Diaphragm preparation method, high pitch loudspeaker assembly and horn type loudspeaker

Abstract

The invention belongs to the technical field of electroacoustic transducers, and relates to a vibrating diaphragm preparation method, a high pitch loudspeaker assembly and a horn type loudspeaker, the loudspeaker assembly comprises a voice coil driving assembly and a vibrating diaphragm assembly, the vibrating diaphragm assembly comprises a dangling edge, a vibrating diaphragm body with non-uniform thickness, a reinforcing ring and a damping material, the edge area of the vibrating diaphragm body is embedded and fixed in the reinforcing ring, and the damping material is embedded in the edge area of the vibrating diaphragm body. The reinforcing ring and the dangling edge are fixedly connected together, and the damping material tightly covers the top surface of the vibrating diaphragm body; the beneficial effects are that the diaphragm body employs a non-uniform thickness design scheme, local structure rigidity distribution is optimized, natural resonant frequency is improved, segmentation vibration is effectively inhibited, the reinforcing ring disperses working stress of the diaphragm body, and the damping material further inhibits resonance and segmentation vibration. The inherent defects of the vibrating diaphragm body in the high-pitch compression driver are jointly overcome, the acoustic performance and the structural reliability are considered, and the technical problems that an existing vibrating diaphragm has segmentation vibration, is high in brittleness and easy to damage and is poor in stability under a high sound pressure level are solved.

Description

A method for preparing a diaphragm, a tweeter assembly, and a horn-type loudspeaker Technical Field

[0001] This invention belongs to the field of electroacoustic transducer technology, and particularly relates to a diaphragm preparation method, a tweeter assembly, and a horn-type loudspeaker. Background Technology

[0002] Existing tweeter compression drivers can achieve sensitivities exceeding 110 dB and maximum sound pressure levels exceeding 130 dB, thus typically employing metal diaphragms (such as titanium or aluminum alloys) or composite material diaphragms. However, under such high sound pressure levels and horn loading conditions, the mechanical and acoustic loads on the diaphragm increase dramatically, making the breakup vibration problem of metal diaphragms particularly prominent, leading to increased distortion. To pursue superior acoustic rigidity and upper frequency response limits, manufacturers have begun to experiment with using high-rigidity materials such as glass as diaphragms.

[0003] In existing technologies, glass diaphragms are generally designed with uniform thickness. Due to the characteristics of the material itself, larger glass diaphragms are prone to segmented vibrations during operation. Therefore, glass diaphragms are only used in small-sized loudspeakers, and large-sized high sound pressure level tweeters cannot use glass diaphragms.

[0004] Secondly, the precision of the curved profile forming of the glass diaphragm is difficult to control, making it impossible to stably reproduce the precise curvature required by the compression driver, which affects the acoustic efficiency of the horn coupling. On the other hand, glass is brittle and has weak impact resistance and stress concentration resistance, making it prone to breakage during conventional assembly, positioning, and working stress, which greatly limits its mass production application.

[0005] Furthermore, the diaphragm of a tweeter compression driver must simultaneously withstand the dynamic sound pressure impact from the horn throat and the steady-state static pressure. Due to the inherent characteristics of the material, glass diaphragms require extremely high reliability in assembly and fixation, as well as equal stress distribution. Existing assembly structures are mostly designed for metal or composite material diaphragms, which cannot provide suitable positioning references and stress dispersion paths for glass diaphragms. This can easily lead to localized stress concentrations after diaphragm assembly, further increasing the risk of breakage and exciting abnormally high Q-value resonant modes. This can cause frequency response spikes, ringing effects, and acoustic instability at high sound pressure levels (SPL), along with increased distortion due to break-up vibrations, thus affecting the listening experience.

[0006] In addition, the glass material has a low internal damping coefficient, and the existing assembly structure cannot compensate for its damping defects through assembly design, which makes it difficult to suppress the segmented vibration in the operating frequency band, further compounding the risk of breakage and the problem of acoustic performance degradation. Summary of the Invention

[0007] (I) Technical problems to be solved In view of the above-mentioned shortcomings and deficiencies of the prior art, the present invention provides a diaphragm preparation method, a tweeter assembly and a horn-type loudspeaker, which solves the technical problems of existing diaphragms having segmented vibration, high brittleness and easy breakage, and poor stability at high sound pressure levels.

[0008] (II) Technical Solution To achieve the above objectives, the main technical solution adopted by the present invention includes: First aspect, the embodiments of the present invention provide a tweeter assembly, including a voice coil drive assembly and a diaphragm assembly. The diaphragm assembly includes a suspension edge, a diaphragm body with non-uniform thickness, a reinforcing ring, and a damping material. The edge region of the diaphragm body is nested and fixed in the reinforcing ring, and the reinforcing ring is fixedly connected to the suspension edge. The damping material tightly covers the top surface of the diaphragm body. The diaphragm body includes a central region and an edge region surrounding the central region. The thickness of the diaphragm body changes along the direction from the central region to the edge region. The voice coil drive assembly is installed on the bottom surface of the suspension edge and drives the diaphragm body to vibrate.

[0009] Optionally, the thickness of the diaphragm body gradually increases or decreases from the center to the edge; or the thickness of the diaphragm body increases or decreases in a stepwise manner from the center to the edge.

[0010] Optionally, the diaphragm body has symmetrical locally thickened areas, or the diaphragm body has asymmetrical locally thickened areas.

[0011] Optionally, the suspension includes a brim, a positioning step, and an annular mounting area. The inner side of the reinforcing ring is provided with a groove for accommodating the edge area, and a flexible buffer layer is provided in the groove. The edge area of ​​the diaphragm body is nested and fixed in the groove, and the reinforcing ring is placed on the positioning step and fixedly connected to the annular mounting area.

[0012] Optionally, damping material may be coated or bonded to the diaphragm body.

[0013] Secondly, embodiments of the present invention provide a horn-type loudspeaker, including the aforementioned tweeter assembly.

