A loudspeaker unit with a fine mesh

Abstract

The utility model discloses a speaker unit with fine mesh, wherein the diaphragm of the unit is a folded ring rectangular diaphragm; wherein the folded ring rectangular diaphragm comprises a folded ring area, and a hollow part arranged at the center of the folded ring area; the hollow part is covered with a fine mesh layer; wherein the fine mesh layer has a fine hole diameter of 0.05-0.3 mm. The hollow part at the center of the diaphragm and the fine mesh layer covering it provide a special channel for the dissipation of heat inside the speaker unit. When the speaker is working, the current generates heat through the voice coil, and these heat needs to be dissipated in time to avoid the speaker from being overheated and thus having its performance reduced or even damaged. Since the center position of the diaphragm is close to the key heat generating components such as the voice coil, the hollow part enables the heat to "escape" from this central area and exchange heat with the outside air through the fine mesh layer.

Description

Technical Field

[0001] This utility model relates to the field of loudspeaker technology, and in particular to a loudspeaker unit with a fine mesh. Background Technology

[0002] Currently, the heat dissipation design of most loudspeakers is still imperfect. When a loudspeaker is operating, especially at high power output, the voice coil generates a significant amount of heat. Existing loudspeaker heat dissipation mainly relies on the slight displacement of the diaphragm to drive airflow, and the magnets and frame conducting heat to the external environment through their material properties. However, this heat dissipation method is inefficient and cannot dissipate heat quickly enough. Heat accumulation inside the loudspeaker leads to increased voice coil temperature, accelerating the aging of the voice coil insulation material and reducing loudspeaker performance and lifespan. Furthermore, high temperatures can demagnetize the magnets, further weakening the loudspeaker's performance stability. Utility Model Content

[0003] In view of this, the purpose of this utility model is to provide a loudspeaker unit with a fine mesh, which can solve at least one of the technical problems mentioned in the background art.

[0004] According to one aspect of the present invention, a loudspeaker unit with a fine mesh is provided, wherein the diaphragm of the unit is a folded ring rectangular diaphragm;

[0005] The folded rectangular diaphragm includes a folded ring area and a hollow portion disposed at the center of the folded ring area; the hollow portion is covered with a fine mesh layer.

[0006] The pore diameter of the fine mesh layer is 0.05–0.3 mm.

[0007] In the above technical solution, a rectangular diaphragm with a folded surround is used, a structure that differs from the traditional circular diaphragm. The folded surround provides better elasticity, allowing the diaphragm to move more stably during vibration. The folded surround design increases the diaphragm's travel range, generating a higher sound pressure level at the same amplitude, thereby increasing the speaker's output volume. A distinctive design feature is the perforated section at the center of the folded surround area, covered with a fine-mesh layer. The diameter of the pores in the fine-mesh layer is 0.05–0.3 mm, equivalent to a micro-perforated structure. This micro-perforation can influence sound propagation. From an acoustic perspective, the fine-mesh layer can act as an acoustic impedance matcher. It reduces sound reflections from the diaphragm into the surrounding air, allowing sound waves to radiate more effectively from the speaker unit, thus improving the speaker's directivity and acoustic efficiency. The presence of the pores also attenuates and filters high-frequency sound waves. When sound waves pass through a narrow aperture, diffraction and interference occur at the edge of the aperture. For high-frequency sound waves, due to their shorter wavelengths, the effects are more pronounced. This helps to improve the frequency response characteristics of the speaker to some extent, preventing the high-frequency range from becoming too sharp and achieving a smoother high-frequency output.

[0008] Furthermore, the hollowed-out section at the center of the diaphragm and the fine-mesh layer covering it provide a unique channel for heat dissipation within the speaker unit. When the speaker is operating, current flows through the voice coil, generating heat. This heat needs to be dissipated promptly to prevent performance degradation or even damage due to overheating. Because the center of the diaphragm is close to critical heat-generating components such as the voice coil, the hollowed-out section allows heat to escape from this central area and exchange heat with the outside air through the fine-mesh layer. The fine-pore structure of the mesh layer increases the surface area in contact with air, acting like a tiny heat dissipation "matrix," enabling heat to be transferred to the surrounding environment more efficiently.

[0009] In some embodiments, the thickness of the porous mesh layer is 0.02–0.10 mm.

