Centrifugal fan and electronic device

Abstract

This application provides a centrifugal fan and electronic device, relating to the field of fan technology. The centrifugal fan provided by this application includes: a volute; a fan body disposed within the volute, including a central disk and multiple fan blades, the first ends of the multiple fan blades being connected and disposed around the central disk; and a noise-reducing ring disposed at the second end of the fan blades and located on one side of the fan blades along the thickness direction of the volute. The noise-reducing ring is configured to connect the second ends of the multiple fan blades into a whole, and includes multiple bent sections. Along the circumference of the central disk, the noise-reducing ring portion between two adjacent fan blades forms a bent section. This application provides a centrifugal fan and electronic device that can increase the sweeping airflow of the fan blades and improve the overall heat dissipation effect of the centrifugal fan.

Description

Technical Field

[0001] This application relates to the field of fan technology, and more particularly to a centrifugal fan and electronic device. Background Technology

[0002] Centrifugal fans, as core components of ventilation and heat dissipation equipment, are widely used in household appliances, industrial equipment, and electronic device heat dissipation. The noise reduction ring is an important noise reduction component in centrifugal fans, typically connected to the blade tips to reduce vibration noise generated during blade rotation and improve the structural strength of the blades. However, the noise reduction ring can impede high-speed airflow, reducing the air volume swept by the blades and lowering the overall heat dissipation effect of the centrifugal fan. Summary of the Invention

[0003] To address at least one of the problems mentioned in the background art, this application provides a centrifugal fan and electronic device that can increase the airflow of the fan blades and improve the overall heat dissipation effect of the centrifugal fan.

[0004] To achieve the above objectives, this application provides the following technical solution:

[0005] This application provides a centrifugal fan, comprising:

[0006] Snail shell;

[0007] The fan body is housed within a volute and includes a central disc and multiple fan blades, with the first ends of the multiple fan blades connected around the central disc.

[0008] A silencing ring is located at the second end of the fan blade and on one side of the fan blade along the thickness direction of the volute. The silencing ring is constructed to connect the second ends of multiple fan blades into a whole. The silencing ring includes multiple bent sections. Along the circumference of the central disk, the silencing ring portion between two adjacent fan blades forms a bent section.

[0009] As an alternative implementation, the bending section includes a first surface and a second surface opposite to each other along the thickness direction of the volute, with the first surface facing away from the fan blade along the thickness direction of the volute, and the bending section having a third surface facing the direction of the central disk, with the third surface and the second surface transitioning through a first inclined surface.

[0010] As an optional implementation, the included angle between the first inclined plane and the second plane is greater than or equal to 120° and less than or equal to 150°.

[0011] As an optional implementation, along the circumference of the central disk, two adjacent fan blades and the bend between the two adjacent fan blades form a silent section. Within a silent section, the angle between the sidewall and the third surface of one fan blade is greater than or equal to 60° and less than or equal to 90°, and the angle between the sidewall and the third surface of the other fan blade is greater than or equal to 90° and less than or equal to 120°.

[0012] As an alternative implementation, the bent segment has a fourth face facing away from the central disk, and the fourth face and the second face are connected by a second inclined surface.

[0013] As an optional implementation, within a silent section, the angle between the sidewall and the fourth surface of one fan blade is greater than or equal to 70° and less than or equal to 105°, and the angle between the sidewall and the fourth surface of the other fan blade is greater than or equal to 75° and less than or equal to 110°.

[0014] As an alternative implementation, two adjacent bending segments are symmetrically arranged along the circumference of the central disk to form a "V" shape structure, with the opening of the "V" shape structure facing towards the central disk or away from the central disk.

[0015] As an alternative implementation, within a silent section, the length of the third surface sandwiched between two fan blades is greater than the length of the fourth surface.

[0016] As an optional implementation, the width of the first inclined surface along the radial direction of the central disk is greater than or equal to 0.2 mm, and / or the width of the silencing ring along the radial direction of the central disk is greater than or equal to 1.5 mm.

[0017] Secondly, this application also provides an electronic device, including the centrifugal fan described in the second aspect.