[0014] Thirdly, embodiments of the present invention provide a diaphragm fabrication method, comprising the following steps: calling acoustic simulation software and multiphysics coupling simulation software to calculate and optimize a non-uniform thickness distribution design scheme for the diaphragm body in different regions based on the acoustic performance requirements of the target loudspeaker; fabricating a forming mold with a corresponding cavity thickness distribution structure based on the non-uniform thickness distribution design scheme; placing the substrate into the forming mold to prepare a diaphragm blank with a predetermined dome shape and a non-uniform thickness distribution structure; and performing subsequent processing on the diaphragm blank to obtain a dome-shaped non-uniform diaphragm body that meets the final external dimensions.

[0015] Optionally, the design steps using acoustic simulation software and multiphysics coupling simulation software include: establishing a three-dimensional model of the dome-shaped diaphragm, inputting the mechanical parameters of the diaphragm substrate and the target frequency response curve, wherein the initial thickness of the three-dimensional model is uniform; identifying the resonance-sensitive region of the uniform thickness model at a specific frequency through simulation analysis; iteratively optimizing the thickness distribution of the diaphragm based on the simulation results, designing thickened structures in the resonance-sensitive region, and designing suitable thin structures in other regions to suppress resonance and optimize the frequency response curve, thereby obtaining a non-uniform thickness distribution design scheme for the diaphragm body in different regions.

[0016] Optionally, the cavity of the forming mold has a structure with a non-uniform thickness distribution, so that the formed diaphragm preform forms a locally thickened area, a gradually thickened area, a stepped thickness area, or any combination thereof.

[0017] (III) Beneficial Effects The beneficial effects of the present invention are as follows: 1. The present invention provides a diaphragm preparation method, a tweeter assembly, and a horn-type loudspeaker. The tweeter assembly includes a voice coil drive assembly and a diaphragm assembly. The diaphragm assembly includes a suspension edge, a diaphragm body with non-uniform thickness, a reinforcing ring, and a damping material. The edge area of ​​the diaphragm body is nested and fixed in the reinforcing ring. The reinforcing ring is fixedly connected to the suspension edge. The damping material tightly covers the top surface of the diaphragm body. The diaphragm body adopts a non-uniform thickness design scheme, which optimizes the local structural stiffness distribution of the diaphragm body, directly improves the natural resonant frequency of the diaphragm body, and effectively suppresses split vibration. The reinforcing ring disperses the working stress of the diaphragm body, and the damping material further suppresses resonance and split vibration. The three together solve the inherent defects of the diaphragm body in the tweeter compression driver, taking into account both acoustic performance and structural reliability. Compared with the prior art, it solves the technical problems of existing diaphragms having split vibration, high brittleness and easy breakage, and poor stability at high sound pressure levels.

[0018] 2. Since the diaphragm fabrication method directly uses the target frequency response curve as the optimization target, the resonance sensitive area of ​​the uniform thickness model is analyzed by simulation software, and the model is locally thickened. The non-uniform thickness distribution scheme of the diaphragm body is designed in reverse, and then the dome-shaped non-uniform diaphragm body is obtained. The local structural stiffness distribution of the diaphragm body is optimized, which directly improves the natural resonant frequency of the diaphragm body. It is far away from the resonance condition in the target frequency band and effectively suppresses the split vibration.

[0019] 3. The edge area of ​​the diaphragm body is assembled with the reinforcing ring, which disperses the working stress of the diaphragm body, greatly improves the diaphragm body's impact and vibration resistance, effectively reduces the risk of glass breakage, breaks the application limitations of brittle materials in high-frequency compression drivers, and extends the product's service life.

[0020] 4. Damping materials enable the brittle and easily broken diaphragm body to withstand greater pressure, increase the damping coefficient within the diaphragm body, effectively suppress resonance and split vibration, reduce high Q value resonance, reduce acoustic distortion, and work in synergy with the diaphragm body to significantly improve acoustic stability at high sound pressure levels and enhance the diaphragm body's ability to withstand high sound pressure. Attached Figure Description

[0021] Figure 1 is a flowchart of the diaphragm preparation method of Embodiment 1 of the diaphragm preparation method, tweeter assembly, and horn-type loudspeaker of the present invention; Figure 2 is one of the exploded view diagrams of the diaphragm assembly of Embodiment 2 of the diaphragm preparation method, tweeter assembly, and horn-type loudspeaker of the present invention; Figure 3 is another exploded view diagram of the diaphragm assembly of Embodiment 2 of the diaphragm preparation method, tweeter assembly, and horn-type loudspeaker of the present invention; Figure 4 is a top view of the diaphragm assembly of Embodiment 2 of the diaphragm preparation method, tweeter assembly, and horn-type loudspeaker of the present invention; Figure 5 is a front view (partially thickened) of the diaphragm body of Embodiment 2 of the diaphragm preparation method, tweeter assembly, and horn-type loudspeaker of the present invention; Figure 6 is a cross-sectional view of the diaphragm body along AA in Figure 5; Figure 7 Figure 8 is a cross-sectional view of the diaphragm body (thin at the center / thick at the edge) of Embodiment 3 of the diaphragm preparation method, tweeter assembly, and horn-type loudspeaker of the present invention; Figure 9 is a cross-sectional view of the diaphragm body (thick at the center / thin at the edge) of Embodiment 4 of the diaphragm preparation method, tweeter assembly, and horn-type loudspeaker of the present invention; Figure 10 is a cross-sectional view of a conventional uniform thickness diaphragm; Figure 11 is a schematic diagram of the vibration behavior of a conventional uniform thickness diaphragm; Figure 12 is a frequency response curve and structural splitting vibration behavior diagram of a conventional uniform thickness diaphragm; Figure 13 is a frequency response curve and structural splitting vibration behavior diagram of the diaphragm body in Figure 9.

