Vibration Assembly

Abstract

Disclosed is a vibration assembly (100), which includes an elastic element (110), which includes a central region (112), an edge region (114) disposed on the outer periphery of the central region (112), and a fixing region (116) disposed on the outer periphery of the edge region (114), and is configured to vibrate along a direction perpendicular to the central region (112), the central region (112) including an elastic member and a reinforcing member (120) laminated along the vibration direction, and the reinforcing member (120) has a plurality of groove structures (121) with openings facing the elastic member.

Description

[Technical Field]

[0001] TECHNICAL FIELD This disclosure relates to the field of acoustics, and more particularly to vibrating assemblies.

[0002] [Incorporated by reference] This application claims priority to a Chinese application filed on August 20, 2022, application number 202211003675.2, the entire contents of which are incorporated herein by reference. [Background technology]

[0003] A speaker typically includes three main components: a driver, a vibrating unit, and a supporting unit. The vibrating unit, also known as the load of the speaker, is primarily a vibration assembly and includes an elastic element, such as a diaphragm. The vibrating unit is an important component of a speaker. When the driving force of the driver is set, a reasonable design of the vibrating unit can ensure good mechanical impedance matching between the load and driver, thereby achieving high sound pressure levels and wide bandwidth output.

[0004] In vibration assemblies, a mass-rigidity structure made of metal such as aluminum alloy, stainless steel, titanium alloy, magnesium alloy, or magnesium-aluminum alloy is typically installed in the central region of the elastic element to improve the rigidity of the central region of the vibrating membrane and prevent sound cancellation due to split vibration modes in the range of 20 Hz to 20 kHz in the central region of the speaker's vibrating membrane. However, installing a mass-rigidity structure directly in the central region of the elastic element increases the mass of the entire vibration assembly, increasing the load on the speaker and causing impedance mismatch between the driver and load parts, resulting in a decrease in the sound pressure level output from the speaker. Summary of the Invention [Problem to be solved by the invention]

[0005] Therefore, there is a need to provide a vibrating assembly in which a reinforcing member having a groove structure is rationally located in the central region of the elastic element. [Means for solving the problem]

[0006] A vibration assembly according to one embodiment of the present specification includes an elastic element, the elastic element including a central region, an edge region disposed on the outer periphery of the central region, and a fixed region disposed on the outer periphery of the edge region, and is configured to vibrate along a direction perpendicular to the central region, the central region including an elastic member and a reinforcing member stacked along the vibration direction, and the reinforcing member having a plurality of groove structures with openings facing the elastic member.

[0007] In some embodiments, the reinforcing member has an openwork structure in areas other than the groove structure.

[0008] In some embodiments, the ratio of the projected area of ​​the reinforcing member to the projected area of ​​the central region in the vibration direction is in the range of 0.15 to 0.8.

[0009] In some embodiments, the ratio of the projected area of ​​the reinforcing member to the projected area of ​​the central region in the vibration direction is in the range of 0.35 to 0.65.

[0010] In some embodiments, the vibrating assembly exhibits a resonance peak in the range of at least 10,000 Hz to 20,000 Hz when vibrating.

[0011] In some embodiments, the groove structure has a height dimension along the vibration direction, a sidewall of the groove structure has a thickness dimension, and a ratio of the height dimension to the thickness dimension is in a range of 7.14 or greater.

[0012] In some embodiments, the ratio of the height dimension to the thickness dimension is in the range of 9 or greater.

[0013] In some embodiments, the vibrating assembly exhibits a resonance peak in the range of at least 5000 Hz to 10000 Hz when vibrating.

[0014] In some embodiments, the groove structure has a height dimension along the vibration direction, and the value of the height dimension is in the range of 50 μm to 500 μm.

[0015] In some embodiments, the height dimension is in the range of 200 μm to 350 μm.

[0016] In some embodiments, the sidewalls of the trench structure have a thickness dimension, the thickness dimension having a value in the range of 50 μm or less.

[0017] In some embodiments, the thickness dimension has a value in the range of 40 μm or less.

[0018] In some embodiments, the opening of the groove structure is provided with a skirt structure extending along the surface of the elastic member, and the width of the skirt structure is in the range of 100 μm to 300 μm.

[0019] In some embodiments, the width of the skirt structure is in the range of 100 μm to 200 μm.

[0020] In some embodiments, the shape of the groove structure comprises at least one of a U-shape, a T-shape, an U-shape, and a cone-shape.

[0021] In some embodiments, the Young's modulus of the material of the reinforcing member is higher than the Young's modulus of the material of the elastic member.

[0022] In some embodiments, the material of the reinforcing member is the same as the material of the elastic member.

[0023] In some embodiments, a filler material is disposed within the groove structure, the filler material having a Young's modulus that is less than the Young's modulus of the material of the reinforcing member.

[0024] A vibration assembly according to one embodiment of the present specification includes an elastic element, the elastic element including a central region, an edge region disposed around the periphery of the central region, and a fixed region disposed around the periphery of the edge region, and is configured to vibrate along a direction perpendicular to the central region, the central region including a reinforcing region and an elastic region arranged in parallel, and the reinforcing region having a plurality of groove structures with openings facing the vibration direction.

[0025] In some embodiments, the ratio of the projected area of ​​the reinforced region to the projected area of ​​the central region in the vibration direction is in the range of 0.15 to 0.8.

[0026] In some embodiments, the ratio of the projected area of ​​the reinforced region to the projected area of ​​the central region in the vibration direction is in the range of 0.35 to 0.65.

[0027] In some embodiments, the vibrating assembly exhibits a resonance peak in the range of at least 10,000 Hz to 20,000 Hz when vibrating.

[0028] In some embodiments, the groove structure has a height dimension along the vibration direction, a sidewall of the groove structure has a thickness dimension, and a ratio of the height dimension to the thickness dimension is in a range of 7.14 or greater.

[0029] In some embodiments, the ratio of the height dimension to the thickness dimension is in the range of 9 or greater.

[0030] In some embodiments, the vibrating assembly exhibits a resonance peak in the range of at least 5000 Hz to 10000 Hz when vibrating.

[0031] In some embodiments, the groove structure has a height dimension along the vibration direction, and the value of the height dimension is in the range of 50 μm to 500 μm.

[0032] In some embodiments, the height dimension is in the range of 200 μm to 350 μm.

[0033] In some embodiments, the sidewalls of the trench structure have a thickness dimension, the thickness dimension having a value in the range of 50 μm or less.

[0034] In some embodiments, the thickness dimension has a value in the range of 40 μm or less.

[0035] In some embodiments, the opening of the groove structure is provided with a skirt structure connected to the elastic region, and the width of the skirt structure is in the range of 100 μm to 300 μm.

[0036] In some embodiments, the width of the skirt structure is in the range of 100 μm to 200 μm.

[0037] In some embodiments, the shape of the groove structure comprises at least one of a U-shape, a T-shape, an U-shape, and a cone-shape.

[0038] In some embodiments, the Young's modulus of the material of the reinforced region is higher than the Young's modulus of the material of the elastic region.

[0039] In some embodiments, the material of the reinforced region is the same as the material of the elastic region.

[0040] In some embodiments, a filler material is disposed within the groove structure, the filler material having a Young's modulus that is smaller than the Young's modulus of the material of the elastic element.

[0041] The present specification is further illustrated by exemplary embodiments, which are not limiting and will be described in detail with reference to the drawings, in which like numbers refer to like structures. [Brief explanation of the drawings]

[0042] [Figure 1] 1 is a schematic diagram of a vibrating assembly and its equivalent vibration model, according to some embodiments herein. [Figure 2]FIG. 10 illustrates a deformation diagram of a vibration assembly at a first resonance peak according to some embodiments herein. [Figure 3] FIG. 10 illustrates a deformation diagram of a vibration assembly at a second resonance peak according to some embodiments herein. [Figure 4] FIG. 10 is a deformation diagram of a vibration assembly according to some embodiments herein at a third resonance peak. [Figure 5A] FIG. 1 is a frequency response curve diagram of a vibration assembly in accordance with some embodiments herein. [Figure 5B] FIG. 10 is a frequency response curve diagram for a vibration assembly according to some embodiments herein that does not have a third resonant peak. [Figure 6] 10A and 10B are frequency response curve diagrams of a vibrating assembly including a groove structure and a vibrating assembly without a groove structure, according to some embodiments herein. [Figure 7A] 1 is a schematic diagram of a reinforcing member having a groove structure and an elastic element according to some embodiments of the present disclosure; [Figure 7B] 1 is a schematic diagram of a reinforcing member having a groove structure and an elastic element according to some embodiments of the present disclosure; [Figure 7C] 1 is a schematic diagram of a reinforcing member having a groove structure and an elastic element according to some embodiments of the present disclosure; [Figure 7D] 1 is a schematic diagram of a reinforcing member having a groove structure and an elastic element according to some embodiments of the present disclosure; [Figure 7E] 1 is a schematic diagram of a reinforcing member having a groove structure and an elastic element according to some embodiments of the present disclosure; [Figure 7F] 1 is a schematic diagram of a reinforcing member having a groove structure and an elastic element according to some embodiments of the present disclosure; [Figure 7G] 1 is a schematic diagram of a reinforcing member having a groove structure and an elastic element according to some embodiments of the present disclosure; [Figure 8] 1 is a schematic diagram of a groove structure according to some embodiments of the present disclosure; [Figure 9]FIG. 10 is another frequency response curve diagram of a vibration assembly in accordance with some embodiments herein. [Figure 10] 10A-10C are frequency response curve diagrams of a vibrating assembly corresponding to stiffening members of different heights, in accordance with some embodiments herein. [Figure 11] 10A-10C are frequency response curve diagrams of a vibrating assembly corresponding to stiffening members of different thicknesses, in accordance with some embodiments herein. [Figure 12] 1 is a schematic diagram of a skirt structure according to some embodiments herein. [Figure 13] 10A-10C are frequency response curve diagrams of a vibrating assembly corresponding to stiffening members with different skirt structure widths, according to some embodiments herein. [Figure 14A] 1A to 1C are schematic diagrams illustrating a manufacturing process of a non-metallic reinforcing member according to some embodiments of the present disclosure. [Figure 14B] FIG. 14B is a schematic diagram of a model corresponding to FIG. 14A. [Figure 15A] 1A to 1C are schematic diagrams illustrating a manufacturing process of a reinforcing member made of a metal material according to some embodiments of the present disclosure. [Figure 15B] FIG. 15B is a schematic diagram of a model corresponding to FIG. 15A. [Figure 16] 1 is a schematic diagram of a vibration assembly having a stiffening member with a single ring structure, according to some embodiments of the present disclosure; [Figure 17] 1 is a partial schematic diagram of a vibration assembly according to some embodiments of the present disclosure. [Figure 18] FIG. 10 is a schematic diagram of deformation at a third resonance peak of a vibration assembly according to some other embodiments herein. [Figure 19] FIG. 10 is a schematic diagram illustrating deformation at a third resonance peak of a vibration assembly according to some other embodiments herein. [Figure 20] FIG. 20 is a frequency response curve diagram of the vibration assembly shown in FIG. 19. [Figure 21] FIG. 10 is another frequency response curve diagram of a vibration assembly in accordance with some embodiments herein. [Figure 22A]FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 22B] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 23A] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 23B] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 23C] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 23D] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 24A] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 24B] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 25A] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 25B] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 25C] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 25D] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 25E] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 26A] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 26B] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 27A] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 27B]FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 27C] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 28] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 29] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 30A] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 30B] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 30C] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 30D] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 30E] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 31] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 32] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 33A] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 33B] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 34A] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 34B] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 34C] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 35A]FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 35B] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 35C] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 35D] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. DETAILED DESCRIPTION OF THE INVENTION

[0043] In order to more clearly explain the technical means of the embodiments of the present specification, the drawings necessary for the description of the embodiments will be briefly described below. Obviously, the drawings described below are only a part of the examples or embodiments of the present specification, and those skilled in the art can apply the present specification to other similar scenarios based on these drawings without any creative effort. Unless otherwise clear from the context or described otherwise, the same symbols in the drawings represent the same structures or operations.