[0018] The centrifugal fan provided in this application includes: a volute; a fan body disposed within the volute, including a central disk and multiple fan blades, the first ends of the multiple fan blades being connected around the central disk; and a noise-reducing ring disposed at the second end of the fan blades and located on one side of the fan blades along the thickness direction of the volute, the noise-reducing ring being configured to connect the second ends of the multiple fan blades into a whole, the noise-reducing ring including multiple bent segments, and in the circumferential direction along the central disk, the noise-reducing ring portion between two adjacent fan blades forming a bent segment.

[0019] The centrifugal fan provided in this application minimizes the obstruction of high-speed airflow by placing a silent ring on one side of the fan blade along the thickness direction of the volute. Furthermore, the silent ring is constructed with multiple bends, with the portion of the silent ring between adjacent fan blades forming a bend. By adjusting the extension direction of the bends, the resistance to airflow is further reduced. While retaining the functions of the silent ring in reducing fan blade rotational vibration noise and improving fan blade structural strength, this effectively increases the fan blade sweep volume, thereby improving the overall heat dissipation effect of the centrifugal fan. This solves the problem in existing technologies where the silent ring obstructs airflow, leading to reduced sweep volume and decreased heat dissipation. Attached Figure Description

[0020] To more clearly illustrate the technical solutions in the embodiments of this application 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 some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0021] Figure 1 This is a schematic diagram of the overall structure of the centrifugal fan provided in an embodiment of this application;

[0022] Figure 2 This is a schematic diagram of the internal structure of a centrifugal fan provided in an embodiment of this application;

[0023] Figure 3 for Figure 2 Enlarged view of point A in the middle;

[0024] Figure 4 A schematic diagram of a first structure of the fan body and the noise reduction ring in a centrifugal fan provided in an embodiment of this application;

[0025] Figure 5 for Figure 4 Enlarged view of point B in the middle;

[0026] Figure 6 A schematic diagram of a second structure of the fan body and the noise reduction ring in a centrifugal fan provided in an embodiment of this application;

[0027] Figure 7 for Figure 6 Enlarged view of point C in the middle.

[0028] Explanation of reference numerals in the attached figures:

[0029] 100. Centrifugal fan; 110. Volute; 120. Fan body; 121. Central disc; 122. Fan blade; 130. Bend section; 131. First surface; 132. Second surface; 133. Third surface; 134. Fourth surface; 135. First inclined surface; 136. Second inclined surface. Detailed Implementation

[0030] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0031] In this application, the terms “upper,” “lower,” “left,” “right,” “front,” “back,” “top,” “bottom,” “inner,” “outer,” “vertical,” “horizontal,” “lateral,” and “longitudinal” indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings. These terms are primarily for the purpose of better describing this application and its embodiments, and are not intended to limit the indicated devices, elements, or components to having a specific orientation, or to be constructed and operated in a specific orientation.

[0032] Furthermore, in addition to indicating location or positional relationship, some of the aforementioned terms may also have other meanings. For example, the term "above" may also be used in some cases to indicate a certain dependency or connection relationship. Those skilled in the art can understand the specific meaning of these terms in this application based on the specific circumstances.

[0033] Furthermore, the terms "installation," "setup," "equipped with," "connection," and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral structure; 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, or an internal connection between two devices, components, or parts. Those skilled in the art can understand the specific meaning of these terms in this application based on the specific circumstances.

[0034] Furthermore, the terms "first," "second," etc., are primarily used to distinguish different devices, elements, or components (which may be the same or different in specific type and construction), and are not intended to indicate or imply the relative importance or quantity of the indicated devices, elements, or components. Unless otherwise stated, "a plurality of" means two or more.

[0035] Centrifugal fans, as core components of ventilation and heat dissipation equipment, are widely used in household appliances, industrial equipment, and electronic device heat dissipation. The noise reduction ring is an important noise reduction component in centrifugal fans, typically connected to the blade tips to reduce vibration noise generated during blade rotation and improve the structural strength of the blades. However, the noise reduction ring can impede high-speed airflow, reducing the air volume swept by the blades and lowering the overall heat dissipation effect of the centrifugal fan.

[0036] In view of this, this application provides a centrifugal fan that minimizes the obstruction of high-speed airflow by placing a silent ring on one side of the fan blade along the thickness direction of the volute. The silent ring is constructed to include multiple bends, with the silent ring portion between two adjacent fan blades forming a bend. By adjusting the extension direction of the bend, the resistance of the airflow is further reduced. While retaining the function of the silent ring in reducing fan blade rotation vibration noise and improving the structural strength of the fan blade, the fan blade sweep volume is effectively increased, thereby improving the overall heat dissipation effect of the centrifugal fan.