[0022] Explanation of reference numerals in the attached drawings: 1. Suspension edge; 11. Cap brim; 12. Positioning step; 13. Annular mounting area; 2. Diaphragm body; 21. Center area; 22. Edge area; 23. Locally thickened area; 3. Reinforcing ring; 4. Damping material; 41. Connecting strip; 42. Concentric ring; 5. Diaphragm. Detailed Implementation

[0023] To better explain and facilitate understanding of the present invention, a detailed description of the invention is provided below with reference to the accompanying drawings and specific embodiments. In this document, directional terms such as "upper" and "lower" refer to the orientation shown in Figure 2, with "upper" referring to the direction of the damping material 4 and "lower" referring to the direction of the suspension edge 1.

[0024] To better understand the above technical solutions, exemplary embodiments of the present invention will be described in more detail below with reference to the accompanying drawings. Although exemplary embodiments of the present invention are shown in the drawings, it should be understood that the present invention can be implemented in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that the present invention can be understood more clearly and thoroughly, and that the scope of the present invention can be fully conveyed to those skilled in the art.

[0025] Example 1, referring to Figure 1, this example provides a diaphragm preparation method, taking a glass diaphragm as an example, including the following steps: S11, calling acoustic simulation software and multiphysics coupling simulation software, calculating and optimizing the non-uniform thickness distribution design scheme of the dome-shaped diaphragm body 2 in different regions according to the acoustic performance requirements of the target loudspeaker.

[0026] In some feasible solutions, step S11 specifically includes the following steps: establishing a three-dimensional model of the dome-shaped diaphragm, inputting the mechanical parameters of the diaphragm substrate and the target frequency response curve, wherein the initial thickness of the three-dimensional model is a uniform thickness; identifying the resonance-sensitive region of the uniform thickness model at a specific frequency through simulation analysis; iteratively optimizing the thickness distribution of the diaphragm based on the simulation results, designing a thickened structure in the resonance-sensitive region, and designing a suitable thin structure in other regions to suppress resonance and optimize the frequency response curve, thereby obtaining a non-uniform thickness distribution design scheme for the diaphragm body 2 in different regions.

[0027] Specifically, first, a three-dimensional model of a dome-shaped diaphragm with a uniform initial thickness (e.g., 0.15 mm) is established, and the mechanical parameters (density, elastic modulus, Poisson's ratio) of the diaphragm substrate are input. The target frequency response curve is set to fluctuate less than ±4 dB within the 1.5 kHz–18 kHz frequency band. Through modal analysis and frequency response analysis, resonance-sensitive regions (manifested as significantly increased local amplitude) in the 10 kHz–15 kHz range are identified. Subsequently, iterative optimization is performed, gradually increasing the thickness parameters of the finite element mesh elements in the identified resonance-sensitive regions. At the same time, to prevent excessive increase in overall mass, the thickness in non-sensitive regions is appropriately reduced. After each iteration, the frequency response curve is recalculated until the resonance peak in the target frequency band is reduced to below 4 dB of the reference sound pressure level, and the upper limit frequency of the piston-type vibration band is pushed up to above 19 kHz. Finally, a three-dimensional digital model with a non-uniform thickness distribution containing thickness coordinate data for each region is output.

[0028] S12. Based on the non-uniform thickness distribution design scheme, prepare a forming mold with a corresponding cavity thickness distribution structure.

[0029] Based on the non-uniform thickness distribution design scheme obtained in S11, precision CNC electrical discharge machining technology is used to machine upper and lower molds with corresponding cavities on the mold steel. The curved surface shape of the cavity matches the target dome shape of the diaphragm body 2, and the gap distribution between the upper and lower molds corresponds to the non-uniform thickness design scheme of the diaphragm body 2. The mold surface needs to be polished to mirror level (Ra ≤ 0.1μm) to reduce molding resistance and ensure the surface finish of the diaphragm body 2.

[0030] S13. Place the substrate into the forming mold to prepare a diaphragm blank with a predetermined dome shape and a non-uniform thickness distribution structure.

[0031] The substrate is a circular borosilicate glass plate substrate with an elastic modulus ranging from 70 to 90 GPa, a softening point temperature of 820 to 860℃, and a coefficient of thermal expansion of (3.2 to 4.0) × 10⁻⁶. -6 / K. The borosilicate glass disc substrate is placed into a forming mold and hot-pressed. Its thickness is usually 0.1mm to 0.3mm, depending on the final diaphragm design.

[0032] Specifically, the upper and lower molds are first preheated to 500-550℃. The substrate is then placed in the lower mold cavity and fed into a furnace. The temperature is increased to 850-880℃ at a rate of 5-10℃ / min and held for 5-15 minutes to uniformly soften the glass. The softened glass and mold are then quickly transferred to a press. A pressure of 5-20 MPa is applied at 880±10℃ and held for 30-120 seconds to completely fill the cavity and form the desired shape. After molding, the glass is slowly cooled to below 500℃ at a controlled rate of 1-3℃ / min, and then cooled to room temperature in the furnace. After cooling, the mold is opened to obtain a diaphragm preform with a non-uniform thickness distribution, consistent with the designed shape.

[0033] Because the forming mold has a cavity with a non-uniform thickness distribution structure, the substrate is heated to a softened or molten state and placed in the cavity, so that the formed diaphragm preform forms a locally thickened area 23, a gradually thickened area, a stepped thickness area, or any combination thereof.

[0034] S14. Perform subsequent processing on the diaphragm blank to obtain a dome-shaped non-uniform diaphragm body 2 that meets the final external dimensions.

[0035] The aforementioned mechanical parameters include basic parameters such as the elastic modulus, density, and Poisson's ratio of the diaphragm material. These data can be obtained from the product reports of glass material suppliers.

[0036] It should be noted that resonance refers to the phenomenon where the amplitude of the diaphragm increases sharply when the frequency of the driving signal (i.e., the electrical signal input to the voice coil of the loudspeaker) is close to or equal to the natural frequency of the diaphragm material or structure itself. Resonance causes the frequency response curve to become uneven, with peaks and valleys, thus causing sound distortion and a harsh, trailing sound (ringing effect).