[0044] It should be understood that the terms "system," "device," "unit," and / or "module" used herein are ways of distinguishing between various assemblies, elements, components, parts, or structures at different levels, however, other terms may be used in place of the above terms if they achieve the same purpose.

[0045] As used in this specification and claims, unless the context clearly dictates otherwise, terms such as "a," "one," "one kind," and / or "the" do not specifically refer to the singular but may include the plural. In general, the terms "comprise" and "containing" are intended to indicate only the inclusion of explicitly identified steps and elements; these steps and elements are not an exclusive list, and a method or apparatus may include other steps or elements.

[0046] Flowcharts are used herein to describe operations performed by systems according to embodiments of the present invention. It should be understood that the preceding and following operations are not necessarily performed in exact order. Instead, steps may be processed in reverse order or simultaneously. Also, other operations may be added to these processes, or one or more operations may be removed from these processes.

[0047] The embodiments of the present specification provide a vibration assembly applicable to various acoustic output devices. Examples of acoustic output devices include, but are not limited to, speakers and hearing aids. The vibration assembly according to the embodiments of the present specification mainly includes an elastic element, which may be connected to a speaker driver, and an edge of the elastic element is fixed (e.g., connected to the speaker housing). In a speaker, the speaker driver serves as an electrical-mechanical energy conversion unit, converting electrical energy into mechanical energy to provide a driving force to the speaker. The vibration assembly receives force or displacement transmitted from the driver and generates a corresponding vibration output, thereby pushing and moving air to generate sound pressure. The elastic element is connected to an air inertial load by a spring and damping, and can be considered to realize the radiation of sound pressure by pushing and moving air.

[0048] The elastic element mainly includes a central region, an edge region located around the periphery of the central region, and a fixed region located around the periphery of the edge region. In some embodiments, to ensure that the speaker has a flat sound pressure level output over a wide range (e.g., 20 Hz to 20 kHz), a certain pattern is designed in the edge region of the elastic element to destroy the vibration mode in the corresponding frequency band of the edge region of the elastic element, thereby avoiding sound cancellation due to localized split vibration of the elastic element, and the pattern design improves the local stiffness of the elastic element. Furthermore, by designing a thick structure in the central region of the elastic element, the stiffness of the central region of the elastic element is improved, preventing sound cancellation due to split vibration modes in the range of 20 Hz to 20 kHz in the central region of the elastic element of the speaker. However, directly designing a thick layer in the central region of the elastic element increases the mass of the entire vibration assembly, increases the load on the speaker, causes impedance mismatch between the drive end and the load end, and reduces the sound pressure level output from the speaker. In a vibration assembly according to an embodiment of the present specification, the central region of the elastic element is designed so that the central region of the elastic element includes an elastic member and a reinforcing member stacked along the vibration direction, and the reinforcing member has multiple groove structures with openings facing the elastic member. In another embodiment of the present specification, the central region of the elastic element is designed so that the central region includes a reinforcing region and an elastic region arranged in parallel, and the reinforcing region has multiple groove structures with openings facing the vibration direction. The reinforcing region may correspond to a projection area of ​​the reinforcing member onto the elastic member along the vibration direction. By designing the reinforcing member / reinforcing region with a groove structure, the vibration assembly exhibits required higher-order modes at mid- to high frequencies (3 kHz or higher). By designing the arrangement and dimensions of the reinforcing member / reinforcing region with a groove structure, three or fewer resonance peaks appear in an appropriate frequency band of the vibration assembly's frequency response curve. Furthermore, the vibration assembly has high sensitivity over a wide frequency range. By providing the reinforcing member / reinforcing region with a groove structure, the vibration assembly has a small mass and high rigidity, improving the overall sensitivity of the speaker. For specific details regarding the vibration assembly, the elastic element, and the reinforcing member / reinforcing region, please refer to the related descriptions below.

[0049] Please refer to FIG. 1, which is a schematic diagram of a vibrating assembly and its equivalent vibration model, according to some embodiments herein.

[0050] In some embodiments, the vibrating assembly 100 mainly includes an elastic element 110, which includes a central region 112, an edge region 114 located around the periphery of the central region 112, and a fixing region 116 located around the periphery of the edge region 114. The elastic element 110 is configured to vibrate along a direction perpendicular to the central region 112 and transmits the force and displacement received by the vibrating assembly 100 to push and move air. The central region 112 includes an elastic member and a reinforcing member 120 stacked along the vibration direction. The vibration direction is the vibration direction of the elastic element 110, i.e., a direction perpendicular to the central region 112. In FIG. 1, the vibration direction is a direction perpendicular to the plane of the paper in FIG. 1. In some embodiments, the elastic member may be a portion located in the central region of the elastic element 110. The reinforcing member 120 is connected to the elastic member and includes a groove structure 121 (shown in FIG. 7A ), with the opening of the groove structure 121 facing the elastic member. In some embodiments, the reinforcing member 120 includes one or more annular structures 122 and one or more elongated structures 124, each of which is connected to at least one of the one or more annular structures 122. A groove structure 121 is provided in a cross section of the elongated structures 124 and / or the annular structures 122. By rationally arranging the reinforcing member 120, the local stiffness of the central region 112 of the elastic element 110 can be controllably adjusted, and sound cancellation due to split vibration modes in a wide range (e.g., 20 Hz to 20 kHz) in the central region 112 of the elastic element 110 of the vibration assembly 100 can be avoided, and the vibration assembly 100 can have a flat sound pressure level curve. By connecting one or more elongated structures 124 and one or more annular structures 122 to each other and arranging them to surround the openwork structure, the reinforcing member 120 has an appropriate ratio of groove structure (i.e., elongated structures 124 or annular structures 122) and openwork structure (i.e., openwork portion), reducing the mass of the reinforcing member 120 and improving the sensitivity of the entire vibration assembly 100. Furthermore, by designing the shape, dimensions and number of the elongated structures 124 and / or annular structures 122 and groove structures 121, the positions of multiple resonant peaks of the vibration assembly 100 can be adjusted to control the vibration output of the vibration assembly 100.

[0051] In some embodiments, the central region 112 includes a juxtaposed reinforcing region and an elastic region (see FIG. 7F ), where the reinforcing region and the elastic region may be a reinforcing member 120 and an elastic member, respectively. In this case, the elastic member is connected to a side of the reinforcing member 120 structure (e.g., a skirt structure of the groove structure 121). The reinforcing member 120 includes one or more annular structures 122 and one or more elongated structures 124, each of which is connected to at least one of the one or more annular structures 122. The groove structure 121 is disposed on a cross-section of the elongated structure 124 and / or the annular structure 122, and the groove structure 121 has an opening formed in the vibration direction.

[0052] The elastic element 110 may be an element that can be elastically deformed by an external load. In some embodiments, when the vibration assembly 100 is applied to a vibration sensor or speaker, the elastic element 110 may be a heat-resistant material to maintain performance during the manufacturing process. In some embodiments, the Young's modulus and shear modulus of the elastic element 110 do not change or change only slightly (e.g., within 5%) when the elastic element 110 is in an environment of 200°C to 300°C. The Young's modulus may represent the deformation capacity of the elastic element 110 when stretched or compressed, and the shear modulus may represent the deformation capacity of the elastic element 110 when sheared. In some embodiments, the elastic element 110 may be a material with excellent elasticity (i.e., easily elastically deformed) so that the vibration assembly 100 has excellent vibration response. In some embodiments, the material of the elastic element 110 may be one or more of an organic polymer material, a rubber-based material, etc.In some embodiments, the organic polymeric material is selected from the group consisting of polycarbonate (PC), polyamides (PA), acrylonitrile butadiene styrene (ABS), polystyrene (PS), high impact polystyrene (HIPS), polypropylene (PP), polyethylene terephthalate (PET), polyvinyl chloride (PVC), polyurethanes (PU), polyethylene (PE), phenolic resins (Phenol), and the like. The organic polymer material may be any one or a combination of the following: polyethylene naphthalate (PEN), polyethylene naphthalate two formal acid glycol ester (PF), melamine-formaldehyde resin (MF), polyarylate (PAR), polyetherimide (PEI), polyimide (PI), polyethylene naphthalate two formal acid glycol ester (PEN), polyetheretherketone (PEEK), carbon fiber, graphene, silica gel, etc. In some embodiments, the organic polymer material may be any one or a combination of the following: a rubber-based material, including, but not limited to, a gel-based material, a silicone gel-based material, an acrylic-based material, a polyurethane-based material, a rubber-based material, an epoxy-based material, a hot melt-based material, a photocurable material, etc., and preferably a silicone adhesive adhesive or a silicone sealing adhesive.