[0010] In the aforementioned technical solution, the ultra-thin design of the perforated mesh layer, with a thickness of only 0.02–0.10 mm, allows heat to dissipate rapidly. During speaker operation, heat generated by components such as the voice coil can be more easily transferred from the perforated portion to the perforated mesh layer. Furthermore, due to the thinness of the mesh layer, heat can contact the outside air with minimal obstruction. Compared to thicker heat dissipation materials, this thin perforated mesh layer significantly shortens the heat transfer path, thereby improving heat dissipation efficiency. In addition, due to the superior heat dissipation, the speaker unit experiences less temperature fluctuation during operation. This is crucial for maintaining stable sound quality. When speaker components (such as the voice coil) are at a stable operating temperature, their electromagnetic and mechanical properties are more stable. For example, the resistance of the voice coil does not increase significantly with temperature increases, thus ensuring the stability of signal transmission and the consistency of sound output. This means that when playing music, whether it's bass, midrange, or treble, the sound can be presented to the listener with higher quality and greater stability.

[0011] In some embodiments, the porous mesh layer is made of stainless steel, polyester, or nylon.

[0012] In the above technical solution, stainless steel possesses excellent thermal conductivity, effectively and rapidly transferring heat from the speaker's interior to the surface of the perforated mesh layer. Its high thermal conductivity allows heat to be evenly distributed across the entire perforated mesh layer, thereby accelerating the heat dissipation process. For example, during high-frequency operation, the heat generated by the voice coil can be quickly transferred away through the stainless steel perforated mesh layer, reducing heat accumulation inside the speaker. Stainless steel also boasts high strength and heat resistance, maintaining structural stability and performance during prolonged high-power operation. It will not easily deform or be damaged by temperature changes, ensuring the continued effectiveness of the heat dissipation channel.

[0013] While polyester has lower thermal conductivity than stainless steel, it possesses excellent flexibility and fatigue resistance. During speaker diaphragm vibration, the polyester microporous mesh layer can withstand repeated deformations without damage, ensuring the long-term effectiveness of the heat dissipation channels. Simultaneously, the lightweight nature of polyester helps reduce diaphragm inertia, improving the speaker's response speed. Polyester also exhibits good corrosion resistance, maintaining its heat dissipation performance under various environmental conditions. For example, in humid or dusty environments, the polyester microporous mesh layer is not easily corroded or blocked, thus enabling continuous and effective heat dissipation.

[0014] Nylon material possesses excellent abrasion resistance and impact resistance, protecting the microporous mesh layer from external damage during speaker use and ensuring the integrity of the heat dissipation channels. Its good chemical stability allows the nylon microporous mesh layer to maintain its heat dissipation function normally in various chemical environments (such as those containing cleaning agents or disinfectants). The low water absorption of nylon material helps maintain the breathability of the microporous mesh layer, preventing the pores from clogging due to moisture absorption, thus ensuring smooth airflow and facilitating heat dissipation.

[0015] Fine-mesh layers made of stainless steel, polyester, or nylon can dissipate heat without significantly negatively impacting sound quality. These materials offer high acoustic transparency, allowing heat to pass through while minimizing obstruction of sound propagation. For example, the rigidity of stainless steel reduces sound wave distortion caused by material vibration; while the flexibility of polyester and nylon prevents additional vibration noise. By carefully selecting materials, a balance between heat dissipation and sound quality can be achieved. For instance, stainless steel is a suitable choice for applications with high heat dissipation requirements, while polyester or nylon are better options for applications with lower weight and greater flexibility requirements.

[0016] In some embodiments, the unit voice coil is a copper-clad aluminum wire voice coil, a flat wire voice coil, or a honeycomb structure voice coil.

[0017] In the aforementioned technical solution, the copper-clad aluminum wire voice coil combines the lightweight of aluminum wire with the high conductivity of copper wire. The lightweight of aluminum wire reduces the voice coil's inertia, allowing it to respond to audio signals more quickly. The high conductivity of copper-clad aluminum wire effectively reduces resistance, minimizing Joule heating generated by current flow during operation. Lower heat generation means the voice coil's temperature rises more slowly during operation, reducing heat dissipation stress. For example, at high power output, the copper-clad aluminum wire voice coil generates less heat compared to a conventional aluminum wire voice coil, enabling the speaker to operate stably for extended periods without performance degradation due to overheating. Simultaneously, this heat dissipation advantage of the copper-clad aluminum wire voice coil also helps improve the speaker's power handling capacity, allowing it to withstand higher power inputs under the same heat dissipation conditions.