[0037] Figure 1 This is a schematic diagram of the overall structure of the centrifugal fan provided in an embodiment of this application; Figure 2 This is a schematic diagram of the internal structure of a centrifugal fan provided in an embodiment of this application; Figure 3 for Figure 2 Enlarged view of point A in the middle; Figure 4 A schematic diagram of a first structure of the fan body and the noise reduction ring in a centrifugal fan provided in an embodiment of this application; Figure 5 for Figure 4 Enlarged view of point B in the middle; Figure 6 A schematic diagram of a second structure of the fan body and the noise reduction ring in a centrifugal fan provided in an embodiment of this application; Figure 7 for Figure 6 Enlarged view of point C in the middle.

[0038] You can refer to this. Figures 1 to 7 This application provides a centrifugal fan 100, comprising:

[0039] 110 volutes;

[0040] The fan body 120 is disposed inside the volute 110 and includes a central disk 121 and multiple fan blades 122, with the first ends of the multiple fan blades 122 connected and arranged around the central disk 121.

[0041] A silencing ring is disposed at the second end of the fan blade 122 and located on one side of the fan blade 122 along the thickness direction of the volute 110. The silencing ring is configured to connect the second ends of multiple fan blades 122 into a whole. The silencing ring includes multiple bent sections 130. Along the circumference of the central disk 121, the silencing ring portion between two adjacent fan blades 122 forms a bent section 130.

[0042] The centrifugal fan 100 provided in this application embodiment minimizes the obstruction of high-speed flowing gas by placing a silent ring on one side of the fan blade 122 along the thickness direction of the volute 110. Simultaneously, the silent ring is constructed to include multiple bent segments 130, with the silent ring portion between two adjacent fan blades 122 forming a bent segment 130. By adjusting the extension direction of the bent segment 130, the resistance to gas flow is further reduced. While retaining the function of the silent ring in reducing the rotational vibration noise of the fan blade 122 and improving the structural strength of the fan blade 122, the airflow of the fan blade 122 is effectively increased, thereby improving the overall heat dissipation effect of the centrifugal fan 100. This solves the problem in the prior art where the silent ring obstructs gas flow, leading to a reduction in airflow and a decrease in heat dissipation effect.

[0043] The silent ring can be made of engineering plastic, a material known for its high strength, impact resistance, and high-temperature resistance. It also offers excellent noise reduction and damping, making it suitable for the high-speed operation of the centrifugal fan 100. Furthermore, it is resistant to deformation and aging, ensuring long-term stable performance. To enhance wear resistance and impact resistance, an additional wear-resistant coating can be applied to the surface of the silent ring that comes into contact with the airflow, reducing wear caused by airflow impact and extending its service life. The silent ring is connected to the fan blade 122 using a combination of locking clips and locating pins to ensure stable installation.

[0044] In the above embodiments, the bending section 130 may include a first surface 131 and a second surface 132 opposite to each other along the thickness direction of the volute 110. Along the thickness direction of the volute 110, the first surface 131 faces away from the fan blade 122. The bending section 130 has a third surface 133 facing the central disk 121. The third surface 133 and the second surface 132 are transitioned by a first inclined surface 135. The transition between the third surface 133 and the second surface 132 by the first inclined surface 135 effectively optimizes the flow state of the gas in the region of the silent ring bending section 130. The inclined structure of the first inclined surface 135 breaks the airflow stagnation problem caused by the right-angle transition, guiding the gas to flow smoothly along the inclined surface, reducing flow losses such as eddies and separation generated at the bend, and reducing the flow resistance when the gas flows through the bending section 130. This allows the airflow to pass more smoothly during the sweeping process of the fan blade 122, effectively increasing the effective sweeping volume of the fan blade 122, thereby enhancing the ventilation and heat dissipation efficiency of the centrifugal fan 100. Simultaneously, the first inclined surface 135... The 35 transition structure increases the stress area and structural continuity of the bending section 130, disperses the stress generated during airflow impact and rotation, and improves the overall structural strength of the bending section 130 and the silent ring. This avoids problems such as cracking and deformation during long-term use, and ensures the stable performance of the silent ring in strengthening the structure of the fan blade 122 and reducing noise. In addition, the layout of this structure in the thickness direction of the volute 110 further compresses the space occupied by the silent ring in the airflow, reducing airflow obstruction from a structural perspective. Combined with the overall layout design of the silent ring, this further improves the aerodynamic performance and heat dissipation effect of the centrifugal fan 100.