[0053] The Shore hardness of the elastic element 110 may represent resistance to local deformation. The higher the Shore hardness, the stronger the resistance to local deformation (especially plastic deformation) and the less likely local deformation occurs. In some embodiments, the Shore hardness of the elastic element 110 may be 1HA to 50HA to vibrate the elastic element 110 with an appropriate drive. In some embodiments, the Shore hardness of the elastic element 110 may be 1HA to 15HA to reduce the difficulty of vibrating the elastic element 110. In some embodiments, the Shore hardness of the elastic element 110 may be 14.9HA to 15.1HA to provide resistance to plastic deformation of the elastic element 110. The Shore hardness of the elastic element 110 may be measured using a Shore hardness tester. Specifically, a sample of the elastic element 110 is placed on a hard platform, and an appropriate force is applied to a zero-reset Shore hardness tester so that the needle of the Shore hardness tester presses vertically against the sample surface at a constant speed until the needle end face of the Shore hardness tester completely contacts the sample surface, at which point the measured value on the dial of the Shore hardness tester is recorded, which is the Shore hardness of the elastic element 110. In some embodiments, when the thickness of the elastic element 110 is thin, samples of the same specification and from the same lot can be stacked to a uniform thickness (e.g., 3 mm or more) for measurement.

[0054] The Young's modulus of the elastic element 110 can represent the ability of the elastic element 110 to elastically deform when subjected to a force. The higher the Young's modulus, the stronger the material's resistance to deformation, and the higher its stiffness and resistance to deformation. In some embodiments, the Young's modulus of the elastic element 110 is in the range of 5E8 Pa to 1E10 Pa to vibrate the elastic element 110 with an appropriate drive. In some embodiments, the Young's modulus of the elastic element 110 is in the range of 1E9 Pa to 5E9 Pa to optimize the elastic deformation capability of the elastic element 110. In some embodiments, the Young's modulus of the elastic element 110 is in the range of 1E9 Pa to 4E9 Pa to optimize the elastic deformation capability of the elastic element 110. In some embodiments, the Young's modulus of the elastic element 110 is in the range of 2E9 Pa to 5E9 Pa to optimize the elastic deformation capability of the elastic element 110. In some embodiments, the method for measuring the Young's modulus of the elastic element 110 may include various methods, such as a resonance method, a nanoindentation method, a dynamic expansion method, a visual image tracking system, and a micro-stretching composite method. For example, the elastic element 110 is a thin film material, and can excite surface acoustic waves on the surface of the thin film with a laser pulse. The velocity dispersion relationship of the surface acoustic waves is determined by the elastic modulus (Young's modulus), density, and thickness of the thin film and the substrate. Therefore, the Young's modulus, density, and thickness of the thin film can be measured by detecting the velocity of the surface acoustic waves based on the fact that the propagation speed of surface acoustic waves differs in different materials. Specifically, by comparing the velocity dispersion relationship of the sound waves detected by the acoustic detector with the dispersion relationship calculated by a theoretical model, information such as the Young's modulus, density, and thickness of the thin film can be obtained.

[0055] In some embodiments, for a given volume of the elastic element 110, to accommodate the mass of the elastic element 110, the density of the elastic element 110 is 1E3 kg / m 3 ~4E3kg / m 3 In some embodiments, to provide an appropriate mass for the elastic element 110, the density of the elastic element 110 is in the range of 1E3 kg / m 3 ~2E3kg / m 3 In some embodiments, to provide an appropriate mass for the elastic element 110, the density of the elastic element 110 is in the range of 1E3 kg / m3 ~3E3kg / m 3 In some embodiments, to avoid the mass of the elastic element 110 being too large, the density of the elastic element 110 is in the range of 1E3 kg / m 3 ~1.5E3kg / m 3 In some embodiments, to avoid the mass of the elastic element 110 being too small, the density of the elastic element 110 is in the range of 1.5E3 kg / m 3 ~2E3kg / m 3 is in the range.

[0056] The central region 112 is a region of the elastic element 110 that extends circumferentially from the center (e.g., the center of gravity) by a certain area. The central region 112 includes an elastic member and a reinforcing member 120, and the reinforcing member 120 is connected to the elastic member. In some embodiments, the elastic member may be a portion located in the central region 112 of the elastic element 110, and the elastic member and the reinforcing member 120 are stacked along the vibration direction, and the surface of the elastic member that is closest to the reinforcing member 120 is connected to the side of the reinforcing member 120 where the openings of the groove structure 121 are located. In this case, the surface of the elastic member can completely cover the reinforcing member 120, i.e., the elastic member can cover the openings of the groove structure 121 of the reinforcing member 120. In other embodiments, the elastic member (i.e., the elastic region of the central region) and the reinforcing member 120 (i.e., the reinforcing region of the central region) are arranged in parallel, and the elastic member is connected to the side of the openwork structure of the reinforcing member 120. In this case, the elastic member can cover the portion of the central region 112 that is not covered by the reinforcing member 120, i.e., the elastic member can not cover or only partially cover the openings of the groove structure 121 of the reinforcing member 120.

[0057] In some embodiments, when the vibration assembly 100 is applied to a speaker, the elastic member in the central region 112 may be directly connected to a driving unit of the speaker. In other embodiments, the reinforcing member 120 in the central region 112 may be directly connected to a driving unit of the speaker. The elastic element 110 is configured to vibrate along a direction perpendicular to the central region 112, and the elastic member in the central region 112 and the reinforcing member 120 can transmit the force and displacement of the driving unit to push and move air and output sound pressure.

[0058] The edge region 114 is located outside the central region 112. In some embodiments, the edge region 114 may be designed with a unique pattern to destroy the vibration mode of the elastic element 110 in the corresponding frequency band of the edge region 114, avoid sound cancellation caused by localized partial vibration of the elastic element 110, and improve the local stiffness of the elastic element 110 through the pattern design.

[0059] In some embodiments, the edge region 114 may include an edge structure. In some embodiments, by adjusting parameters such as the edge width and arch height of the edge structure, the stiffness of the edge region 114 corresponding to the edge structure varies, and the frequency band of the corresponding high-frequency localized split vibration mode also varies. The edge width may be the radial width of the projection of the edge region 114 along the vibration direction of the elastic element 110. The arch height is the height of the edge region 114 protruding from the central region 112 or the fixed region 116 along the vibration direction of the elastic element 110.

[0060] In some embodiments, the maximum area of ​​the projection of the outermost annular structure 122 of the reinforcing member 120 along the vibration direction of the elastic element 110 is smaller than the area of ​​the central region 112. That is, between the outermost part of the projection of the reinforcing member 120 and the edge region 114, there is an area that is not supported by the reinforcing member 120, and in this specification, the part of the central region 112 between the edge region 114 and the reinforcing member 120 is referred to as a suspension region 1121. The part of the elastic element 110 corresponding to the suspension region 1121 is also referred to as an elastic element. In some embodiments, by adjusting the maximum contour of the reinforcing member 120, the area of ​​the suspension region 1121 can be adjusted to adjust the vibration mode of the vibrating assembly.

[0061] The fixing region 116 is disposed on the outer periphery of the edge region 114. The elastic element 110 can be connected and fixed via the fixing region 116. For example, the elastic element 110 can be connected and fixed to a speaker housing or the like via the fixing region 116. In some embodiments, the fixing region 116 can be considered to be attached and fixed to the speaker housing and not involved in the vibration of the elastic element 110. In some embodiments, the fixing region 116 of the elastic element 110 can be connected to the speaker housing via a support element. In some embodiments, the support element can include a soft material that is easily deformed so that it deforms when the vibrating assembly 100 vibrates to provide a larger displacement for the vibration of the vibrating assembly 100. In other embodiments, the support element can include a hard material that is less likely to deform.

[0062] In some embodiments, the elastic element 110 may further include a connection region 115 located between the edge region 114 and the anchoring region 116. In some embodiments, the connection region 115 can adjust the modal vibration modes of the vibrating assembly 100 by providing additional stiffness and damping to the vibration of the elastic element 110.

[0063] To ensure that elastic element 110 provides appropriate stiffness, the thickness and elastic modulus of elastic element 110 can be set within a reasonable range. In some embodiments, the thickness of elastic element 110 may be in the range of 3 μm to 200 μm. In some embodiments, to avoid elastic element 110 having too high a stiffness, the thickness of elastic element 110 may be in the range of 3 μm to 100 μm. In some embodiments, to avoid elastic element 110 having too high a stiffness, the thickness of elastic element 110 may be in the range of 3 μm to 50 μm.

[0064] The reinforcing member 120 may be an element for increasing the stiffness of the elastic element 110. In some embodiments, the reinforcing member 120 is connected to the central region 112, and the reinforcing member 120 and / or the central region 112 are connected to a speaker driver to transmit force and / or displacement so that the vibrating assembly 100 pushes and moves air to output sound pressure.

[0065] In some embodiments, the reinforcing member 120 may include one or more annular structures 122 and one or more elongated structures 124, each of which is connected to at least one of the one or more annular structures 122 to provide cross support to the central region 112 of the elastic element 110. At least one of the one or more elongated structures 124 extends toward the center of the central region 112. In some embodiments, the one or more elongated structures 124 may pass through the center of the central region 112 to support the center of the central region 112. In some embodiments, the reinforcing member 120 may further include a central connector 123, where the one or more elongated structures 124 may cover the center of the central region 112 without passing through the center of the central region 112, and the one or more elongated structures 124 may be connected to the central connector 123.

[0066] In some embodiments, groove structures 121 may be provided on the cross-sections of one or more annular structures 122 and / or one or more elongated structures 124. The provision of groove structures 121 can adjust the stiffness and mass of the reinforcing member 120, avoid excessive load on the speaker, avoid impedance mismatch between the driver and load, and improve the output effect of the vibration assembly 100.

[0067] The annular structure 122 may be a structure extending around a specific center. In some embodiments, the center surrounded by the annular structure 122 may be the center of the central region 112. In other embodiments, the center surrounded by the annular structure 122 may be a location offset from the center of the central region 112. In some embodiments, the annular structure 122 may be a structure with a closed contour. In some embodiments, the shape of the annular structure 122 projected along the vibration direction of the elastic element 110 may include, but is not limited to, one or more combinations of a circular ring, a polygonal ring, a curved ring, or an elliptical ring. In other embodiments, the annular structure 122 may be a structure with an open contour. For example, the annular structure 122 may be a circular ring, a polygonal ring, a curved ring, or an elliptical ring with a cutout. In some embodiments, the number of the annular structures 122 may be one. In some embodiments, the number of the annular structures 122 may be multiple, and the multiple annular structures may have the same center of gravity. In some embodiments, the number of the annular structures 122 may be in the range of 1 to 10. In some embodiments, the number of annular structures 122 may range from 1 to 5. In some embodiments, the number of annular structures 122 may range from 1 to 3. If the number of annular structures 122 is too large, the mass of the stiffening member 120 may be too large, which may further reduce the sensitivity of the entire vibrating assembly 100. In some embodiments, the number of annular structures 122 may be designed to adjust the mass and stiffness of the stiffening member 120. In some embodiments, the dimensions of the annular structures 122 located at the outermost periphery of the stiffening member 120 may be considered the maximum dimension of the stiffening member 120. In some embodiments, by setting the dimensions of the annular structures 122 located at the outermost periphery, the size (or area) of the suspension region 1121 between the edge region 114 and the stiffening member 120 may be adjusted to change the vibration mode of the vibrating assembly 100.