[0018] Flat wire voice coils are made by winding flat wires, allowing for a more compact arrangement compared to traditional round wire voice coils. This compact arrangement increases the fill density of the voice coil, resulting in a larger conductor cross-sectional area within the same volume. A larger conductor cross-sectional area reduces the voice coil's resistance, thus reducing heat generation. Furthermore, the shape of the flat wire voice coil provides a larger contact area with the magnetic gap, facilitating heat conduction. The heat generated when the voice coil is operating can be transferred more quickly through this larger contact area to the metal components around the magnetic gap (such as the magnetic cone), and then dissipated through these components. This efficient heat conduction path allows the flat wire voice coil to dissipate heat more effectively, improving the thermal stability of the loudspeaker.

[0019] The honeycomb voice coil design is inspired by the hexagonal structure of a honeycomb, which boasts a high strength-to-mass ratio. Within the voice coil, the honeycomb structure provides excellent support, reducing deformation during vibration and thus minimizing heat generation caused by deformation. The porous nature of the honeycomb voice coil also facilitates airflow. During operation, these pores act as heat dissipation channels, allowing for smoother airflow and carrying away the heat generated by the voice coil. Compared to traditional voice coils, the honeycomb voice coil offers higher heat dissipation efficiency, better meeting the demands of high-power, long-duration operation.

[0020] In some embodiments, the loop region is a double-gradient catenary wave loop.

[0021] In the above technical solution, the design of the double-gradient catenary wave-shaped fold allows the diaphragm to achieve more uniform motion during vibration. This uniform vibration avoids excessive local deformation and stress concentration, thereby reducing heat generation caused by vibration. Simultaneously, uniform vibration also helps to evenly distribute heat within the diaphragm and fold area, preventing localized overheating. The wave shape of the fold generates more complex airflow patterns during diaphragm vibration. These airflows can more effectively remove heat from the fold area and the vicinity of the diaphragm. The wave-shaped fold increases the airflow path and velocity, thus enhancing the heat dissipation effect.

[0022] In some embodiments, the porous mesh layer and the folded rectangular diaphragm are fixed together by an adhesive film.

[0023] In the above technical solution, an adhesive film is used to fix the perforated mesh layer to the folded rectangular diaphragm. This adhesive film has excellent thermal conductivity. It can effectively conduct heat between the perforated mesh layer and the diaphragm, allowing heat to dissipate to the surrounding environment more quickly. In this way, heat will not accumulate at the interface between the perforated mesh layer and the diaphragm, thus reducing the risk of localized overheating. Traditional glue fixing methods may not have good thermal conductivity, and heat is prone to accumulate at the interface between the perforated mesh layer and the diaphragm. Using an adhesive film with thermal conductivity can dissipate heat more effectively, reducing the problem of localized overheating. This makes the speaker more stable when operating at high power.

[0024] In some embodiments, the area of ​​the folded ring region is at least 25% of the diaphragm area.

[0025] In the above technical solution, the larger surround area allows heat to be distributed more evenly across the entire diaphragm. Heat can be rapidly transferred from the voice coil area at the center of the diaphragm to the surround area and then dissipated through it. The wave-shaped design of the surround area further increases its contact area with the air, promoting heat transfer. Attached Figure Description

[0026] To more clearly illustrate the technical solutions in the embodiments of this utility model 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 this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0027] Figure 1 This is an exploded three-dimensional structural diagram of an embodiment of a loudspeaker unit with a fine mesh screen;

[0028] Figure 2 This is an exploded side view of an embodiment of a loudspeaker unit with a perforated mesh.

[0029] Figure 3 This is a top view schematic diagram of an embodiment of a loudspeaker unit with a fine mesh. Detailed Implementation

[0030] The present invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be particularly noted that the following embodiments are only for illustrating the present invention and do not limit the scope of the present invention. Similarly, the following embodiments are only some embodiments of the present invention, not all embodiments. All other embodiments obtained by those skilled in the art without creative effort are within the protection scope of the present invention.