[0045] In the above embodiments, the included angle between the first inclined surface 135 and the second surface 132 can be greater than or equal to 120° and less than or equal to 150°. This angle range can optimize the guiding effect of gas flow, avoid the airflow from generating violent impacts and forming a large number of eddies and turbulence, accurately guide the gas to smoothly turn along the first inclined surface 135, minimize the flow resistance of the gas at the bend section 130, improve the smoothness of gas flow, and effectively increase the sweeping volume of the fan blade 122. At the same time, this angle range makes the structural stress distribution of the bend section 130 more uniform, enhances the structural strength of the bend section 130, resists the deformation risk caused by the airflow impact when the fan blade 122 rotates, and ensures that the silent ring can achieve the functions of noise reduction and reinforcement of the fan blade 122 in a long-term stable manner. In conjunction with the overall layout design of the silent ring, it comprehensively improves the aerodynamic performance and heat dissipation effect of the centrifugal fan 100.

[0046] When the angle between the first inclined surface 135 and the second surface 132 is less than 120°, the transition structure of the inclined surface is too steep. This will cause severe flow impact when the gas flows through the bend section 130, easily forming vortices and airflow separation at the junction of the inclined surface and the second surface 132, increasing gas flow resistance. This not only reduces the sweep volume of the fan blade 122 but also exacerbates airflow noise. At the same time, an excessively small angle will cause the structural stress of the bend section 130 to concentrate in the transition area, reducing the structural strength of the bend section 130 and making it prone to cracking and deformation, thus affecting the structure of the silent ring on the fan blade 122. Reinforcement and noise reduction functions: When the angle between the first inclined surface 135 and the second surface 132 is greater than 150°, the inclined transition structure is too gentle, which will prolong the flow path of the gas at the bend section 130, increase the contact area and frictional resistance between the airflow and the bend section 130, and also reduce the gas flow efficiency, resulting in a decrease in the sweep volume of the fan blade 122 and a decrease in the heat dissipation effect of the centrifugal fan 100. In addition, the excessive angle will make the structure of the bend section 130 redundant, increase the material cost and overall weight of the silent ring, and at the same time, it is not conducive to the smooth direction of the gas, and cannot give full play to the design advantages of the inclined transition to optimize the airflow.

[0047] In the above embodiment, along the circumference of the central disk 121, two adjacent fan blades 122 and the bending section 130 located between the two adjacent fan blades 122 can form a silent section. Within a silent section, the angle between the sidewall of one fan blade 122 and the third surface 133 is greater than or equal to 60° and less than or equal to 90°, and the angle between the sidewall of the other fan blade 122 and the third surface 133 is greater than or equal to 90° and less than or equal to 120°. The included angles between the sidewalls of the two fan blades 122 and the third surface 133 of the bent section 130 within the silent section are set to greater than or equal to 60° and less than or equal to 90° and greater than or equal to 90° and less than or equal to 120°, respectively. This angle range can accurately match the airflow direction generated by the rotation of the fan blades 122, guiding the airflow smoothly within the silent section, reducing airflow impact, eddies, and airflow separation, and lowering gas flow resistance, thereby increasing the sweep volume of the fan blades 122. At the same time, it optimizes the structural stress distribution between the sidewalls of the fan blades 122 and the third surface 133 of the bent section 130, enhances the structural strength of the silent section, and ensures the stable structural reinforcement and noise reduction function of the silent ring on the fan blades 122. The angle is determined to maximize the overall aerodynamic performance and heat dissipation of the centrifugal fan 100. When the angle is too small, the airflow will collide violently with the third surface 133 of the bend section 130, forming severe vortices and airflow separation, which will greatly increase the flow resistance. This will not only reduce the sweep volume but also aggravate the airflow noise. Furthermore, stress concentration is likely to occur at the joint, reducing the structural strength and making it easy to cause component damage. When the angle is too large, the airflow path in the silent section will become longer, increasing the frictional resistance between the airflow and the structure, reducing the airflow turning efficiency, and failing to fully utilize the airflow inertia to improve the sweep effect, thereby weakening the aerodynamic performance and heat dissipation efficiency of the centrifugal fan 100.