[0037] The resonant sensitive region refers to a specific geometric area of ​​the diaphragm (such as a ring-shaped area or central part within a certain radius). This region has the most concentrated vibrational energy at a specific frequency and is most prone to resonance with abnormally large amplitude. It is the key part that triggers split vibration and high Q-value resonance peaks. The Q value is a parameter that measures the damping of a resonant system. High Q-value resonance refers to a strong and sharp resonance of the diaphragm at a specific frequency point. The energy is not easily dissipated. In a loudspeaker, this manifests as a prominent peak on the frequency response curve, accompanied by severe ringing effect, resulting in a harsh and unnatural sound quality.

[0038] Through simulation analysis, the software can dynamically simulate the vibration modes of the diaphragm at different frequencies. In these simulations, it can be clearly observed that at certain frequencies, the vibration amplitude of specific regions on the diaphragm is much greater than that of other regions, exhibiting strong, uncoordinated local distortion or splitting. These regions are the resonance-sensitive areas.

[0039] For ease of distinction, this application refers to the diaphragm model with uniform thickness in the prior art as diaphragm 5, and the non-uniform thickness diaphragm described in this invention as diaphragm body 2. As shown in Figure 11, diaphragm 5 has multiple dark-colored regions. These regions have high stress and deformation; that is, the dark-colored regions are the resonance-sensitive regions referred to in this application. Resonance occurs in these resonance-sensitive regions.

[0040] The substrate is a rigid material, including but not limited to glass, glass-ceramics, ceramic materials, and any combination thereof. In practical applications, the substrate can also be other materials, such as metals, polymers, and composite materials. In this application, the non-uniform thickness scheme of the diaphragm body 2 can be a continuously varying thickness gradient, a stepped thickness distribution, a multi-region thickness distribution, and any combination thereof, which can be optimized for specific vibration modes as needed. The diaphragm body 2 does not have through holes in the thickness direction.

[0041] In actual production applications, the diaphragm body 2 with non-uniform thickness distribution can be formed through other precision manufacturing processes, including but not limited to stamping, machining, chemical etching, material deposition, controlled stretching, forming processes, or combinations of the above processes. The thickness distribution scheme can be formed during the initial forming process or introduced through subsequent processing steps. During production, uniform ultra-thin glass, glass-ceramic, or ceramic is usually used as the substrate, and the design shape is obtained through precision machining. During the processing, flexible force control is used to avoid stress cracking in the glass, ensuring that the actual thickness distribution and arc contour of the diaphragm body 2 after forming are consistent with the simulation design scheme, thus realizing the mass production of the diaphragm body 2.

[0042] In some feasible solutions, the diaphragm preparation method also includes a step of strengthening the formed diaphragm body 2, which includes, but is not limited to, quenching, chemical strengthening, chemical vapor deposition or sputtering coating.

[0043] Example 2: This embodiment of the invention provides a tweeter assembly. The tweeter assembly is suitable for use with a tweeter compression driver and is applied in large-scale professional audio systems, such as the main sound reinforcement systems of concert halls, theaters, stadiums, and cinemas. It needs to meet the following acoustic performance requirements: operating frequency band of 1.5kHz-20kHz, and sensitivity ≥110 dB (1W / 1m). The tweeters are classified into woofers, midrange speakers, and tweeters according to their operating audio frequency.

[0044] Referring to Figures 2 to 4, the loudspeaker assembly includes a voice coil drive assembly and a diaphragm assembly. The diaphragm assembly includes a suspension edge 1, a diaphragm body 2 with non-uniform thickness, a reinforcing ring 3, and damping material 4. The edge region 22 of the diaphragm body 2 is nested and fixed in the reinforcing ring 3, and the reinforcing ring 3 is fixedly connected to the suspension edge 1. The damping material 4 tightly covers the top surface of the diaphragm body 2. The voice coil drive assembly is mounted on the bottom surface of the suspension edge 1 and drives the diaphragm body 2 to vibrate. The voice coil drive assembly includes a voice coil, a magnetic circuit system, and a support structure. The magnetic circuit system includes a permanent magnet, a magnetically conductive washer, and a T-iron, forming an annular magnetic gap. The voice coil is made of enameled wire wound on a voice coil frame, inserted into the magnetic gap, and fixedly connected to the center bottom of the diaphragm body 2 by an adhesive. When an audio current passes through the voice coil, the voice coil experiences a force in the magnetic field, thereby driving the diaphragm body 2 to reciprocate.

[0045] It should be noted that this application uses a glass diaphragm body 2 as an example for illustration. In practical applications, the diaphragm body 2 can be made of rigid materials such as glass, glass ceramics, ceramics, and metals. The dome-shaped non-uniform thickness diaphragm body 2 fundamentally solves the resonance concentration problem caused by uniform thickness diaphragms, suppressing these harmful resonance behaviors.

[0046] Referring to Figures 2, 5, and 6, the diaphragm body 2 includes a central region 21 and an edge region 22, and the diaphragm body 2 is provided with locally thickened regions 23. There are four locally thickened regions 23 of the diaphragm body 2, which are incomplete elliptical shapes. The remaining regions are thin regions, which are X-shaped as a whole and have the same thickness, but are thinner than the locally thickened regions 23.

[0047] It should be explained that the central region 21 is located near the center of the dome of the diaphragm body 2, and the edge region 22 is located away from the center of the dome of the diaphragm body 2. The two are relative in their location. The locally thickened region 23 can fall in the central region 21, or it can fall in the edge region 22, or it can extend from the central region 21 to the edge region 22.

[0048] In some feasible designs, the base radius R of the diaphragm body 2 is 38.1 mm, and the dome height H is 14 mm. The thickness of the X-shaped thin area is 0.125 mm, and the thickness of the locally thickened area 23 is 0.2 mm.