[0031] Example 1

[0032] Please see Figures 1 to 3 A loudspeaker unit with a perforated mesh includes a perforated mesh layer 1, a diaphragm 2, a voice coil 3, a magnet 4, a support 5, and a magnetic return assembly 6. The diaphragm 2 of the unit is a folded-around rectangular diaphragm; wherein the folded-around rectangular diaphragm 2 includes a folded-around region 21, and a hollow portion 22 disposed at the center of the folded-around region 21; the hollow portion is covered by the perforated mesh layer 1; wherein the diameter of the pores in the perforated mesh layer is 0.05–0.3 mm. The reason for selecting the above range is as follows:

[0033] I. Consideration of the range of fine pore diameter

[0034] Too small an aperture (<0.05mm) will cause severe high-frequency attenuation, especially when the aperture is less than 0.05mm. Even with a high porosity design, the sound impedance (r) of a single aperture will be significantly reduced. a The extremely high aperture value leads to excessive attenuation of mid-to-high frequency (>2kHz) energy, resulting in a muffled sound lacking detail. Furthermore, this extremely small aperture is close to the economic limit of current precision manufacturing, making it prone to clogging and requiring special treatments such as oleophobic and hydrophobic coatings. An aperture that is too large (>0.3mm) will result in insufficient acoustic impedance, rendering the control meaningless. At this point, r... a The value is very small; even with low porosity, the total acoustic resistance (R0) is low. a It may be difficult to effectively dampen the vibration in the central region of the diaphragm or suppress wind noise. The effect of suppressing higher-order modes in the central region will be worse. It may also affect the directivity and frequency response smoothness due to obvious diffraction or scattering of sound waves.

[0035] From the perspective of acoustic resistance principles, fine-mesh mesh creates resistance to airflow, which manifests as acoustic resistance. Acoustic resistance is the acoustic impedance (Z). a The real part of the acoustic impedance r is similar to that of a resistor. a When the orifice is small (its diameter is much smaller than the wavelength) and the flow rate is low, the approximate formula is:

[0036]

[0037] in: It is the air viscosity coefficient (approximately 1.8e-5 Pa). (s@20°C) The thickness (mm) of the fine-mesh material. Let r be the radius of the fine hole (mm). Therefore, r... a and Inversely proportional, a slight decrease in aperture results in a sharp increase in acoustic resistance per aperture. Total acoustic resistance R a ≈r a / σ, a high porosity σ (numerous and densely packed pores) results in a lower total acoustic resistance. Smaller pore sizes require higher pore density to maintain a reasonable porosity; otherwise, the acoustic resistance will be too high.

[0038] II. The Influence of Porosity

[0039] Porosity represents the proportion of open area to total area. Pore size and porosity together determine acoustic resistance (Ra). a Harmony quality (M) a Sound quality (M) a Analogous to inductance, it is related to the air quality inside the hole. ( (This refers to air density). Within the target operating frequency band (mid-frequency to high-frequency), the fine-mesh mesh should primarily exhibit pure resistivity (R). a (Dominant) requires sufficiently small pores and reasonable porosity to avoid M a Excessive porosity introduces unnecessary inertia. A porosity range of 30%-70% is recommended. Too low a porosity results in poor sound transmission and increased weight; too high a porosity leads to low acoustic impedance and weak structural strength. Using a hexagonal close-packed pore array is a commonly used and efficient design.

[0040] III. Acoustic Filter Characteristics and Cutoff Frequency of Fine-Mesh Mesh

[0041] In this case, the fine-mesh mesh is equivalent to a first-order low-pass acoustic filter. Its cutoff frequency ( Approximate to Related. Substituting into the formula, we can see that... Roughly the same as Proportional. Changes in aperture affect R. a and M a The effects are different, and thus affect By selecting the pore size and porosity, the frequency point at which the fine-pore mesh begins to significantly attenuate high frequencies can be precisely set. For example: target ≈15kHz, which may require an aperture of approximately 0.15mm. Target ≈ 8kHz, may require an aperture of approximately 0.08mm (smaller aperture, lower cutoff frequency).