[0048] In the above embodiments, the bent section 130 may have a fourth surface 134 facing away from the central disk 121, and the fourth surface 134 and the second surface 132 are connected by a second inclined surface 136. The second inclined surface 136 can guide the airflow to smoothly turn along the second inclined surface 136, reducing flow losses such as eddies and airflow separation generated in this area, reducing impact resistance and friction resistance during gas flow, and improving the flow efficiency of the airflow in the bent section 130 area, thereby effectively improving the sweep volume of the fan blade 122. At the same time, the transition design of the second inclined surface 136 disperses the stress distribution of the bent section 130 under the impact of airflow, enhances the structural strength and stability of the bent section 130, ensures that the silent ring can stably perform its structural reinforcement and noise reduction functions for the fan blade 122, avoids problems such as structural stress concentration and aggravated airflow impact caused by right-angle transition, and further improves the aerodynamic performance and heat dissipation effect of the centrifugal fan 100.

[0049] In the above embodiments, the angle between the second inclined surface 136 and the second surface 132 can be greater than or equal to 120° and less than or equal to 150°. This angle range optimizes the airflow pattern in the region of the bend section 130 facing away from the central disk 121, allowing the second inclined surface 136 to guide the airflow through a smooth transition, reducing eddies and flow losses, lowering gas flow resistance, increasing the sweep volume of the fan blade 122, and simultaneously making the stress distribution of the bend section 130 more uniform, enhancing structural strength, and ensuring the stable operation of the silent ring. When the angle is less than 120°, the transition of the second inclined surface 136 is too steep, and the airflow will violently impact the second surface 132, resulting in eddies and airflow separation. The angle significantly increases airflow resistance, which not only reduces sweeping efficiency but also exacerbates airflow noise. Furthermore, stress concentration is prone to occur in the transition area, reducing the structural strength of the bending section 130 and making it susceptible to structural failures such as cracking and deformation. When the included angle is greater than 150°, the transition of the second inclined surface 136 is too gentle, which prolongs the airflow path, increases the contact area and frictional resistance between the airflow and the bending section 130, and fails to effectively guide the airflow direction, reducing airflow efficiency. At the same time, it causes structural redundancy in the bending section 130, increasing material costs and overall weight, and failing to fully utilize the design advantages of the inclined transition to optimize airflow, thereby weakening the aerodynamic performance and heat dissipation effect of the centrifugal fan 100.

[0050] In the above embodiments, the second surface 132 of the bent section 130 can also be configured as a streamlined arc surface structure similar to the upper surface of an airfoil. This structure conforms to the natural flow trajectory of airflow, effectively reducing frictional resistance when airflow passes through it, preventing airflow from stagnating or forming eddies on the second surface 132, allowing airflow to smoothly transition along the arc surface, reducing collision losses between airflow and structure, and significantly improving the smoothness of airflow. Secondly, the airfoil-like arc surface structure can optimize airflow turning efficiency, reduce the impact of airflow at the turning point, reduce noise caused by airflow turbulence, and at the same time avoid airflow separation, ensuring the stability of airflow. Furthermore, this structure can... This design allows for a more reasonable contact area between the airflow and the second surface 132, reducing the impact of the airflow on the structure and thus lowering the risk of stress concentration. This enhances the overall stability and service life of the silent ring. Furthermore, the streamlined arc surface better adapts to the airflow direction when the fan blades 122 rotate, avoiding airflow obstruction caused by structural abruptness. This ensures that the airflow can flow along a preset path, further optimizing the aerodynamic performance of the fan. At the same time, it does not require additional structural complexity and achieves effective airflow guidance without increasing manufacturing costs. It balances quietness, noise reduction, and airflow efficiency, adapting to the operating conditions of the centrifugal fan 100.