[0049] In actual production, the dimensions of the diaphragm body 2 are customized according to actual needs, with a maximum base radius R exceeding 100mm and a thickness of 0.05 to 0.2mm in the thin region. Regardless of the non-uniform local thickening scheme adopted, the thickness ratio of the thin region to the locally thickened region 23 ranges from 1:1.2 to 1:2, ensuring that the natural resonant frequency of the diaphragm body 2 can be increased, effectively suppressing split vibration, and simultaneously destroying the circumferential standing wave caused by rotational symmetry. This significantly reduces the resonant peak value (Q value) at specific frequencies, making the frequency response curve smoother and solving specific high-order resonance problems caused by geometric symmetry that are difficult to eliminate with conventional thickness gradients.

[0050] In actual production applications, the diaphragm body 2 can also have an asymmetrical thickened area, that is, the non-uniform thickness distribution of the diaphragm body 2 is asymmetrical relative to the central axis of the diaphragm.

[0051] Asymmetric and local thickening schemes can effectively disrupt the circumferential standing wave caused by rotational symmetry, thereby reducing the formation of high-Q resonant modes and solving specific high-order resonance problems caused by geometric symmetry that are difficult to eliminate with conventional thickness gradients. The asymmetric and local thickening design can disrupt the symmetry of the diaphragm body 2, preventing the original circumferential standing wave from forming and maintaining smoothly. The energy is dispersed and disrupted, transforming into multiple weaker and more dispersed vibration modes, thus significantly reducing the resonant peak value (Q value) at specific frequencies and making the frequency response curve smoother.

[0052] Referring to Figures 2 and 3, in some feasible solutions, the reinforcing ring 3 is an overall annular structure adapted to the edge region 22 of the diaphragm body 2. An inner groove (not shown in the figures) is provided to accommodate the edge region 22 of the diaphragm body 2. The inner wall of the groove is provided with a flexible buffer layer. This achieves a tight fit between the reinforcing ring 3 and the diaphragm body 2 while avoiding edge stress concentration caused by rigid contact, significantly improving the impact and vibration resistance of the diaphragm body 2 and solving the defect of glass's high brittleness and easy breakage. The reinforcing ring 3 is usually made of lightweight, high-strength materials, such as aluminum alloy and carbon fiber. The flexible buffer layer can be made of materials such as silicone, rubber, or sponge.

[0053] Referring to Figures 2 and 3, in some feasible solutions, the suspension edge 1 includes a brim 11, a positioning step 12, and an annular mounting area 13. The edge area 22 of the diaphragm body 2 is nested and bonded to the groove of the reinforcing ring 3. The reinforcing ring 3 and the suspension edge 1 are placed on the positioning step 12 and fixedly connected to the annular mounting area 13. The diaphragm body 2 is first nested and bonded to the groove of the reinforcing ring 3, and then the reinforcing ring 3 is positioned to the positioning step 12, achieving precise assembly of the reinforcing ring 3, the diaphragm body 2, and the suspension edge 1, facilitating the subsequent installation of the damping material 4 and ensuring assembly consistency. In the actual assembly process, the diaphragm body 2 and the groove need to be cleaned first. The diaphragm body 2 and the reinforcing ring 3 are assembled and bonded in place using special tools. Uniform pre-pressure is applied to ensure tight adhesion. After curing, a stable connection is formed, ensuring that the connection strength meets the stress requirements under various working conditions.

[0054] Referring to Figures 2 and 4, in some feasible solutions, the damping material 4 is coated or bonded to the diaphragm body 2. The damping material 4 includes concentric rings 42 and connecting strips 41. The diameters of the concentric rings 42 are different, and multiple connecting strips 41 are symmetrically arranged around the center of the concentric rings 42 and connect the concentric rings 42. In this embodiment, the damping material 4 has three concentric rings 42 with diameters increasing sequentially from the inside to the outside. The center of the concentric rings 42 coincides with the center of the diaphragm body 2. There are four connecting strips 41. One end of each connecting strip 41 is connected to the innermost concentric ring 42, and the other end is connected to the other two concentric rings 42 in sequence. The connecting strips 41 are located on the bisector of the locally thickened area 23. The damping material 4 is adapted to the positioning structure on the top surface of the diaphragm body 2 to ensure the precise placement of the damping material 4.

[0055] The damping material 4 can be an acoustically specific damping material, such as polyurethane rubber or silicone rubber. The material should meet the requirements of high temperature resistance, strong adhesion to glass, and not affect the vibration flexibility of the diaphragm body 2. The damping material 4 is placed in the central region 21 of the diaphragm body 2, converting vibrational mechanical energy into heat energy, rapidly dissipating resonant energy, and reducing the ringing effect.

[0056] Damping material 4 enables the brittle and easily broken diaphragm body 2 to withstand greater pressure, increases the internal damping coefficient of the diaphragm body 2, effectively suppresses split vibration, reduces high Q-value resonance, and reduces acoustic distortion. The synergistic effect of damping material 4 and the non-uniform thickness of the diaphragm body 2 significantly improves acoustic stability at high sound pressure levels and enhances the diaphragm body 2's ability to withstand high sound pressure. Acoustic stability includes frequency response uniformity, distortion controllability, modal robustness, and transient response fidelity.

[0057] The tweeter assembly is designed to operate in the 1.5 kHz to 20 kHz frequency range. Within this target frequency range, the diaphragm assembly, through its non-uniform thickness design, effectively suppresses breakup vibrations, resulting in a flat frequency response (fluctuations within ±4 dB), high sensitivity, high sound pressure level, and low distortion.

[0058] Example 3: This example provides a tweeter assembly.

[0059] Referring to Figure 7, unlike the speaker assembly of Embodiment 2, the thickness of the diaphragm body 2 in this embodiment gradually increases from the center to the edge. The thickness of the diaphragm body 2 is relatively thin in the central region 21, and gradually increases as it transitions radially outward to the edge region 22, thereby forming a non-uniform thickness distribution structure that is thin in the center and thick at the edges.