[0042] IV. The Control Effect of Fine Mesh on Airflow and Noise

[0043] During large-amplitude diaphragm vibrations, especially at low frequencies and high dynamic ranges, a high-speed airflow forms behind the central perforated area. The fine-perforated mesh can disperse this high-speed airflow into low-speed micro-airflows, reducing the Reynolds number. The parameters denoted by v (flow velocity) and d (characteristic size, here the aperture) are key for determining laminar / turbulent flow. Smaller apertures drastically reduce d, so even if the flow velocity v decreases only slightly due to flow diversion, the Reynolds number (Re) will drop significantly. Therefore, smaller channels have a higher critical Re (easier to maintain laminar flow), and the viscous effect of the orifice wall is stronger, directly consuming turbulent energy. Smaller apertures result in stronger flow diversion and more significant noise suppression. However, excessively small apertures can lead to excessive acoustic impedance and audible high-frequency attenuation, requiring a balance between noise suppression and high-frequency extension.

[0044] V. Improvement of Directivity by Fine-Mesh Mesh

[0045] At higher frequencies, rectangular diaphragms are prone to beaming. A fine-mesh array transforms the central acoustic radiation into a dense array of point sources, distributed on a plane with spacing much smaller than the wavelength. The spherical waves radiated by each point source interfere with each other, and the dense array of point sources causes the sound waves to diffuse over a wide angle. Compared to piston radiation, high-frequency directivity attenuation is gentler, thus improving the high-frequency beaming phenomenon of rectangular diaphragms. The aperture spacing is a key factor, determined by both aperture diameter and porosity. With a fixed porosity, the smaller the aperture diameter, the smaller the aperture spacing needs to be to maintain porosity. To effectively improve directivity, the aperture spacing must be much smaller than the wavelength of the target improvement frequency. For example, for 10kHz (wavelength 34mm) audio, an aperture spacing of ≤8.5mm is recommended, ideally ≤5.7mm. An aperture diameter of 0.05-0.3mm combined with a reasonable porosity (30-70%) can easily achieve a sufficiently small aperture spacing, effectively improving directivity in the range of several kHz to tens of kHz.

[0046] VI. The Influence of Fine-Mesh Mesh on Diaphragm Modes

[0047] Compared to circles, rectangles are more prone to generating segmented vibrations (higher-order modes) at low frequencies, with the central region being a high-frequency area and exhibiting low piston-like efficiency. A central perforated area with a fine mesh can remove inefficient / harmful mass; the perforation directly removes some mass, and the fine mesh closely adheres to the diaphragm, covering the perforated area. This is equivalent to applying a distributed viscoelastic damping layer to the active segmented vibration region. When the diaphragm vibrates at its center, it drives air through the fine mesh, reducing the acoustic resistance R. a The vibration energy is converted into heat energy and dissipated. The high rigidity of the mesh material can also constrain the local deformation of the diaphragm below.

[0048] Based on the above discussion, it can be seen that there are two directions for choosing the aperture:

[0049] (1) Based on the goal (Low-pass effect): If you want good high-frequency extension ( For frequencies >18kHz, select 0.2 - 0.3mm. If a balance is desired ( ~12-18kHz), select 0.15 - 0.2mm. If you prioritize mid-frequency purity / strong noise reduction ( ~8-12kHz), select 0.1 - 0.15mm. For extreme noise reduction / focus on mid-frequency ( <8kHz), select 0.05 - 0.1mm.

[0050] (2) Based on porosity: After selecting the pore size, adjust the porosity (usually 40%-60%) to fine-tune R. a and M a High porosity reduces R a and M a (Transparent but with reduced damping / noise suppression), low porosity increases R a and M a (Strong damping but reduced efficiency may affect low frequencies).

[0051] Based on aperture spacing (directivity): Ensure aperture spacing ( (The highest frequency wavelength where improved directivity is desired), for example, a target of 10kHz. <8.5mm. For a pore size of 0.15mm, with a hexagonal arrangement and a porosity of approximately 50%, The aperture is approximately 0.17mm, which meets the requirements. The aperture size has little impact on the directionality, as long as the aperture density is high enough.