[0051] In the above embodiments, within a silent section, the angle between the sidewall of one fan blade 122 and the fourth surface 134 can be greater than or equal to 70° and less than or equal to 105°, and the angle between the sidewall of the other fan blade 122 and the fourth surface 134 can be greater than or equal to 75° and less than or equal to 110°. This angle range can precisely match the airflow direction when the fan blade 122 rotates, guiding the airflow smoothly on the side away from the central disk 121 within the silent section. This effectively avoids airflow impact, eddies, and airflow separation, reduces gas flow resistance, and increases the sweeping air volume of the fan blade 122. At the same time, it optimizes the structural stress distribution of the sidewall of the fan blade 122 and the fourth surface 134 of the bend section 130, enhancing the structural strength of the silent section and ensuring the stable performance of the silent ring's structural reinforcement and noise reduction functions for the fan blade 122. When the included angle is too small, the airflow will collide violently with the fourth surface 134 of the bend section 130, forming severe eddies and airflow separation, significantly increasing flow resistance. This not only reduces the sweeping air volume but also exacerbates airflow noise, and stress concentration is prone to occur at the joint, reducing structural strength and easily causing component damage. When the included angle is too large, the airflow path within the silent section will become longer, increasing the frictional resistance between the airflow and the structure, reducing airflow turning efficiency, and failing to fully utilize airflow inertia to improve the sweeping effect, thereby weakening the aerodynamic performance and heat dissipation efficiency of the centrifugal fan 100.

[0052] In the above embodiment, two adjacent bending sections 130 can be symmetrically arranged along the circumference of the central disk 121 to form a "V" shape. The symmetrical structure can make the circumferential airflow uniformly stressed, avoiding local eddies, airflow deviation, and abnormal noise increase caused by structural asymmetry. The "V" shape can conform to the airflow diffusion direction between adjacent fan blades 122, forming a natural guide channel, reducing airflow impact and stagnation between bending sections 130, while improving the integrity and stability of the circumferential structure of the silent ring, reducing stress concentration, and improving the structure's vibration resistance. The opening of the "V" shape can face towards the central disk 121 or away from the central disk 121.

[0053] In the above embodiments, within a silent section, the length of the third surface 133 sandwiched between two fan blades 122 can be greater than the length of the fourth surface 134. It can be understood that the third surface 133, facing the central disk 121 and sandwiched between the two fan blades 122, is a key area for the initial convergence and guidance of airflow. A longer length can provide more space for airflow guidance, ensuring a smooth transition of airflow from the root of the fan blades 122 to the outside, reducing the compression, impact, and eddy current generation of airflow between the two fan blades 122. The fourth surface 134, facing away from the central disk 121, mainly undertakes the role of smooth airflow subsequent discharge. A shorter length can avoid excessive extension leading to redundant airflow paths and increased frictional resistance, while also taking into account the overall structural compactness of the bend section 130, optimizing stress distribution, and avoiding insufficient airflow guidance due to the third surface 133 being too short and airflow obstruction due to the fourth surface 134 being too long, thereby further improving the airflow guidance efficiency and structural stability of the silent section.

[0054] In the above embodiments, the width of the first inclined surface 135 along the radial direction of the central disk 121 can be greater than or equal to 0.2 mm. This size limit ensures that the first inclined surface 135 can form an effective airflow guiding structure, ensuring the structural integrity and airflow guiding effect of the inclined transition area, avoiding problems such as insufficient structural strength and airflow guiding failure caused by too small a width. It can stably play the role of the first inclined surface 135 in reducing gas flow resistance and optimizing airflow path, improving the sweep volume of the fan blade 122 and the aerodynamic performance of the centrifugal fan 100, while ensuring the stable realization of the structural reinforcement and noise reduction function of the silent ring for the fan blade 122. When the width of the first inclined surface 135 along the radial direction of the central disk 121 is less than 0.2 mm, the effective working area of ​​the inclined surface structure is too small, and it is impossible to form a continuous and stable airflow guiding path. It is easy to have problems such as airflow impact eddies and increased flow resistance. At the same time, it will lead to weak structural strength in the transition area, which is prone to stress concentration, deformation or even damage, seriously affecting the performance and service life of the silent ring.

[0055] In the above embodiments, the radial width of the silent ring along the central disk 121 can be greater than or equal to 1.5 mm. This dimensional requirement ensures that the silent ring has sufficient structural strength to effectively withstand the airflow impact and vibration load when the fan blade 122 rotates, stably achieving the structural reinforcement and noise reduction functions of the fan blade 122. At the same time, it ensures the reliability of the connection between the silent ring and the second end of the fan blade 122, avoiding problems such as loose connection and structural deformation caused by insufficient radial width, ensuring the stability of the silent ring under high-speed rotation conditions, and providing a structural basis for optimizing airflow and increasing the sweep volume of the fan blade 122. When the radial width of the silent ring along the central disk 121 is less than 1.5 mm, its structural strength will decrease significantly, and it is prone to cracking, deformation, or even falling off under the action of airflow impact and periodic vibration. This will not only lose the structural reinforcement and noise reduction functions of the fan blade 122, but also destroy the stability of the airflow field, increase flow resistance, reduce the sweep volume of the fan blade 122, and thus affect the overall heat dissipation efficiency and operational reliability of the centrifugal fan 100.