[0060] The diaphragm body 2 adopts a non-uniform thickness distribution structure, which is thinner at the center and thicker at the edges, thus improving the structural stiffness of the edge region 22. Since the edge region 22 typically bears significant bending stress and boundary constraints during the vibration of the diaphragm body 2, increasing the edge thickness provides a more rigid skeleton for the large-sized diaphragm body 2. This effectively improves the mechanical stability of the diaphragm body 2 at the boundaries, resisting the increased edge torsion and vibration instability caused by the increased size, and reducing edge-related structural deformation. Simultaneously, maintaining a relatively thin structure in the central region 21 helps reduce the effective vibrating mass of the diaphragm, thereby maintaining high sensitivity and good high-frequency response.

[0061] The diaphragm body 2, with a non-uniform thickness distribution that is thin at the center and thick at the edges, can suppress the cracking vibration mode caused by the edge of the diaphragm, improve the mechanical coupling between the diaphragm and its supporting structure, and maintain good high-frequency radiation efficiency while improving structural stability. It is suitable for high-power professional sound reinforcement systems, such as high-frequency horns used in stadiums and music festivals, and ensures that the diaphragm body 2 can work for a long time without damage under extremely high sound pressure levels.

[0062] It should be noted that the non-uniform thickness distribution of the diaphragm body 2, which is thin in the center and thick at the edges, can better disperse and bear the huge driving force from the voice coil drive assembly and the horn back pressure, preventing the connection from failing due to fatigue or overstress.

[0063] Example 4: This example provides a tweeter assembly.

[0064] Referring to Figure 8, unlike the speaker assembly of Embodiment 3, the thickness of the diaphragm body 2 in this embodiment gradually decreases from the center to the edge. The diaphragm body 2 has a larger thickness in the central region 21, and the thickness gradually decreases as it transitions radially outward to the edge region 22, forming a non-uniform thickness distribution structure that is thicker at the center and thinner at the edges.

[0065] The diaphragm body 2 employs a non-uniform thickness distribution scheme, thicker at the center and thinner at the edges. Increasing the thickness of the central region 21 significantly improves its stiffness. Since the central region 21 is typically associated with the dominant radial and circumferential structural resonant modes, increasing its stiffness helps shift the dominant structural failure modes to higher frequencies. The relatively thinner edge region 22 provides greater boundary compliance, helping to reduce stress concentration and allowing controlled deformation of the diaphragm body 2 at the boundaries.

[0066] The diaphragm body 2 adopts a non-uniform thickness distribution scheme with a thicker center and thinner edges, which can move the main fracture mode out of the expected operating frequency band, reduce the high Q value resonance peak caused by the vibration of the central region 21, and broaden the flat, low-distortion piston-type operating frequency band. This fundamentally reduces the chance of entering a complex segmented vibration state, thereby obtaining a clean and fast transient response, improving the overall acoustic performance, and making it suitable for high-end hi-end home audio, top-of-the-line recording studio monitor speakers and other usage scenarios.

[0067] Example 5: This example provides a tweeter assembly.

[0068] Unlike the speaker assembly in Embodiment 2, the thickness of the diaphragm body 2 in this embodiment decreases or increases in a stepped manner from the center to the edge. The diaphragm body 2 has a stepped, non-uniform thickness distribution structure in the radial direction, meaning that the diaphragm thickness varies discretely between different radial regions. Figure 9 shows the stepped reduction in thickness of the diaphragm body 2 from the center to the edge.

[0069] The stepped thickness distribution scheme, as a further optimization of the continuously varying thickness scheme, introduces intentionally designed stiffness discontinuities into the diaphragm structure. This structural discontinuity effectively disrupts the coherent standing wave structure formed during diaphragm vibration, thereby weakening the high-Q resonant modes enhanced by geometric symmetry.

[0070] Compared to a continuously varying thickness structure, a stepped thickness distribution creates a mechanical impedance mismatch in the vibration propagation path, causing vibration energy to disperse into multiple modes. Therefore, the diaphragm body 2 with a stepped thickness distribution can suppress narrowband resonance peaks, reduce the formation of structural standing waves, and improve the broadband acoustic stability and attenuation characteristics of the diaphragm. When a vibration wave reaches the boundary formed by the stepped thickening or thinning of the diaphragm body 2, its propagation path and characteristics are suddenly altered. Some energy is reflected, some is altered in propagation mode, and some may dissipate, disrupting and dispersing the original pure, strong echo (high Q-value resonance peak) into multiple more dispersed and weaker small echoes. The stepped thickness distribution design can actively interrupt the propagation and formation of harmful vibrations.

[0071] As the size of the diaphragm body 2 increases, its vibration modes become more complex, exhibiting not only radial vibrations but also complex circumferential standing waves. These circumferential standing waves are highly sensitive to geometric symmetry. The stepped thickness structure of the diaphragm body 2, especially the asymmetrical or discontinuously varying steps, can effectively disrupt the regularity of the circumferential direction, thereby preventing the formation of circumferential standing waves.

[0072] Therefore, the diaphragm body 2 with stepped thickness distribution is suitable for professional monitoring, measurement, or applications that require extremely fast transient response and no ringing effect.

[0073] In addition, the stepped thickness distribution scheme has certain advantages in manufacturing process, and the diaphragm body 2 with such stepped thickness distribution can be prepared by partition forming, machining and other processes.

[0074] It should be noted that the stepped thickness structure shown in Figure 9 is for illustrative purposes only. In actual implementation, it may include one or more concentric thickness regions, and the thickness change may be abrupt, gradual, or a combination thereof.