[0052] Furthermore, the fine-aperture mesh acts as a low-pass acoustic filter. The small aperture causes early and dramatic high-frequency attenuation, requiring the target frequency band to remain flat before attenuation. The small aperture effectively suppresses the "popping" sound (wind noise) generated by airflow behind the diaphragm, especially during transient large amplitude vibrations. The dense mesh can slightly diffuse sound waves, improving high-frequency directivity. However, apertures <0.05mm are difficult to manufacture, prone to clogging, and have low strength; apertures >0.3mm are insufficient to provide adequate acoustic impedance.

[0053] In this embodiment, the thickness of the perforated mesh layer is 0.02–0.10 mm, with a maximum range of 0.04–0.06 mm (full-frequency unit). The specific reasons are as follows: the acoustic impedance Ra of the perforated mesh consumes acoustic energy, leading to increased attenuation with increasing frequency; the inertia Ma of the air within the pores hinders the transient response, causing tailing distortion; and the periodic scattering of sound waves by the perforated array causes frequency response peaks and valleys. Based on this, the following parameter optimization countermeasure strategy is proposed.

[0054]

[0055] Based on the above strategies, the setting is 0.04–0.06 mm.

[0056] In this embodiment, the fine-pore mesh layer is made of stainless steel, polyester, or nylon.

[0057] Based on the requirements of the fine-mesh layer in the design (diameter 0.05–0.3 mm, thickness 0.02–0.10 mm), and considering the speaker application scenarios (requiring good acoustic transmission, certain mechanical strength, lightweight, and environmental resistance) and manufacturing costs, the following three materials are very suitable choices:

[0058] Stainless steel microporous mesh: Stainless steel possesses high strength and rigidity, maintaining shape stability even at extremely thin thicknesses, resisting deformation, sagging, or cracking, and capable of withstanding the vibration stress of the speaker diaphragm. Furthermore, it is corrosion-resistant, high-temperature resistant, and aging-resistant, exhibiting stable performance and a long lifespan in various environments. Etching, weaving, or electroforming processes can precisely manufacture the required aperture and thickness (etched or woven thin meshes of 0.02-0.1mm are feasible). The regular mesh structure results in minimal distortion when sound waves pass through. Although stainless steel is relatively more expensive than polymer materials, its durability and stability reduce later maintenance and replacement costs. The cost of mass-producing etched or precision-woven meshes is controllable, making its overall cost-effectiveness excellent for speaker units requiring high performance and long lifespan. It is a mid-to-high-end but cost-effective choice.

[0059] Polyester film microporous mesh is extremely lightweight, significantly lighter than metal mesh, and has minimal impact on the vibration quality and sensitivity of the speaker diaphragm. Polyester film (such as PET) is the cheapest of the three materials. Laser drilling or chemical etching processes are mature and cost-effective for large-scale production. It is also easy to cut, shape, and bond, facilitating assembly into the diaphragm's perforated sections. Furthermore, the film itself has low acoustic impedance, resulting in good acoustic performance after perforation. This material and processing cost are highly competitive, making it the first choice for those seeking high cost-effectiveness and lightweight design. It is ideal for cost-sensitive products requiring large-scale production.

[0060] Nylon braided mesh boasts excellent flexibility and drape, easily conforming to complex curved surfaces (such as the slight curvature of a diaphragm) and offering good installation adaptability. Nylon filaments are inexpensive to produce, and the microfiber weaving process is mature, resulting in cost-effective large-scale production. With both raw material and weaving process costs being low, it is an economical choice. It is particularly suitable for applications where extreme lightweighting is not critical, but good fit and low cost are required.

[0061] For the highest strength, stability, and lifespan, choose stainless steel microporous mesh. Although the unit cost is slightly higher, its reliability and durability offer a long-term cost advantage for demanding products. For extreme lightweighting and lowest cost, choose polyester film microporous mesh. This is the most economical solution while having minimal impact on speaker performance (sensitivity). For good flexibility, easy installation, and low cost, choose nylon woven mesh. It is low-cost, easy to install, and its acoustic performance meets requirements.