[0068] In some embodiments, the one or more annular structures 122 may include a first annular structure and a second annular structure, where the radial dimension of the first annular structure is smaller than the radial dimension of the second annular structure. In some embodiments, the first annular structure is disposed inside the second annular structure. In some embodiments, the first annular structure and the second annular structure may have overlapping centers of gravity. In other embodiments, the first annular structure and the second annular structure may not have overlapping centers of gravity. In some embodiments, the first annular structure and the second annular structure may be connected via one or more elongated structures 124.

[0069] The elongated structure 124 may have any extension pattern. In some embodiments, the elongated structure 124 may extend along a straight line. In some embodiments, the elongated structure 124 may extend along a curved line. In some embodiments, extending along a curved line may include, but is not limited to, extending in an arc, a spiral, a spline curve, a circular arc, and an S-shape. In some embodiments, the elongated structure 124 is connected to the annular structure 122 to divide the annular structure 122 into multiple openwork structures. That is, the openwork structure is provided in a region of the reinforcing member 120 other than the groove structure 121. In some embodiments, the region corresponding to the openwork structure in the central region 112 may be referred to as an openwork region (i.e., an elastic region). In some embodiments, the number of the elongated structure 124 may be one. For example, one elongated structure 124 may be located along any diameter of the annular structure 122, and the elongated structure 124 may be connected to both the center of the central region (i.e., the center of gravity of the annular structure 122) and the annular structure 122. In some embodiments, the number of elongated structures 124 may be multiple. In some embodiments, multiple elongated structures 124 may be located along multiple diameters of the annular structure 122. In some embodiments, the multiple elongated structures 124 may extend toward a central location of the central region 112, which may be the center of gravity of the elastic element 110. In some embodiments, the multiple elongated structures 124 may be connected to a central location of the central region and form a central connection 123 at the central location. In some embodiments, the central connection 123 may be a separate structure, and multiple elongated structures 124 may be connected to the central connection 123. In some embodiments, the shape of the central connection 123 may include, but is not limited to, a circle, a square, a polygon, an ellipse, or the like. In some embodiments, the shape of the central connector 123 may be arbitrarily set.

[0070] In some embodiments, the number of elongated structures 124 may range from 1 to 100 to increase the stiffness of elastic element 110. In some embodiments, the number of elongated structures 124 may range from 1 to 50 to prevent elastic element 110 from being too stiff. In some embodiments, the number of elongated structures 124 may range from 1 to 40 to prevent elastic element 110 from being too stiff. In some embodiments, the number of elongated structures 124 may range from 1 to 30 to prevent elastic element 110 from being too stiff. By adjusting the number of elongated structures 124, the overall mass of vibrating assembly 100, the stiffness of stiffening member 120, and the area of ​​the openwork region of elastic element 110 can be adjusted to change the modal vibration modes of the vibrating assembly.

[0071] In some embodiments, the shape of the projection of the elongated structure 124 along the vibration direction of the elastic element 110 comprises at least one of a rectangle, a trapezoid, a curved shape, an hourglass shape, and a petal shape. By designing the elongated structure 124 with different shapes, the mass distribution of the stiffening member 120 (e.g., the location of the center of mass), the stiffness of the stiffening member 120, and the area of ​​the openwork region can be adjusted to change the modal vibration modes of the vibrating assembly.

[0072] It should be noted that in the embodiments of the present specification, the structures described for the annular structure 122 and the elongated structure 124 are merely preferred structures selected to rationally configure the structure of the reinforcing member 120, and should not be understood as limiting the shape of the reinforcing member 120 and each part thereof. In fact, in the reinforcing member 120 in the embodiments of the present specification, the annular structure 122 and the elongated structure 124 having the groove structure 121 can form an openwork structure (corresponding to the openwork region located in the central region 112) between the annular structure 122 and the elongated structure 124, and adjustment of the vibration characteristics of the vibrating assembly 100 (e.g., the number and frequency range of resonant peaks) can be achieved by adjusting the parameters of the groove structure and the openwork structure (e.g., the area, the thickness of the groove structure, etc.). In other words, for any shape of reinforcing member having a groove structure and an openwork structure, the parameter setting method for the groove structure and the openwork structure provided in this specification can be used to set the parameter, thereby achieving the goal of adjusting the vibration performance of the vibration assembly (e.g., the number and position of the resonant peaks, the shape of the frequency response curve, etc.), and all of these means should be included in the scope of this application.

[0073] In some embodiments, as shown in FIG. 1, the connection region 115 between the fixed region 116 and the edge region 114 of the elastic element 110 is installed in a suspended manner, the equivalent mass of the region is Mm1, and the region is fixedly connected to the housing via a spring Km and a damper Rm, and the connection region 115 is connected to the air load at the front end of the elastic element 110 via a spring Ka1 and a damper Ra1 to transmit force and displacement to push and move the air.

[0074] In some embodiments, the edge region 114 of the elastic element 110 has a local equivalent mass Mm2, which is connected to the connection region 115 of the elastic element 110 via a spring Ka'1 and a damping Ra'1, and the edge region 114 is connected to the air load at the front end of the elastic element 110 via a spring Ka2 and a damping Ra2 to transmit force and displacement to push and move the air.

[0075] In some embodiments, a reinforcing member 120 is installed in the central region 112 of the elastic element 110, and the reinforcing member 120 is connected to the elastic element located in the central region 112, and a partial suspension region 1121 exists between the region of the elastic element supported by the reinforcing member 120 and the edge region 114. The region has a local equivalent mass Mm3, and is connected to the edge region 114 via a spring Ka'2 and a damping Ra'2, and the region where the reinforcing member 120 is located is connected to the air load at the front end of the elastic element 110 via a spring Ka3 and a damping Ra3, transmitting force and displacement to push and move the air.

[0076] In some embodiments, depending on the design of the stiffening member 120, the central region 112 of the elastic element 110 corresponding to the stiffening member 120 may have one or more openwork regions, each of which may correspond to a mass-spring-damping system, with an equivalent mass Mm i , equivalent stiffness Ka i , Ka' i , equivalent damping Ra i , Ra' i The openwork area has a spring Ka' i , attenuation Ra' i The openwork area is further connected to the adjacent openwork area via a spring Ka'. i , attenuation Ra' i The suspension region 1121 is connected to the edge region 114 and the region supported by the reinforcing member 120 in the central region 112 via the spring Ka. i , attenuation Ra i 110 is connected to the air load at the front end of the elastic element 110 via a spring 114 to transmit force and displacement to push and move the air.

[0077] In some embodiments, the stiffening member 120 itself has an equivalent mass Mm n and the reinforcing member 120 has a spring Ka' n , attenuation Ra' n and the reinforcing member 120 is connected to the central region 112 via the spring Ka n , attenuation Ra nWhen the reinforcing member 120 itself resonates, it drives the central region 112 to drive the resilient element 110, generating a large moving speed and displacement, and thereby a high sound pressure level.

[0078] Based on the dynamic characteristics of the mass-spring-damping system, each mass-spring-damping system has its own resonant peak frequency f0 and can generate large movement speeds and displacements at f0. By designing different parameters of the vibration assembly 100 (e.g., the structural parameters of the elastic element 110 and / or the reinforcing member 120), the mass-spring-damping systems formed by the structures at different positions of the vibration assembly 100 can resonate in the required frequency band. Furthermore, the frequency response curve of the vibration assembly 100 has multiple resonant peaks, thereby greatly widening the effective frequency band of the vibration assembly 100. By designing the reinforcing member 120, the vibration assembly 100 can have a lighter mass and output a higher sound pressure level.

[0079] FIG. 2 is a diagram of deformation of a vibration assembly according to some embodiments of the present specification at a first resonance peak, FIG. 3 is a diagram of deformation of a vibration assembly according to some embodiments of the present specification at a second resonance peak, and FIG. 4 is a diagram of deformation of a vibration assembly according to some embodiments of the present specification at a third resonance peak.

[0080] As can be seen from the schematic diagram of the equivalent vibration model of the vibration assembly 100 shown in Figure 1, each part of the vibration assembly 100 resonates at a different frequency band, and by outputting a large velocity value in the corresponding frequency band, a large sound pressure value is output in the corresponding frequency band of the frequency response curve of the vibration assembly 100, and a corresponding resonance peak appears. Due to the multiple resonance peaks, the frequency response of the vibration assembly 100 has high sensitivity within the audible sound range (e.g., 20 Hz to 20 kHz).

[0081] As shown in FIGS. 1 and 2, in some embodiments, the mass of the stiffening member 120, the mass of the elastic element 110, the equivalent air mass, and the equivalent driving end mass are combined to form a total equivalent mass Mt, and the equivalent damping of each part forms a total equivalent damping Rt. The elastic element 110 (particularly the edge region 114 and the elastic element 110 in the suspension region between the edge region 114 and the stiffening member 120) has a large compliance and provides stiffness Kt to the system, forming a mass Mt-spring Kt-damping Rt system. The system has a resonant frequency, and when the excitation frequency of the driving end is close to the velocity resonant frequency of the system, the system resonates (as shown in FIG. 2), and a large velocity value v occurs in a frequency band near the velocity resonant frequency of the Mt-Kt-Rt system. a and the sound pressure amplitude and sound velocity output from the vibration assembly 100 are positively correlated (p a ∝v a), a resonance peak appears in the frequency response curve, and this resonance peak is defined herein as the first resonance peak of the vibration assembly 100. In some embodiments, as shown in FIG. 2, FIG. 2 shows the vibration situation of the vibration assembly 100 in the AA cross section, where the white structure in FIG. 2 represents the shape and position of the reinforcing member 120 before deformation, and the black structure represents the shape and position of the reinforcing member 120 at the time of the first resonance peak. Note that FIG. 2 only shows the structure situation of the vibration assembly 100 from the center of the reinforcing member 120 to one side edge of the elastic element 110 in the AA cross section, i.e., only half of the AA cross section, and the other half of the AA cross section, which is not shown, is symmetrical to the situation shown in FIG. 2. As can be seen from the vibration situation of the vibration assembly 100 in the AA cross section, at the position of the first resonance peak, the main deformation position of the vibration assembly 100 is the part of the elastic element 110 connected to the fixed region 116. In some embodiments, the frequency of the first resonant peak of the vibrating assembly 100 (also referred to as the first resonant frequency) may be related to the ratio of the mass of the vibrating assembly 100 to the elastic coefficient of the elastic element 110. In some embodiments, the frequency range of the first resonant peak is 200 Hz to 2500 Hz to improve the sound pressure level output by the speaker in a wide mid-low frequency range (e.g., 20 Hz to 3500 Hz). In some embodiments, the frequency range of the first resonant peak is 400 Hz to 1500 Hz to mainly improve the sound pressure level output by the speaker in a general mid-low frequency range (e.g., 80 Hz to 2500 Hz). Preferably, the frequency range of the first resonant peak is 500 Hz to 1200 Hz. More preferably, the frequency range of the first resonant peak is 600 Hz to 1000 Hz. In some embodiments, the first resonant peak of the vibrating assembly 100 can be set in the above frequency range by configuring the structure of the reinforcing member 120.

