresses vibration. The main noise frequency generated by 51 pieces of the fan blades 200 under m = 3 modulation is shifted, effectively avoiding the sensitive frequency band of the human ear and achieving noise reconstruction. While maintaining the air volume performance. All structural optimizations are completed without changing the basic connection method, reflecting the synergistic improvement of aerodynamic, acoustic and mechanical performance.

[0061] Further, in another embodiment of the present application, the hub 100 is a circular hub, and the included angle of the fan blade 200 relative to the center of the hub 100 is 3.3°. The included angle is the spatial angle between the root center line of the fan blade 200 and the radial reference line of the hub 100, that is, the included angle formed by the first end 201 and the second end 202 of the fan blade 200 after connecting to the rotation center. In essence, it is a dynamic compensation angle formed by geometric preposition during installation of the fan blade 200. In terms of structure, the central angle range occupied by each fan blade 200 around the hub 100 center line, that is, the projection points between the air inlet edge and the air outlet edge of each fan blade 200 on the circumference of the hub 100 form a central angle of 3.3°. This specific included angle design achieves multiple optimization effects through innovative structural arrangement.

[0062] Specifically, the contact surface of the hub 100 and the root of the fan blade 200 adopts a two-way involute curved surface matching, the middle part of the matching area is thickened, and the two sides are gradually thinned. Such a gradual change structure not only ensures the connection strength, but also realizes the smooth transmission of load. Through the wedge-shaped matching formed by the wrap angle of 3.3° and the positioning groove of the hub 100, the centrifugal force is reasonably dispersed along the tangential and radial directions, the stress concentration phenomenon is reduced, and the connection is more stable. In terms of aerodynamic performance, the wrap angle of 3.3° makes the fan blade 200 naturally form a forward-leaning airflow attack angle after installation, so that the airflow is more smoothly attached to the curved surface of the fan blade 200, and the flow separation loss is reduced. At the same time, the matching angle of 149.7° between the flow guide ring 300 and the hub- fan blade- flow guide ring forms a spatial twist flow channel, forming a stable dynamic balance system, and generates a self-stabilizing effect when rotating. In terms of structural layout, the wrap angle of 3.3° makes the 51 fan blades 200 form a uniform and compact arrangement 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 remains a continuous spatial curved surface transition from the hub 100 to the flow guide ring 300, and the spacing of the inlet edge and the outlet edge on the circumference of the hub 100 is calculated to ensure that the adjacent fan blades 200 form the best airflow channel. This arrangement not only ensures sufficient flow area, but also avoids airflow interference or flow separation. Through the precise wrap angle control, the smooth transition of airflow is realized. The wrap angle makes the fan blade 200 achieve optimal arrangement in a limited circumferential space, which not only avoids airflow interference caused by over-dense arrangement, but also prevents flow separation caused by over-dense arrangement. Moreover, controlling the wrap angle parameter ensures that the adjacent fan blades 200 form an ideal phase relationship, effectively suppressing the periodic pressure pulsation that may occur during rotation. Furthermore, the optimized wrap angle design makes the entire wind turbine system maintain structural compactness while achieving optimal flow coefficient and pressure recovery characteristics. Through the design of the wrap angle of 3.3°, the positioning accuracy of the fan blade 200 is ensured while maintaining the basic structural characteristics of the hub 100, and the aerodynamic performance and mechanical reliability are improved through angle optimization.

[0063] Further, in another possible embodiment of the present application, as shown in Figure 5 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, and a tapered three-dimensional flow channel space is formed between the outer circumferential surface of the hub 100 and the inner edge of the flow guide ring 300. Such a tapered layout makes the radial cross section of the fan blade 200 from the flow guide ring 300 to the hub 100 present a continuous smooth transition, not only optimizing the radial flow path of the airflow, but also achieving a gradient distribution of structural strength through a specific radius ratio, avoiding local vortex generation.

[0064] Specifically, the second end of the fan blade 200 is connected to the outer circumferential surface of the hub 100 by a three-dimensional curved surface, and the connection area is designed with a gradually changing thickness, smoothly transitioning from the hub 100 side to the middle of the fan blade, which not only ensures that the end of the guide ring 300 has sufficient working radius to obtain good aerodynamic performance, but also reduces the centrifugal stress by appropriately shortening the radial dimension of the hub 100 end. This specific proportional relationship optimizes the bending moment distribution at the root of the fan blade 200, making the load transfer more uniform and ensuring uniform distribution of contact pressure, significantly reducing stress concentration at the connection part of the hub 100. The tapered geometry allows the airflow to smoothly transition from the end of the guide ring 300 to the end of the hub 100 when flowing over the surface of the fan blade 200, ensuring airflow adhesion. This geometric configuration optimizes the pressure distribution of the airflow on the surface of the fan blade, effectively suppressing the boundary layer separation phenomenon. In terms of structural reliability, a radius ratio design of 0.88 ensures that the fan blade 200 has sufficient rigidity to resist aerodynamic excitation forces, while optimizing the mass distribution to reduce the dynamic imbalance of rotating parts. This calculated geometric proportion balances the aerodynamic efficiency, structural strength, and manufacturing feasibility while maintaining structural compactness.