[0056] Furthermore, this application embodiment also provides an electronic device, including the centrifugal fan 100 in the above embodiment. The centrifugal fan 100 minimizes the obstruction of high-speed flowing gas by setting a silent ring on one side of the fan blade 122 along the thickness direction of the volute 110. At the same time, the silent ring is constructed to include multiple bends 130, with the silent ring portion between two adjacent fan blades 122 forming a bend 130. By adjusting the extension direction of the bend 130, the resistance when the gas flows through is further reduced. While retaining the function of the silent ring in reducing the rotational vibration noise of the fan blade 122 and improving the structural strength of the fan blade 122, the air volume of the fan blade 122 is effectively increased, thereby improving the heat dissipation effect and service life of the electronic device.

[0057] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this application, and are not intended to limit them. Although this application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features therein. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the various implementations of this application.

Claims

1. A centrifugal fan, characterized in that, include: worm shell (110); The fan body (120) is disposed inside the volute (110) and includes a central disk (121) and a plurality of fan blades (122), the first ends of the plurality of fan blades (122) being connected around the central disk (121); A silencing ring is disposed at the second end of the fan blade (122) and located on one side of the fan blade (122) along the thickness direction of the volute (110). The silencing ring is configured to connect the second ends of a plurality of fan blades (122) into a whole. The silencing ring includes a plurality of bent segments (130). Along the circumferential direction of the central disk (121), the silencing ring portion between two adjacent fan blades (122) forms one bent segment (130).

2. The centrifugal fan according to claim 1, characterized in that, The bent section (130) includes a first surface (131) and a second surface (132) opposite each other along the thickness direction of the volute (110), and the first surface (131) faces away from the fan blade (122) along the thickness direction of the volute (110). The bent section (130) has a third surface (133) facing the central disk (121), and the third surface (133) and the second surface (132) are connected by a first inclined surface (135).

3. The centrifugal fan according to claim 2, characterized in that, The angle between the first inclined plane (135) and the second plane (132) is greater than or equal to 120° and less than or equal to 150°.

4. The centrifugal fan according to claim 2, characterized in that, Along the circumference of the central disk (121), two adjacent fan blades (122) and the bend (130) between the two adjacent fan blades (122) form a silent section. Within a silent section, the angle between the sidewall of one fan blade (122) and the third surface (133) is greater than or equal to 60° and less than or equal to 90°, and the angle between the sidewall of the other fan blade (122) and the third surface (133) is greater than or equal to 90° and less than or equal to 120°.

5. The centrifugal fan according to claim 4, characterized in that, The bent section (130) has a fourth surface (134) facing away from the central disk (121), and the fourth surface (134) and the second surface (132) are connected by a second inclined surface.

6. The centrifugal fan according to claim 5, characterized in that, Within one of the silent sections, the angle between the sidewall of one of the fan blades (122) and the fourth surface (134) is greater than or equal to 70° and less than or equal to 105°, and the angle between the sidewall of the other fan blade (122) and the fourth surface (133) is greater than or equal to 75° and less than or equal to 110°.

7. The centrifugal fan according to claim 1, characterized in that, Along the circumference of the central disk (121), two adjacent bending segments (130) are symmetrically arranged to form a "V" shape structure. The opening of the "V" shape structure faces the central disk (121) or is away from the central disk (121).

8. The centrifugal fan according to claim 5, characterized in that, Within one of the silent sections, the length of the third surface (133) sandwiched between the two fan blades (122) is greater than the length of the fourth surface (134).

9. The centrifugal fan according to any one of claims 2-6, characterized in that, The width of the first inclined surface (135) along the radial direction of the central disk (121) is greater than or equal to 0.2 mm, and / or the width of the silencing ring along the radial direction of the central disk (121) is greater than or equal to 1.5 mm.

10. An electronic device, characterized in that, Includes the centrifugal fan as described in any one of claims 1 to 9.

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