[0082] As shown in FIGS. 1 and 3, the reinforcing member 120 itself has an equivalent mass Mm n and the reinforcing member 120 has a spring Ka' n , attenuation Ra' n and the reinforcing member 120 is connected to the central region 112 via the spring Kan , attenuation Ra n When the reinforcing member 120 itself resonates, it drives the central region 112 to drive the resilient element 110 to generate a large moving speed and displacement, thereby generating a high sound pressure level.

[0083] The stiffening member 120, the connection region 115, the edge region 114, the suspension region 1121 between the region where the stiffening member 120 is installed in the central region 112 and the edge region 114, the equivalent air mass, and the equivalent mass at the driving end combine to form a total equivalent mass Mt1, and the equivalent damping of each part forms a total equivalent damping Rt1. The stiffening member 120 and the elastic element 110 (especially the region of the central region 112 covered by the stiffening member 120) have high stiffness and provide stiffness Kt1 to the system, forming a mass Mt1-spring Kt1-damping Rt1 system, which is configured such that an annular region in the diameter direction of the central region 112 is an equivalent fixed support point, and the stiffness Kt1 is provided within the annular region and the annular region. The connection region 115, the edge region 114, and the suspension region 1121 between the region where the reinforcing member 120 of the central region 112 is installed and the edge region 114 are driven by the reinforcing member 120 to vibrate, realizing a resonance mode (shown in FIG. 3) with the reversal motion as the vibration mode. This resonance is also at the resonance frequency point of the mass Mt1-spring Kt1-damper Rt1 system. When the excitation frequency of the driving end is close to the velocity resonance frequency of the system, the Mt1-Kt1-Rt1 system resonates, and a large velocity value v occurs in the frequency band near the velocity resonance frequency of the Mt1-Kt1-Rt1 system. a and the sound pressure amplitude and sound velocity output from the vibration assembly 100 are positively correlated (p a ∝v a), a resonance peak appears in the frequency response curve, and this resonance peak is defined herein as the second resonance peak of the vibration assembly 100. In some embodiments, as shown in FIG. 3, FIG. 3 shows the vibration situation of the vibration assembly 100 in the AA cross section, where the white structure in FIG. 3 represents the shape and position of the reinforcing member 120 before deformation, and the black structure represents the shape and position of the reinforcing member 120 at the time of the second resonance peak. Note that FIG. 3 only shows the structure situation of the vibration assembly 100 from the center of the reinforcing member 120 in the AA cross section to one side edge of the elastic element 110, i.e., only half of the AA cross section, and the other half of the AA cross section, which is not shown, is symmetrical to the situation shown in FIG. 3. As can be seen from the vibration situation of the vibration assembly 100 in the AA cross section, the main deformation position of the vibration assembly 100 around the frequency of the second resonance peak (also referred to as the second resonance frequency) is the site of reverse deformation of the reinforcing member 120. In some embodiments, the second resonance peak of the vibration assembly 100 may be related to the stiffness of the reinforcement member 120. In some embodiments, the frequency range of the second resonance peak may be 5000 Hz to 10000 Hz to improve the sound pressure level output by the speaker in a wide mid-to-high frequency range (e.g., 3500 Hz to 11000 Hz). In some embodiments, the frequency range of the second resonance peak may be 6000 Hz to 8000 Hz to mainly improve the sound pressure level output by the speaker in a general mid-to-high frequency range (e.g., 4000 Hz to 10000 Hz). Preferably, the frequency range of the second resonance peak is 6500 Hz to 7500 Hz. In some embodiments, the second resonance peak of the vibration assembly 100 can be set in the above frequency range by configuring the structure of the reinforcement member 120.

[0084] As shown in FIGS. 1 and 4, the reinforcing member 120 has one or more openwork regions corresponding to the central region 112, each openwork region being a mass-spring-damping system with an equivalent mass Mm i , equivalent stiffness Ka i , Ka' i , equivalent damping Ra i , Ra' iThe openwork area has a spring Ka' i , attenuation Ra' i and connected to the adjacent openwork area via spring Ka' i , attenuation Ra' i and the openwork area is connected to the suspension area 1121 between the area supported by the reinforcing member 120 of the central area 112 and the edge area 114 via the spring Ka i , attenuation Ra i 110 is connected to the air load at the front end of the elastic element 110 via a spring 114 to transmit force and displacement to push and move the air.

[0085] Because the openwork regions are spaced apart by the elongated structures 124 and / or the annular structures 122 of the reinforcing member 120, each openwork region can form a different resonant frequency and independently push and move the air regions connected thereto to generate a corresponding sound pressure. Furthermore, by designing the position, size, and number of each elongated structure 124 and / or the annular structures 122 of the reinforcing member 120, each openwork region can have a different resonant frequency, thereby causing one or more high-frequency resonant peaks (i.e., third resonant peaks) to appear in the frequency response curve of the vibration assembly 100. In some embodiments, the one or more high-frequency resonant peaks (i.e., third resonant peaks) may be in the range of 12,000 Hz to 18,000 Hz to improve the sound pressure level output by the speaker in a wide high-frequency range (e.g., 11,000 Hz to 20,000 Hz). In some embodiments, the frequency range of the third resonant peak may be 13,000 Hz to 17,000 Hz, primarily to improve the sound pressure level output by the speaker in a typical high frequency range (e.g., 12,000 Hz to 18,000 Hz). Preferably, the frequency range of the third resonant peak is 14,000 Hz to 16,000 Hz. More preferably, the frequency range of the third resonant peak is 14,500 Hz to 15,500 Hz.

[0086] Furthermore, to improve the sound pressure level output by vibrating assembly 100 at high frequencies (10,000 Hz to 20,000 Hz), the resonant frequencies of each openwork region are made equal or close by designing the position, size, and number of each elongated structure 124 and / or annular structure 122. In some embodiments, by setting the resonant frequency difference between each openwork region to within 4,000 Hz, a high-frequency resonant peak with a high output sound pressure level appears in the frequency response curve of vibrating assembly 100, and this resonant peak is defined herein as the third resonant peak of vibrating assembly 100. In some embodiments, the frequency range of the third resonant peak may be 12,000 Hz to 18,000 Hz.

[0087] In some embodiments, the resonant frequency of each openwork region can be adjusted by designing the area of ​​one or more openwork regions and the thickness of the elastic element 110, so that the third resonant peak of the vibrating assembly 100 is in the above frequency range. That is, the frequency range of the third resonant peak can be adjusted by designing the range of the ratio between the area of ​​each openwork region and the thickness of the elastic element 110. The area of ​​each openwork region is expressed in mm 2 The thickness of the elastic element 110 may be in mm, and the ratio of the area of ​​each openwork area to the thickness of the elastic element 110 may be in mm. Illustratively, when the area of ​​a certain openwork area is 20 mm 2and the thickness of the elastic element 110 is 0.2 mm, the ratio of the area of ​​each openwork region to the thickness of the elastic element 110 is 100 mm. In some embodiments, to achieve a third resonance peak of the vibrating assembly 100 in a frequency range of 12,000 Hz to 18,000 Hz, the ratio of the area of ​​each openwork region to the thickness of the elastic element 110 is in a range of 100 mm to 1,000 mm. In some embodiments, to achieve a third resonance peak of the vibrating assembly 100 in a frequency range of 14,000 Hz to 16,000 Hz, the ratio of the area of ​​each openwork region to the thickness of the elastic element 110 is in a range of 120 mm to 900 mm. In some embodiments, to achieve a third resonance peak of the vibrating assembly 100 in a frequency range of 14,500 Hz to 15,500 Hz, the ratio of the area of ​​each openwork region to the thickness of the elastic element 110 is in a range of 150 mm to 800 mm. In some embodiments, the ratio of the area of ​​each openwork region to the thickness of the elastic element 110 is in the range of 150 mm to 700 mm to set the third resonant peak of the vibrating assembly 100 in the frequency range of 14700 Hz to 15200 Hz.

[0088] As shown in FIG. 5A, FIG. 5A is a frequency response curve diagram of a vibration assembly according to some embodiments of the present disclosure. By designing the structures of the reinforcing member 120 and the elastic element 110, the vibration assembly 100 can have multiple resonance peaks in the audible range. Furthermore, by combining multiple resonance peaks, the vibration assembly 100 has high sensitivity across the entire audible range. By designing the structure of the reinforcing member 120, the third resonance peak 240 of the vibration assembly 100 can be achieved in a different frequency range. By designing the frequency difference between the third resonance peak 240 and the second resonance peak 230, a flat frequency response curve and a high output sound pressure level can be achieved in the frequency band between the third resonance peak 240 and the second resonance peak 230, and valleys in the frequency response curve can be avoided.

[0089] As shown in FIG. 5A, due to the design of the reinforcing member 120 and the elastic element 110, the vibration assembly 100 exhibits the required higher-order modes in the audible range (20 Hz to 20,000 Hz), and the above-mentioned first resonance peak 210, second resonance peak 230, and third resonance peak 240 appear on the frequency response curve of the vibration assembly 100, i.e., the number of resonance peaks on the frequency response curve of the vibration assembly 100 in the frequency range of 20 Hz to 20,000 Hz is three, thereby making the vibration assembly 100 have high sensitivity in a wide frequency band range.

[0090] In some embodiments, by designing the structures of the reinforcing member 120 and the elastic element 110, the vibrating assembly 100 can have only two resonance peaks in the audible range (20 Hz to 20,000 Hz). For example, by designing the structure of the reinforcing member 120 (including the overall dimensions of the reinforcing member 120, the number and dimensions of the elongated structures 124 and / or annular structures 122 having groove structures 121 in their cross sections, etc.), the size of each openwork region can be designed, thereby adjusting the resonance frequency of the corresponding suspension region 1121, so that the third resonance peak 240 formed by the vibrating assembly 100 at high frequencies is not obvious and does not appear in the frequency response curve. If the resonant frequency of each suspension area 1121 is made higher than the audible sound range, or if the resonant frequencies of each suspension area 1121 are different and different suspension areas 1121 have different vibration phases in different frequency bands in the high frequency range (10,000 Hz to 18,000 Hz), the effect of high frequency roll-off can be obtained, and the third resonant peak 240 will not appear on the sound pressure level frequency response curve of the vibration assembly 100.