[0065] Further, in one possible embodiment of the present application, as shown in Figure 1 The dehumidifier fan wheel is connected to the motor shaft through the circular truncated cone, achieving efficient connection of the dehumidifier fan wheel and the motor shaft. The center of the hub 100 extends axially to form a closed circular truncated cone structure. The top of the circular truncated cone is provided with an annular positioning stop, which forms an axial positioning reference with the shoulder part of the motor shaft, avoiding the imbalance caused by traditional key connection. In another possible embodiment of the present application, the transition area between the root of the circular truncated cone and the main body of the hub 100 is arranged with a reinforcing rib structure, which effectively disperses the stress concentration during torque transmission, improving the fatigue life of the connection part. Overall, the closed circular truncated cone structure makes the overall center of mass of the fan wheel closer to the motor support point, reducing the cantilever moment and significantly improving the dynamic stability during high-speed rotation.

[0066] Specifically, as shown in Figure 1 The circular truncated cone is a solid circular truncated cone. The solid circular truncated cone structure significantly improves the rigidity modulus of the hub, effectively avoiding the common excitation frequency range. At the same time, the continuous mass distribution can eliminate the interface micro-motion of traditional assembled structures, reducing vibration and noise. The modal shape of the solid structure is more regular, and combined with the streamline shape of the transition area of the circular truncated cone, the periodic excitation during rotation is significantly reduced, and airflow separation noise is reduced. As shown in Figure 6As shown, this design not only eliminates the noise in a specific frequency band, but also reduces the total noise level by about 0.6dB without changing the aerodynamic efficiency. This noise reduction effect achieved through structural optimization has long-term stability, and compared with traditional sound insulation processing methods, it can fundamentally solve the noise problem.

[0067] Further, the application also provides a dehumidifier containing the above-mentioned dehumidifier fan wheel.

[0068] In summary, the application discloses a dehumidifier fan wheel and a dehumidifier, which comprise a hub, the dehumidifier fan wheel is connected to a motor shaft through the hub, a plurality of fan blades, one end of the fan blade is fixed on the hub, and the fan blade is arranged around the edge of the hub, and a flow guide ring, the flow guide ring is fixedly connected to the other end of the fan blade relative to the hub, air is sucked into the dehumidifier fan wheel from the flow guide ring and flows out through the fan blade, wherein the fan blades are unevenly distributed around the edge of the hub, so that the angles and spacings between the fan blades are different, so as to reduce the noise peak value when the dehumidifier fan wheel rotates. In the technical solution of the application, the fan blade layout is unevenly distributed, which effectively breaks the periodic noise generated by the traditional equidistant fan blades, can disperse the air flow pulse and reduce the noise peak value in a specific frequency band, and disperses the noise energy to a wider frequency band. The cooperation of the flow guide ring and the fan blade ensures the smooth introduction of the inlet air flow, optimizes the distribution state of the air flow in the flow channel, reduces the air flow separation and vortex phenomenon, maintains the air volume while improving the aerodynamic efficiency of the fan wheel. The two ends of the fan blade are fixedly connected to the hub and the flow guide ring respectively, forming a stable triangular support structure, the flow guide ring serves as a ring-shaped reinforcing piece and significantly improves the structural rigidity of the whole assembly, and the uneven load distribution effectively reduces the resonance risk and reduces the vibration amplitude during operation. The fan wheel designed in the application can directly replace the traditional fan wheel without changing the overall structure of the dehumidifier, is suitable for dehumidifier products of different specifications and power levels, and is compatible with various motor driving systems. While maintaining the basic function of the fan wheel, the application realizes the cooperative optimization of the noise reduction performance and the aerodynamic efficiency, and provides an effective technical solution for improving the use experience of the dehumidifier product.

[0069] It should be understood that the application is not limited to the above examples, and those skilled in the art can make improvements or changes according to the above description, and all these improvements and changes shall belong to the protection scope of the appended claims of the application.

Claims

1. A dehumidifier impeller, characterized in that: The dehumidifier fan wheel includes: A hub, through which the dehumidifier impeller is connected to the motor shaft; a plurality of fan blades, one end of each of the fan blades being fixed to the hub, and each of the fan blades being arranged around the edge of the hub; A guide ring, the guide ring being fixedly connected to the other end of the fan blade relative to the hub, and air is sucked 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, so that the angles and spacings between the fan blades are different, so as to reduce the noise peak when the dehumidifier impeller rotates.

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

3. The dehumidifier impeller according to claim 2, characterized in that: The angle between the two blades satisfies the following conditions: Wherein, i is the number of the blades arranged around the hub, θ i is the angle between the i-th blade and the i+1-th blade, is the angle between the i-th blade and the (i+1)-th blade when the blades are evenly arranged around the hub, and Δφ and m are modulation parameters.

4. The dehumidifier impeller according to claim 3, characterized in that: The fan blades are subject to the following constraints to meet the balance requirements of the fan blades: Among them, θ z is the angle between the zth blade and the z+1th blade.

5. The dehumidifier impeller according to claim 4, characterized in that: Take the value 1.2, take the value 3.

6. The dehumidifier impeller according to claim 4, characterized in that: 51 fan blades are arranged around the hub, the angle between the first end and the tangent is 149.7°, and the angle between the second end and the tangent is 67.5°.

7. The dehumidifier impeller according to claim 4, characterized in that: The hub is a circular hub, and the fan blades have a wrap angle of 3.3° relative to the center of the hub.

8. The dehumidifier impeller according to claim 7, characterized in that: 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 impeller according to claim 8, characterized in that: The center of the hub protrudes along the axial direction to form a closed frustum, and the dehumidifier impeller is connected to the motor shaft through the frustum.

10. A dehumidifier, characterized in that: The dehumidifier comprises a fan wheel according to any one of claims 1 to 9.

Images