[0075] In summary, the continuous gradient scheme (e.g., thicker at the center / thinner at the edge) of this application shifts the main resonant frequency by changing the stiffness distribution, aiming to widen and smooth the piston working area. The stepped thickness scheme is an upgrade of the continuous gradient scheme, introducing stiffness discontinuities to disrupt the resonant modes. It not only shifts the main resonant frequency by changing the stiffness distribution but also aims to forcibly intervene in the upcoming segmented vibration outside the piston working area. The asymmetric thickening and local thickening schemes are further upgrades to the stepped thickness scheme, effectively disrupting the circumferential standing waves caused by rotational symmetry and further reducing the formation of high-Q resonant modes. Furthermore, in practical applications, these schemes can be arbitrarily combined and superimposed according to actual usage requirements. For example, based on the continuous gradient scheme, a locally thickened region 23 can be superimposed on the diaphragm body 2.

[0076] It is understood that the different thickness schemes listed in Embodiments 2, 3, 4, and 5 are various specific implementations of the non-uniform thickness design concept of the diaphragm body 2 in this invention. All four can work in conjunction with the reinforcement and stabilization system composed of the reinforcing ring 3 and the damping material 4. The non-uniform thickness design optimizes the local structural stiffness distribution of the diaphragm body 2, directly improves the natural resonant frequency of the diaphragm body 2, suppresses split vibration, and optimizes the dynamic characteristics directly from the root of resonance. The reinforcing ring 3 and the damping material 4 provide guarantees and supplements from the aspects of stabilizing the boundary of the diaphragm body 2 and attenuating vibration energy, respectively. The synergy of the three enables the speaker assembly to obtain consistent and significantly improved acoustic stability (i.e., flat frequency response, low distortion, and high reliability at high sound pressure levels) regardless of the specific non-uniform thickness distribution of the diaphragm body 2 used, breaking through the application bottleneck of the diaphragm body 2 in high-frequency compression drivers.

[0077] In actual production applications, Figure 10 shows the existing diaphragm 5 with uniform thickness. Figure 12 shows the frequency response curve and vibration behavior diagram of the dome-shaped diaphragm 5 with uniform thickness distribution, demonstrating the entire process of the diaphragm 5 from normal operation to complete failure, specifically including the piston working region (200-10KHz, vibration type is piston vibration), the transition and modal excitation region (10K-13KHz, vibration type is local modal vibration and slight split vibration), the main split resonance peak (13KHz, vibration type is main resonance), and the high-order modal disorder region (14K-20KHz, vibration type is high-order split vibration and disordered high-order modal vibration). Figure 12 includes frequency response and impedance characteristic curves. The horizontal axis represents frequency (in Hz), indicating the frequency of the input drive signal, using a logarithmic scale to more clearly show the full-frequency response characteristics and changes at key frequencies. The left vertical axis represents sound pressure level (SPL, in dB), visually showing the acoustic output efficiency and flatness of the speaker at different frequencies. The right vertical axis represents impedance (in Ω), representing the impedance of the speaker's voice coil, revealing the inherent characteristics of the speaker's mechanical vibration system. The impedance peak in the figure directly corresponds to the mechanical resonant frequency (i.e., natural frequency) of the diaphragm. In this example, the main structural split mode of diaphragm 5 appears around 13kHz, leading to increased acoustic distortion, ringing, and even mechanical failure in the high-frequency range, resulting in poor stability at high SPL levels.

[0078] Figure 13 shows the frequency response curve and vibration behavior diagram of the dome-shaped diaphragm body 2 with non-uniform thickness distribution (center thickening) of this application. The frequency response curve of Figure 13 shows the entire process from normal operation to complete failure, specifically including the improved piston working region (200-18KHz), the main split resonance peak (19KHz), and the improved higher-order mode attenuation region (19K-20KHz).

[0079] Within the piston operating region, the range of flat and smooth curves is significantly widened. In this frequency band, the diaphragm body 2 vibrates synchronously as a whole (piston), exhibiting piston-like vibration. The non-uniform thickness (center thickening) structure increases the local stiffness of the central region 21 of the diaphragm body 2, altering its overall modal distribution. This enhances the diaphragm body 2's ability to resist its own structural modal excitation over a wider frequency range, thereby extending the dominant range of overall piston-like vibration, and ensuring that the voice coil driving force's control over the diaphragm remains effective at higher frequencies.

[0080] In the main resonance region, the sharp main resonance peak shifts significantly from 13kHz in Figure 12 to 19kHz. The peak height is noticeably reduced, and the peak shape becomes wider and flatter (i.e., the Q value decreases). The subsequent curve drop and oscillation are also relatively milder. Due to the thickening of the center of the diaphragm body 2, the natural frequency of the main structure splitting mode is increased (to 19kHz). The diaphragm body 2 requires higher energy (corresponding to a higher frequency) to excite the same level of splitting. The non-uniform thickness structure of the diaphragm body 2 disrupts the regular and efficient resonance conditions of a uniform thickness diaphragm, making the vibration energy more dispersed and suppressing the intensity of the resonance (i.e., the Q value).

[0081] In the high-order mode attenuation region, the curve decays more smoothly after the peak, with less undulation. Because the main split mode is elevated and weakened, the onset point of subsequent high-order split vibrations and modal disorder is also delayed, improving the overall stability of the high-frequency band. The discontinuous mechanical impedance caused by the non-uniform thickness structure makes it difficult for vibrational energy to form highly coherent standing waves, thus improving the acoustic stability and attenuation characteristics in the high-frequency band.

[0082] Furthermore, the main impedance peak of the impedance curve in Figure 12 appears at 13kHz, which corresponds to the mechanical resonant frequency of diaphragm 5 and the sound pressure level resonant peak frequency. The peak of the main impedance peak in the impedance curve in Figure 13 appears at 19kHz, which corresponds to the mechanical resonant frequency of diaphragm body 2 and the sound pressure level resonant peak frequency. The audible frequency range for the human ear is 20-20kHz, while the main harmful resonances (segmented vibrations) of diaphragm 5 and diaphragm body 2 occur in the high-frequency region sensitive to the human ear.