[0091] 5B, which illustrates a frequency response curve diagram for a vibration assembly according to some embodiments herein without a third resonance peak. By designing the annular structure 122 and the elongated structure 124 of the reinforcing member 120, the reinforcing member 120 has one or more openwork regions corresponding to the central region 112. Each openwork region acts as a mass-spring-damping system. By designing the location, size, and number of the elongated structures 124 of the reinforcing member 120, the resonant frequencies of the openwork regions are equal or close to each other. In some embodiments, the resonant frequency difference between the openwork regions is in the range of 4000 Hz, resulting in one or more high-frequency resonance peaks (i.e., third resonance peaks) with high output sound pressure levels in the frequency response curve of the vibration assembly 100.

[0092] In some embodiments, as shown in FIG. 5B, by designing the position, dimensions, and number of each elongated structure 124 and / or annular structure 122 of the reinforcing member 120, the resonant frequency of each openwork area can be made higher than the audible sound range, or the resonant frequency of each openwork area can be made different, and different openwork areas can have different vibration phases in different frequency bands in the high frequency range (10,000 Hz to 18,000 Hz), thereby achieving the sound overlap cancellation effect. In this way, the high frequency roll-off effect can be obtained, and the third resonant peak 240 does not appear in the sound pressure level frequency response curve of the vibration assembly 100.

[0093] As shown in FIG. 6, FIG. 6 is a frequency response curve diagram of a vibration assembly including a groove structure and a vibration assembly not including a groove structure, according to some embodiments herein. In some embodiments, the mass and stiffness distribution of the stiffening member 120 can be effectively adjusted by designing the structural dimensions and shape of the stiffening member 120 having the groove structure 121. In some embodiments, changing the stiffness of the stiffening member 120 itself while leaving the mass of the stiffening member 120 unchanged or changing it changes the stiffness Kt1 provided to the system by the stiffening member 120 and the elastic element 110 (particularly the central region 112 of the elastic element 110), which in turn changes the resonant frequency of the reversal motion of the mass Mt1-spring Kt1-damping Rt1 system, thereby changing the position of the third resonance peak 240 of the vibration assembly 100. In some embodiments, reducing the mass of the stiffening member 120 without reducing the stiffness of the stiffening member 120 may improve the output of the vibration assembly 100.

[0094] As shown in Figure 6, due to the design of groove structure 121, vibration assembly 100 has a flat frequency response output in the range of 1 kHz to 6 kHz, and vibration assembly 100 forms a second resonance peak 230 and a third resonance peak 240 in the range of 6 kHz to 10 kHz and 12 kHz to 18 kHz, respectively, improving the sensitivity of the high frequency output. And, due to the design of groove structure 121, vibration assembly 100 has a highly sensitive output. Also, due to the design of groove structure 121, vibration assembly 100 has one or more resonance peaks at high frequencies, and vibration assembly 100 has a highly sensitive output over a wide frequency band.

[0095] In some embodiments, by installing the groove structure 121, the rigidity of the reinforcing member 120 and the elastic element 110 can be ensured and the mass of the reinforcing member 120 can be reduced, thereby improving the output of the vibration assembly 100 and having a positive impact on improving the performance of the vibration assembly 100.

[0096] 7A-7G are schematic diagrams of reinforcing members and elastic elements having different groove structures according to some embodiments of the present disclosure. As shown in FIGS. 7A-7E, in some embodiments, reinforcing member 120 and elastic element 110 having groove structure 121 may be separate structures, and the two may form a hollow, rigid reinforced structure after assembly and molding. In some embodiments, the width of groove structure 121 may be consistent in the vibration direction. For example, groove structure 121 shown in FIG. 7A has a square U-shaped structure, and groove structure 121 shown in FIG. 7B has a fillet U-shaped structure. In some embodiments, the width of groove structure 121 may gradually decrease or increase in the vibration direction. For example, groove structure 121 shown in FIG. 7C has a T-shaped structure, and groove structure 121 shown in FIG. 7E has a conical protrusion structure. In some embodiments, the width of groove structure 121 may vary (e.g., decrease and then increase) arbitrarily. For example, groove structure 121 shown in FIG. 7D has a U-shaped structure. By using a hollow structure, the groove structure 121 can be installed, ensuring the rigidity of the reinforcing member 120 and the elastic element 110, while reducing the mass of the reinforcing member 120, thereby improving the output of the vibration assembly 100.

[0097] As shown in FIG. 7F , in some embodiments, the reinforcing member 120 having the groove structure 121 and the elastic element 110 may be an integral structure, e.g., both may be processed and molded at the same time. In some embodiments, when an integral structure is used, the groove structure 121 may be a U-shaped structure (e.g., a square U-shaped structure as shown in FIG. 7F ) to facilitate design and manufacturing and reduce the difficulty of manufacturing. In this case, the elastic member in the central region 112 of the elastic element 110 is disposed between the groove structure 121 of the reinforcing member 120, and the elastic member is arranged as an elastic region in parallel with the reinforcing member 120, which serves as a reinforcing region. In other embodiments, the groove structure 121 may be another type of hollow structure (e.g., the U-shaped structure or T-shaped structure described above), as long as it ensures the rigidity of the reinforcing member 120 and the elastic element 110 while reducing the mass of the reinforcing member 120.

[0098] 7G , in some embodiments, a filler material may be placed in the hollow portion of groove structure 121 of reinforcement member 120 to adjust the mass and stiffness of reinforcement member 120 and improve the output of vibrating assembly 100. In some embodiments, the Young's modulus of the filler material may be smaller than the Young's modulus of the material of elastic element 110 to reduce interference of the filler material with the vibration deformation of elastic element 110. In some embodiments, the filler material may include a non-metallic material or a metallic material. In some embodiments, the non-metallic material of the filler material is selected from the group consisting of polycarbonate (PC), polyamides (PA), acrylonitrile butadiene styrene (ABS), polystyrene (PS), high impact polystyrene (HIPS), polypropylene (PP), polyethylene terephthalate (PET), polyvinyl chloride (PVC), polyurethanes (PU), polyethylene (PE), phenolic resins (Phenol), and the like. The filler material may include, but is not limited to, any one or combination of the following: polyethylene naphthalate (PEI), polyethylene naphthalate two formal acid glycol ester (PEN), polyetheretherketone (PEEK), carbon fiber, graphene, silica gel, etc. In some embodiments, the metal material of the filler material may include aluminum alloy, magnesium-lithium alloy, copper, stainless steel, etc.

[0099] 7A and 8, FIG. 8 is a schematic diagram of a groove structure according to some embodiments of the present disclosure. In some embodiments, the structural and dimensional parameters of the groove structure 121 significantly affect the stiffness of the reinforcing member 120, and the stiffness and mass of the reinforcing member 120 can be adjusted by adjusting the structural and dimensional parameters of the groove structure 121. As shown in FIG. 8, the groove structure 121 has a height h along the vibration direction and a width w perpendicular to the vibration direction. The sidewalls of the groove structure 121 have a thickness b. A skirt structure perpendicular to the vibration direction (e.g., extending along the surface of the elastic member) is provided at the opening of the groove structure 121, and the width of the skirt structure is bm. The stiffness of the reinforcing member 120 having the groove structure 121 is mainly provided by the groove structure 121. The groove structure 121 is hollow, and its stiffness is mainly a bending stiffness EI, where E is Young's modulus and I is the moment of inertia. For the groove structures 121 shown in FIGS. 7A and 8, the calculation formulas for the moment of inertia I of the corresponding reinforcing members 120 are as follows:

[0100] I=[wh^3-(w-2b){(h-2b)}^3 ] (Equation 1)

[0101] As can be seen from Equation 1, the moment of inertia I of the reinforcing member 120 having the groove structure 121 is determined only by the height h, width w, and thickness b of the reinforcing member 120, where h and b are both cubed parameters, and their impact on the rigidity of the reinforcing member 120 having the groove structure 121 is particularly significant.

[0102] By designing the parameter h to increase, the moment of inertia I increases, and the stiffness of the reinforcing member 120 having the groove structure 121 is further improved, so that the second resonance peak 230 of the speaker can move backward; conversely, by designing the parameter h to decrease, the stiffness of the reinforcing member 120 decreases, and the second resonance peak 230 of the vibration assembly 100 moves forward. Similarly, by designing the parameter b to increase, the moment of inertia I increases, and the stiffness of the reinforcing member 120 having the groove structure 121 is further improved, so that the second resonance peak 230 of the vibration assembly 100 can move backward; conversely, by designing the parameter b to decrease, the stiffness of the reinforcing member 120 decreases, and the second resonance peak 230 of the vibration assembly 100 moves forward.

[0103] In some embodiments, the parameters h and b are simultaneously optimized, and the h value is optimized and increased while the b value is optimized and decreased, so that the stiffness of the reinforcing member 120 having the groove structure 121 does not change, the mass is reduced, the frequency value of the second resonant peak 230 of the vibration assembly 100 does not change, and the output frequency response of the vibration assembly 100 can be improved; conversely, the h value is optimized and decreased while the b value is optimized and increased, so that the stiffness of the reinforcing member 120 having the groove structure 121 does not change, the mass is increased, the frequency value of the second resonant peak 230 of the vibration assembly 100 does not change, and the output frequency response of the vibration assembly 100 can be reduced.

[0104] In some embodiments, by simultaneously optimizing the design of the parameters h and b, optimizing and increasing the h value and optimizing and decreasing the b value, the stiffness of the reinforcing member 120 having the groove structure 121 can be reduced, the mass can be reduced, the second resonance peak 230 of the vibration assembly 100 can be moved forward, and the output frequency response of the vibration assembly 100 can be improved.

[0105] In some embodiments, by simultaneously optimizing the design of the parameters h and b, and optimizing and increasing the h value and optimizing and decreasing the b value, the stiffness of the reinforcing member 120 having the groove structure 121 can be reduced, the mass can be increased, the second resonance peak 230 of the vibration assembly 100 can be moved forward, and the output frequency response of the speaker can be reduced.