[0062] From a manufacturing perspective, stainless steel mesh primarily uses precision etching or ultra-fine filament weaving. Polyester mesh mainly uses laser drilling or chemical etching. Nylon mesh uses ultra-fine fiber precision weaving. All three materials achieve good acoustic transmittance when meeting the required porosity and aperture. Stainless steel mesh exhibits slight diffraction at high frequencies, but the impact is usually minimal. Polyester and nylon meshes typically have lower acoustic impedance. In extreme environments (high temperature, high humidity, corrosion), stainless steel offers a more significant stability advantage. Under normal conditions, polyester and nylon are sufficient. Considering the bonding compatibility and process between the mesh layer and the diaphragm (usually polymer materials or paper), polyester and nylon are more compatible with adhesives. In actual mass production decisions, samples are typically made for acoustic testing (frequency response, distortion), mechanical testing (vibration fatigue), and cost calculation. Ultimately, the most suitable material is selected based on the product's positioning (high-end, mid-range, entry-level). All three are proven options that meet the requirements of the solution and are cost-effective.

[0063] In this embodiment, the unit voice coil is a copper-clad aluminum wire voice coil, a flat wire voice coil, or a honeycomb structure voice coil. Based on the above three voice coils, the following three schemes are given:

[0064] Option A: Copper-clad aluminum wire (CCAW) voice coil + internal magnet circuit

[0065] Wire diameter: Φ0.08–0.12mm (high-frequency unit) / Φ0.15–0.20mm (full-range unit); Number of layers: single or double layer (power > 20W); Frame: aluminum-magnesium alloy (lightweight and thermally conductive) or Kapton (high temperature resistant); Advantages include lightweight (density ≈ 3.0g / cm³): offsetting the added mass of the fine mesh and improving high-frequency extension (> 18kHz); High conductivity (≈ 70% IACS): reducing resistance loss and improving efficiency by 10–15%; Lower cost than pure copper voice coils, offering the best cost performance.

[0066] Option B: Edgewound voice coil + double magnetic gap design; cross-section: rectangular (width-to-height ratio 1:2~1:3, such as 0.2×0.4mm); magnetic circuit: T-iron + double neodymium magnetic rings (magnetic flux density ≥1.2T); its advantages are high fill rate, more efficient driving of rigid fine-hole mesh; better heat dissipation, and ability to suppress even-order harmonic distortion (THD < 0.5% @ 1kHz).

[0067] Option C: Honeycomb voice coil (high-end option); Process: Laser-welded hexagonal aluminum wire mesh skeleton; Advantages include better rigidity / weight, 3 times better resistance to lateral deformation, perfectly matching the high rigidity requirements of fine-pore mesh; Reduces thermal mismatch, with an expansion coefficient close to that of metal fine-pore mesh, and a lifespan of >1000h@40°C.

[0068] In this embodiment, the folded ring region is a double-gradient catenary wave folded ring. Exemplarily, the diaphragm with the double-gradient catenary wave folded ring topology has, from the central hollow portion and fine mesh outwards, an inner folded ring region, a damping transition zone, and an outer folded ring region. The inner folded ring region employs a catenary curvature gradient design to suppress 2-4kHz segmented vibrations and reduce modal distortion. The damping transition zone uses a silicone rubber-carbon nanotube composite material to provide damping. The negative stiffness wave-shaped design of the outer folded ring region enhances low-frequency stroke and blocks high-frequency standing waves. Simultaneously, the diaphragm material system employs a sandwich composite damping layer. The core layer is foamed titanium alloy fiber felt, the damping layer is butyl rubber and graphene slurry, and the surface layer is fluorinated thermoplastic polyurethane. These layers work synergistically to optimize diaphragm performance and reduce air friction noise and distortion.

[0069] In this embodiment, the fine-pore mesh layer and the folded rectangular diaphragm are fixed together by an adhesive film. Exemplarily, this solution employs a pre-coated thermally activated adhesive film and a vacuum step-curing process. The adhesive film substrate is selected from foamed polyurethane with a density of 0.35 g / cm³ and a sound velocity of 240 m / s, and 15% nano-zinc oxide, 10% carbon fiber fragments, and 5% hollow ceramic microspheres are added for functional modification, resulting in an initial viscosity of 280,000 cPs, an activation temperature of 80℃, and a final hardness of Shore 60A. The simplified five-step operation process includes adhesive film pre-processing, surface plasma treatment, positioning and mounting, vacuum pressing, and step-curing. The vacuum pressing is performed at a pressure of 0.3 MPa, a temperature of 80℃, and a vacuum degree of -95 kPa. The step-curing process is divided into three stages.