[0083] Therefore, it can be seen that the non-uniform thickness design of the diaphragm body 2 of the present invention not only changes the acoustic output (frequency response curve), but also fundamentally changes the resonance characteristics of the diaphragm body 2, pushing its main resonant frequency from 13kHz to 19kHz. In other words, the non-uniform thickness design scheme of the present invention optimizes the local structural stiffness distribution of the diaphragm body 2, directly increasing the inherent resonant frequency of the diaphragm body 2, and pushing its main structural split mode (i.e., the harmful high Q value resonance peak) to a higher frequency (from 13kHz as shown in Figure 12 to 19kHz as shown in Figure 13), with a relative frequency increase of 46%. This design significantly broadens the effective frequency range of the diaphragm body 2 moving in the form of an integral piston, so that the main vibration mode of the diaphragm body 2 is close to the ideal piston motion in the 1.5k-18kHz operating frequency band, thereby effectively suppressing the split vibration that may occur in this frequency band and cause serious distortion.

[0084] Example 6: Based on Examples 1 to 5, this example provides a horn-type loudspeaker, including a horn and a tweeter compressor driver composed of the aforementioned tweeter assembly. The horn is mounted above the tweeter compressor driver, and the two are connected together. The diaphragm body 2 pushes the air in the front compression chamber, and the generated high sound pressure sound wave is guided by the phase plug and enters the horn from the narrow throat, thereby radiating sound energy. This application improves the diaphragm assembly and applies it to products such as tweeter assemblies and horn-type loudspeakers. The voice coil driver assembly and the horn are existing products on the market and will not be described in detail here.

[0085] In the description of this invention, it should be understood that the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified.

[0086] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; 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; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0087] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first and second features are in direct contact, or that they are in indirect contact through an intermediate medium. Furthermore, "above," "over," or "on top" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," or "beneath" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0088] In the description of this specification, the terms "one embodiment," "some embodiments," "embodiment," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0089] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make modifications, alterations, substitutions and variations to the above embodiments within the scope of the present invention.

Claims

1. A tweeter assembly suitable for a tweeter compression driver, characterized in that: The device includes a voice coil drive assembly and a diaphragm assembly. The diaphragm assembly includes a suspension edge (1), a dome-shaped non-uniform thickness diaphragm body (2), a reinforcing ring (3), and a damping material (4). The diaphragm body (2) is fixedly installed between the suspension edge (1) and the reinforcing ring (3). The damping material (4) tightly covers the top surface of the diaphragm body (2). The diaphragm body (2) includes a central region (21) and an edge region (22) surrounding the central region (21). The thickness of the diaphragm body (2) varies along the direction from the central region (21) to the edge region (22). The voice coil drive assembly is installed on the bottom surface of the suspension edge (1) and drives the diaphragm body (2) to vibrate.

2. The tweeter assembly as described in claim 1, characterized in that: The thickness of the diaphragm body (2) gradually increases or decreases from the center to the edge, or the thickness of the diaphragm body (2) increases or decreases in a stepwise manner from the center to the edge, so as to destroy the resonance sensitive area of ​​the diaphragm body (2) in the high-frequency region and increase its inherent resonance frequency.

3. The tweeter assembly as described in claim 1, characterized in that: The diaphragm body (2) has a symmetrical local thickened area (23), or the diaphragm body (2) has an asymmetrical local thickened area (23) to destroy the resonance sensitive area of ​​the diaphragm body (2) in the high frequency region, increase its inherent resonance frequency, and reduce high Q value resonance.

4. A tweeter assembly as described in any one of claims 2 or 3, characterized in that: The suspension edge (1) includes a brim (11), a positioning step (12), and an annular mounting area (13); the inner side of the reinforcing ring (3) is provided with a groove for accommodating the edge area (22), and the inner wall of the groove is provided with a flexible buffer layer; the edge area (22) of the diaphragm body (2) is nested and fixed in the groove, and the reinforcing ring (3) is placed on the positioning step (12) and fixedly connected with the annular mounting area (13).

5. A tweeter assembly as described in claim 4, characterized in that: The damping material (4) is coated or bonded to the diaphragm body (2).

6. A horn-type loudspeaker, characterized in that: Includes a tweeter assembly as described in any one of claims 1 to 5.

7. A method for preparing a diaphragm, characterized in that, Includes the following steps: Using acoustic simulation software and multiphysics coupling simulation software, based on the acoustic performance requirements of the target loudspeaker, the non-uniform thickness distribution design scheme of the diaphragm body (2) in different regions is calculated and optimized; based on the non-uniform thickness distribution design scheme, a forming mold with a corresponding cavity thickness distribution structure is prepared; the substrate is placed into the forming mold to prepare a diaphragm blank with a predetermined dome shape and non-uniform thickness distribution structure; the diaphragm blank is then processed to obtain a dome-shaped non-uniform diaphragm body (2) that meets the final external dimensions.

8. The diaphragm preparation method according to claim 7, characterized in that, The steps of calling acoustic simulation software and multiphysics coupling simulation software for design include: establishing a three-dimensional model of the dome-shaped diaphragm, inputting the mechanical parameters of the diaphragm substrate and the target frequency response curve, and the initial thickness of the three-dimensional model is uniform thickness; through simulation analysis, identifying the resonance sensitive area of ​​the uniform thickness model at a specific frequency; based on the simulation results, iteratively optimizing the thickness distribution of the diaphragm, designing a thickening structure in the resonance sensitive area, and designing a suitable thin structure in other areas to suppress resonance and optimize the frequency response curve, thereby obtaining the non-uniform thickness distribution design scheme of the diaphragm body (2) in different areas.

9. The diaphragm preparation method according to claim 7, characterized in that, The cavity of the forming mold has a non-uniform thickness distribution, so that the formed diaphragm blank can form a locally thickened area (23), a gradually thickened area, a stepped thickness area, or any combination thereof.

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