[0106] The physical quantity λ is defined as the ratio of the height h to the thickness b of the reinforcing member 120 having the groove structure 121, that is, as follows:

[0107] λ=h / b (Equation 2)

[0108] As shown in FIG. 9, FIG. 9 is another frequency response curve diagram of a vibration assembly according to some embodiments of the present disclosure. As can be seen from FIG. 9, in some embodiments, when comparing the curve λ=5 with the curve λ=15, or the curves λ=7.14, λ=9, and λ=12, increasing the ratio λ can achieve the effect of increasing the output power without changing the frequency value of the second resonance peak 230 of the vibration assembly 100. For example, the parameters h and b can be simultaneously optimized by optimizing and increasing the h value and optimizing and decreasing the b value, thereby maintaining the stiffness of the reinforcing member 120 having the groove structure 121 and reducing its mass. In some embodiments, as can be seen from FIG. 9, the output power of the vibration assembly 100 gradually increases with increasing λ. Specifically, when λ is small, for example, when λ=5, the output sound pressure level is significantly lower than when λ=12, λ=9, λ=7.14, or λ=15. The frequency of the second resonance peak 230 is lower, resulting in a smaller, relatively flat bandwidth between the first resonance peak 210 and the second resonance peak 230. When λ=15, the frequency of the second resonance peak 230 is lower than when λ=12, λ=9, or λ=7.14, resulting in a smaller, relatively flat bandwidth between the first resonance peak 210 and the second resonance peak 230. However, the output sound pressure level is significantly improved, making this a suitable choice for some narrow frequency band application scenarios. Therefore, overall, λ should be set to a large value.

[0109] By designing the ratio λ, it is possible to effectively adjust the frequency value and output sensitivity of the second resonance peak 230 of the vibration assembly 100, and the second resonance peak 230 of the vibration assembly 100 is in the range of 6000 Hz to 8000 Hz, resulting in high sensitivity. In some embodiments, the ratio λ of the height h to the thickness b of the reinforcing member 120 having the groove structure 121 may be in the range of 7.14 or greater. In some embodiments, more preferably, the ratio λ of the height h to the thickness b of the reinforcing member 120 having the groove structure 121 may be in the range of 9 or greater.

[0110] 9, the height h and thickness b of the reinforcing member 120 are both cubic parameters, and their influence on the stiffness of the reinforcing member 120 including the groove structure 121 is particularly significant. Furthermore, as the ratio λ of the height h to the thickness b of the reinforcing member 120 including the groove structure 121 increases, the reinforcing member 120 can have a smaller mass and higher stiffness, thereby providing a greater output for the vibration assembly 100. However, as the height h and thickness b of the reinforcing member 120 including the groove structure 121 change, the difficulty of the process and the overall reliability of the reinforcing member 120 are affected.

[0111] 10, which is a frequency response curve diagram of a vibration assembly corresponding to a reinforcing member having different heights, according to some embodiments of the present disclosure. As can be seen from FIG. 10, the stiffness of the reinforcing member 120 having the groove structure 121 decreases as the height h decreases, and the second resonance peak 230 of the vibration assembly 100 moves forward, with a corresponding increase in sensitivity. Furthermore, the reinforcing member 120 having the groove structure 121 has excellent output power when the height h is either 170 μm or 270 μm.

[0112] While a high height h is beneficial to speaker performance, increasing the height h of the reinforcing member 120 having the groove structure 121 dramatically increases the difficulty of the processing of the reinforcing member 120 (e.g., chemical etching, cutter processing, laser cutting, electrochemical processing, or injection molding or hot press molding for non-metallic materials). As h increases, it becomes difficult to guarantee processing accuracy. Taking into account the actual processing process, in some embodiments, the height h of the reinforcing member 120 having the groove structure 121 may be in the range of 50 μm to 500 μm. In some embodiments, to further reduce the difficulty of actual processing, the height h of the reinforcing member 120 having the groove structure 121 may be in the range of 200 μm to 350 μm.

[0113] 11, which illustrates frequency response curves of vibration assemblies corresponding to reinforcing members with different thicknesses, according to some embodiments of the present disclosure. As can be seen from FIG. 11, the stiffness and mass of the reinforcing member 120 having the groove structure 121 decrease with a decrease in thickness b. This causes the second resonance peak 230 of the vibration assembly 100 to move forward, and the sensitivity of the vibration assembly 100 to improve. When the thickness b of the reinforcing member 120 is large, the stiffness and mass of the reinforcing member 120 increase, increasing the load imposed on the vibration assembly 100 by the reinforcing member 120. This causes the second resonance peak 230 to move backward, significantly reducing the output sensitivity of the vibration assembly 100. For example, when the thickness b is 100 μm, the output is significantly reduced compared to other thicknesses (e.g., 20 μm, 30 μm, 50 μm, etc.). As the thickness b gradually decreases, the second resonance peak 230 gradually moves forward, but the output sensitivity is significantly improved, making the vibration assembly 100 suitable for some narrow frequency band application scenarios. Overall, the thickness b should be small.

[0114] Designing the thickness b to be small is advantageous for speaker performance, but as the thickness b of the reinforcing member 120 having the groove structure 121 decreases, the reliability of the reinforcing member 120 having the groove structure 121 is significantly affected. Taking into account the reliability of the actual product, in some embodiments, the thickness b of the reinforcing member 120 having the groove structure 121 may be in the range of 50 μm or less. In some embodiments, in order to ensure that the reinforcing member 120 having the groove structure 121 has high reliability and a small mass, the thickness b of the reinforcing member 120 having the groove structure 121 may be in the range of 40 μm or less.

[0115] As shown in Figures 7G, ​​8, and 12, Figure 12 is a schematic diagram of a skirt structure according to some embodiments of the present specification. In Figure 12, the shaded area represents the skirt structure. From a process perspective, the larger the design value of the width bm of the skirt structure, the larger the connection area between the reinforcing member 120 having the groove structure 121 and the central region 112 of the elastic element 110, thereby achieving higher adhesive strength and improving the reliability of the vibration assembly 100. The design of the width bm of the skirt structure directly determines the area of ​​the suspension region 1121 of the elastic element 110, and the equivalent mass Mm i , equivalent stiffness Ka i , Ka' i , equivalent damping Ra i , Ra' i are determined, which further affect the location of the third resonant peak 240 of the vibrating assembly 100 and the frequency response output of the vibrating assembly 100.

[0116] FIG. 13 shows frequency response curves of vibration assemblies corresponding to reinforcement members with different skirt structure widths, according to some embodiments of the present disclosure. As can be seen from FIG. 13, as the skirt structure width bm increases, the output of the vibration assembly 100 decreases significantly, and the output of the third resonance peak 240 decreases. When designing the skirt structure width bm, considering performance, a smaller bm is preferable. As shown in FIG. 13, when the skirt structure width bm is 500 μm, the output SPL decreases significantly compared to when the skirt structure width bm is other values ​​(e.g., 100 μm, 150 μm, 300 μm, etc.). As the skirt structure width bm decreases, the process difficulty increases. Based on the balance between performance and process, in some embodiments, the skirt structure width bm of the reinforcement member 120 having the groove structure 121 may be in the range of 100 μm to 300 μm. In some embodiments, in order to reduce the process difficulty and provide the vibration assembly 100 with excellent output performance, the width bm of the skirt structure of the reinforcing member 120 having the groove structure 121 may be in the range of 100 μm to 200 μm.

[0117] In some embodiments, when the elastic member or reinforcing member 120 in the central region 112 is connected to a speaker driver, the stress and amplitude experienced by the elastic member are greatest at the connection point, and the stress and amplitude experienced by the elastic member decrease with distance from the connection point along the extension direction (hereinafter referred to as the extension direction). To accommodate the different amplitudes or stresses experienced by the elastic member at different points in the central region 112, the stiffness of the reinforcing member 120 at different points in the extension direction may vary. In some embodiments, the dimensions of the elongated structure 124 and the groove structure 121 of the annular structure 122 at different points in the extension direction of the reinforcing member 120 may vary, and / or the distance between adjacent groove structures 121 may vary. In some embodiments, when the central connection portion 123 is connected to a speaker driver, the stiffness of the groove structure 121 gradually decreases in the extension direction from a portion adjacent to the central connection portion 123 to a portion adjacent to the edge region 114. For example, in the extension direction, the parameter h of the groove structure 121 gradually decreases from a portion close to the central connection portion 123 to a portion close to the edge region 114. For example, in the extension direction, the parameter b of the groove structure 121 gradually decreases from a portion close to the central connection portion 123 to a portion close to the edge region 114. Also, for example, in the extension direction, the parameter bm of the groove structure 121 gradually decreases from a portion close to the central connection portion 123 to a portion close to the edge region 114. In some embodiments, in the extension direction, the distance between adjacent groove structures 121 gradually increases from the distance between the groove structure 121 close to the central connection portion 123 and the adjacent groove structure 121 slightly away from the central connection portion 123 (the adjacent annular structure 122) to the distance between the groove structure 121 close to the edge region 114 and the adjacent groove structure 121 slightly away from the edge region 114 (the adjacent annular structure 122). The distance between adjacent groove structures 121 here is the distance between the centers (centroids) of adjacent groove structures 121 (adjacent annular structures 122).

[0118] According to some embodiments herein, there is provided a manufacturing process for a reinforcing member 120 having a groove structure 121. In some embodiments, the reinforcing member 120 having a groove structure 121 may be made of a non-metallic material or a metallic material.

[0119] In some embodiments, the Young's modulus of the material of the reinforcing member 120 (also referred to as the reinforcing region) is higher than the Young's modulus of the material of the elastic member (also referred to as the elastic region) to improve the stiffness of the reinforcing member 120 and the elasticity of the elastic member, thereby increasing its amplitude and thereby improving the output of the vibrating assembly 100. In some embodiments, the material of the reinforcing member 120 is different from the material of the elastic member. For example, the reinforcing member 120 is a metallic material with high stiffness, and the elastic member is a non-metallic material with low stiffness. In some embodiments, the material of the reinforcing member 120 is the same as the material of the elastic member. For example, the reinforcing member 120 and the elastic member are both non-metallic materials. In this case, the reinforcing member 120 can be considered a structure that improves the stiffness of the elastic element 110 through structural design.

[0120] In some embodiments, the material of the reinforcing member 120 having the groove structure 121 may be a composite of one or more of the following materials: PEEK (polyether ether ketone), PI (polyimide), PEN (polyethylene naphthalate), PU (polyurethane), TPE (thermoplastic elastomer), PEI (polyetherimide), silica gel, carbon fiber, PT (polypropylene), cashmere fiber, etc. The material of the elastic element 110 may include, but is not limited to, one or more of PEEK, PI, PEN, PU, ​​PEI, and silica gel. Compared with metallic materials, non-metallic materials are less difficult to process, and processing uniformity can be more easily ensured.