[0070] In this embodiment, the area of ​​the loop region is at least 25% of the diaphragm area. The rationale for this area selection is as follows: based on the acoustic fit equation:

[0071]

[0072] In the formula: Ring stiffness factor (taken as 0.62, empirical value); Target low-frequency cutoff frequency (Hz); Equivalent mass (g) of fine-mesh mesh = mesh surface mass + additional acoustic mass; Fine-mesh acoustic impedance Based on this formula, assuming the design of a full-frequency unit ( =80 Hz Fine-mesh parameters: Stainless steel etched mesh (thickness 0.05mm, density 7.9g / cm³); aperture ratio 30%, effective mass... =0.22 g Acoustic impedance ≈520 Rayl@1kHz. The above formula yields:

[0073] Folding ratio constraint:

[0074]

[0075] Based on this embodiment, it can be seen that this utility model adopts a folded-ring rectangular diaphragm, which differs from the traditional circular diaphragm. The folded ring provides better elasticity, allowing the diaphragm to move more stably during vibration. The folded ring design increases the diaphragm's travel range, generating a higher sound pressure level at the same amplitude, thereby increasing the speaker's output volume. A distinctive design feature is the hollowed-out section at the center of the folded ring area, covered with a fine-pore mesh layer. The diameter of the pores in the fine-pore mesh layer is 0.05–0.3 mm, equivalent to a micro-perforated structure. This micro-perforation can influence sound propagation. From an acoustic perspective, the fine-pore mesh layer can act as an acoustic impedance matcher. It reduces sound reflections from the diaphragm into the surrounding air, allowing sound waves to radiate more effectively from the speaker unit, thus improving the speaker's directivity and acoustic efficiency. The presence of the pores also attenuates and filters high-frequency sound waves. When sound waves pass through a fine aperture, diffraction and interference occur at the edges of the aperture. For high-frequency sound waves, due to their shorter wavelengths, the effects are more pronounced. This helps improve the frequency response characteristics of the speaker to some extent, preventing the high-frequency range from becoming overly sharp and achieving a smoother high-frequency output. Furthermore, the hollowed-out portion at the center of the diaphragm and the porous mesh layer covering it provide a unique channel for heat dissipation within the speaker unit. When the speaker is operating, current flows through the voice coil, generating heat. This heat needs to be dissipated promptly to prevent the speaker from overheating and degrading in performance or even being damaged. Since the center of the diaphragm is close to key heat-generating components such as the voice coil, the hollowed-out portion allows heat to escape from this central area and exchange heat with the outside air through the porous mesh layer. The fine porous structure of the mesh layer increases the surface area in contact with air, acting like a tiny heat dissipation "matrix," allowing heat to be transferred to the surrounding environment more efficiently.

[0076] The above description is only a part of the embodiments of this utility model, and does not limit the scope of protection of this utility model. Any equivalent device or equivalent process transformation made based on the content of this utility model specification and drawings, or direct or indirect application in other related technical fields, are similarly included in the patent protection scope of this utility model.

Claims

1. A loudspeaker unit with a fine mesh screen, characterized in that, The diaphragm of the unit is a folded ring rectangular diaphragm; The folded rectangular diaphragm includes a folded ring area and a hollow portion disposed at the center of the folded ring area; the hollow portion is covered with a fine mesh layer. The pore diameter of the fine mesh layer is 0.05–0.3 mm.

2. A loudspeaker unit with a fine mesh as described in claim 1, characterized in that, The thickness of the fine porous mesh layer is 0.02–0.10 mm.

3. A loudspeaker unit with a fine mesh as described in claim 1, characterized in that, The fine-pore mesh layer is made of stainless steel, polyester, or nylon.

4. A loudspeaker unit with a fine mesh as described in claim 1, characterized in that, The voice coil of the unit is made of copper-clad aluminum wire, flat wire, or honeycomb structure.

5. A loudspeaker unit with a fine mesh as described in claim 1, characterized in that, The folded zone is a double-gradient catenary wave folded zone.

6. A loudspeaker unit with a fine mesh as described in claim 1, characterized in that, The fine-pore mesh layer and the folded rectangular diaphragm are fixed together by an adhesive film.

7. A loudspeaker unit with a fine mesh as described in claim 1, characterized in that, The area of ​​the folded ring region is at least 25% of the diaphragm area.

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