[0121] In some embodiments, the vibration assembly is manufactured by the following steps: manufacturing a groove structure and an openwork structure in the reinforcement member; and connecting the reinforcement member and the elastic element to manufacture the vibration assembly. In some embodiments, the groove structure is manufactured by a first process. In some embodiments, the first process may include one or more of injection molding, hot press molding, etching, cutting, laser cutting, and electrochemical machining. In some embodiments, the openwork structure may be manufactured by a second process. In some embodiments, the second process may include laser cutting. In some embodiments, the groove structure and the openwork structure may be manufactured by an integral molding process. In some embodiments, after manufacturing the reinforcement member, an adhesive may be applied to the reinforcement member or the elastic element (e.g., by spraying an adhesive), and then the reinforcement member and the elastic element may be connected by hot press molding to manufacture the vibration assembly.

[0122] 14A and 14B, Fig. 14A is a schematic diagram illustrating a manufacturing process of a non-metallic reinforcement member and a vibration assembly according to some embodiments of the present disclosure, and Fig. 14B is a schematic diagram of a model corresponding to Fig. 14A. In some embodiments, when the material of the reinforcement member 120 (also referred to as the reinforcement region) is the same as the material of the elastic member (also referred to as the elastic region), the reinforcement member 120 can be made of a non-metallic material. For the reinforcement member 120 having the groove structure 121 made of a non-metallic material, the manufacturing process may include the following steps 1410 to 1430.

[0123] In step 1410, molding is performed using a hot press mold.

[0124] In some embodiments, the reinforcing member 120 may be manufactured by molding using a hot press mold. For example, after processing the mold, a liquid sample or a solid sample is poured into the mold, and the mold is fixed to a heating plate using solid contact pressure or gas pressure. The melting temperature and time of the sample are controlled, and the sample is melted, hardened, cooled, and then removed from the mold to obtain the initial reinforcing member 120. In some embodiments, the reinforcing member 120 may be manufactured using other processes capable of processing non-metallic materials, which are not described herein. In some embodiments, the groove structure 121 may be directly formed (i.e., grooves are formed in the reinforcing member 120) by placing a corresponding mold during the hot press molding process using a mold. In some embodiments, the groove structure 121 may be formed by laser engraving a predetermined area of ​​the reinforcing member 120 to remove material and form the groove. In some embodiments, the reinforcing member 120 may have the groove structure 121. In some embodiments, the groove structure 121 may be formed in the reinforcing member 120 using other processes, such as corrosion, which are not described herein.

[0125] In step 1420, laser engraving is performed.

[0126] In some embodiments, laser engraving can be used to remove material from areas of the reinforcing member 120 to form the openwork structure. In some embodiments, other processes, such as corrosion, can be used to form the openwork structure in the reinforcing member 120, and are not discussed herein.

[0127] Step 1430 involves connecting and molding.

[0128] In some embodiments, the reinforcing member 120 having the groove structure 121 and the elastic element 110 can be connected and finally molded. In some embodiments, an adhesive can be sprayed on the surface of the elastic element 110 or the reinforcing member 120, and then the elastic element 110 and the reinforcing member 120 can be connected by hot pressing. In some embodiments, the elastic element 110 and the reinforcing member 120 can be directly connected by hot pressing without applying an adhesive between them. In some embodiments, the reinforcing member 120 can be connected and fixed to the elastic element 110 by other methods, which will not be described herein.

[0129] In some embodiments, the material of the stiffening member 120 may include, but is not limited to, aluminum alloys, copper and its alloys, stainless steel, gold and its alloys, tungsten, etc. Compared to non-metallic materials, a stiffening member 120 made of a metallic material has higher stiffness for the same mass, which can improve the output of the vibrating assembly 100.

[0130] 15A and 15B, Fig. 15A is a schematic diagram illustrating a manufacturing process of a metallic reinforcement member and a vibration assembly according to some embodiments of the present specification, and Fig. 15B is a schematic diagram of a model corresponding to Fig. 15A. In some embodiments, when the material of the reinforcement member 120 (also referred to as the reinforcement region) is different from the material of the elastic member (also referred to as the elastic region), the reinforcement member 120 can be made of a metallic material. For a reinforcement member 120 having a groove structure 121 made of a metallic material, the manufacturing process generally includes the following steps 1510 to 1530.

[0131] In step 1510, processing and molding is performed.

[0132] In some embodiments, machining may include one or more processes capable of processing metallic materials, such as chemical etching, cutting, laser cutting, electrochemical machining, and the like.

[0133] In step 1520, laser engraving is performed.

[0134] In some embodiments, step 1520 may be the same as step 1420 and will not be described here.

[0135] In some embodiments, step 1520 can be performed simultaneously with step 1510 , ie, the groove structure 121 of the reinforcing member 120 can be integrally molded directly with the reinforcing member 120 .

[0136] Step 1530 involves connecting and molding.

[0137] In some embodiments, step 1530 may be the same as step 1430 and will not be described here.

[0138] In some embodiments, the relationship between the area of ​​the suspension region 1121 and the edge region 114 and the thickness of the elastic element 110 affects the local equivalent mass Mm3, the local equivalent mass Mm2, the local area stiffness Ka'2 and the local area stiffness Ka'1, and therefore controls the range of the second resonant peak 230 of the vibrating assembly 100.

[0139] 16, which is a schematic diagram of a vibration assembly having a reinforcing member with a single ring structure, according to some embodiments of the present disclosure. In some embodiments, the reinforcing member 120 includes a central connection portion 123 and an elongated structure 124, the elongated structure 124 extends from the central connection portion 123 to the periphery of the reinforcing member 120, and the groove structure 121 is disposed on the cross section of the elongated structure 124. The horizontal projection area of ​​the suspension region 1121 is defined as S v and the horizontal plane projected area of ​​the edge region 114 is defined as S e is defined as the horizontal plane projection area S of the suspension area 1121. v and the horizontal plane projected area S of the edge region 114 e The sum of s The physical quantity α (unit: mm) is defined as S s and the thickness of the elastic element 110 (also called the vibration film thickness) H i It is defined as the ratio of

[0140] α=Ss / H i (Formula 3)

[0141] In some embodiments, to place the second resonant peak 230 in the range of 5000 Hz to 10000 Hz, S s and the thickness of the diaphragm H i The ratio α to α may be in the range of 5000 mm to 12000 mm. In some embodiments, α may be in the range of 6000 mm to 10000 mm to achieve second resonance peak 230 in the range of 6000 Hz to 9000 Hz. In some embodiments, α may be in the range of 6000 mm to 9000 mm to achieve second resonance peak 230 in the range of 6000 Hz to 8500 Hz. In some embodiments, α may be in the range of 6000 mm to 8000 mm to achieve second resonance peak 230 in the range of 6000 Hz to 8000 Hz. In some embodiments, α may be in the range of 6000 mm to 7000 mm to achieve second resonance peak 230 in the range of 6000 Hz to 7500 Hz. In some embodiments, α may be in the range of 7000 mm to 9000 mm to achieve second resonant peak 230 in the range of 7000 Hz to 8500 Hz. In some embodiments, α may be in the range of 7000 mm to 8000 mm to achieve second resonant peak 230 in the range of 7000 Hz to 8000 Hz.

[0142] In some embodiments, by designing the arch height of the edge of the edge region 114, the three-dimensional dimensions of the edge region 114 of the elastic element 110 can be changed to change the stiffness Ka'1 of the edge region 114 while leaving the horizontal projection area of ​​the edge region 114 of the vibration assembly 100 and the horizontal projection area of ​​the suspension region 1121 unchanged, and further the second resonance peak of the vibration assembly 100 can be controlled.

[0143] As shown in Fig. 17, Fig. 17 is a partial schematic diagram of a vibration assembly according to some embodiments of the present specification. In this specification, the arch height of the edge of the edge region 114 is defined as Δh, and the physical quantity δ (unit: mm) is defined as S sand the arch height Δh of the edge of the diaphragm.

[0144] δ=S s / Δh (Equation 4)

[0145] In some embodiments, δ may be in the range of 50 mm to 600 mm. In some embodiments, δ may be in the range of 100 mm to 500 mm so that edge region 114 has appropriate three-dimensional dimensions. Preferably, δ may be in the range of 200 mm to 400 mm. More preferably, δ may be in the range of 250 mm to 400 mm. In some embodiments, δ may be in the range of 250 mm to 350 mm so that edge region 114 has appropriate rigidity. Preferably, δ may be in the range of 250 mm to 300 mm. More preferably, δ may be in the range of 200 mm to 300 mm.

[0146] In some embodiments, by setting the horizontal projection area of ​​the maximum contour of the reinforcing member 120 (i.e., the dimensions of the outermost annular structure 122), the dimensions (or area) of the suspension region 1121 between the edge region 114 and the reinforcing member 120 are adjusted to change the equivalent mass Mt1 and equivalent stiffness Kt1, and further control the range of the second resonant peak 230 of the vibration assembly 100.

[0147] In this specification, the horizontal projection area of ​​the central region 112 is defined as S c and the horizontal projection area of ​​the maximum contour of the reinforcing member 120 is defined as S rm and the horizontal projection area of ​​the suspension area 1121 is defined as S v and S rm =S c -S v .

[0148] In this specification, physical quantities,

[0149]

number

[0150] (unit: 1) is the horizontal projection area S of the suspension area 1121 v and the horizontal projection area S of the central region 112 c It is defined as the ratio of

[0151]

number

[0152] =S v / S c (Formula 5)

[0153] In some embodiments,

[0154]

number

[0155] In some embodiments, in order to ensure that the suspension region 1121 has an appropriate area,

[0156]

number

[0157] is in the range of 0.1 to 0.5.

[0158]

number

[0159] is in the range of 0.15 to 0.35. More preferably,

[0160]

number

[0161] is in the range of 0.15 to 0.5. In some embodiments, in order to ensure that the equivalent mass Mt1 and the equivalent stiffness Kt1 have appropriate values,

[0162]

number

[0163] is in the range of 0.2 to 0.5.

[0164]

number

[0165] is in the range of 0.15 to 0.25. More preferably,

[0166]

number

[0167] is in the range of 0.15 to 0.2.

[0168] In some embodiments, the elongated structures 124 can have different widths, shapes, and numbers to adjust the frequency of the speaker's frequency response by changing the openwork area (the suspension area corresponding to the central area 112) of the reinforcing member 120. For specific details, see Figures 20 to 25E and their associated descriptions below.

[0169] In some embodiments, by designing the area of ​​the openwork region (e.g., by designing the number and position of the elongated structures 124 of the reinforcing member 120, the number and position of the annular structures 122, etc.), the resonant frequency of the vibrating assembly 100 can be adjusted to improve the usability of the vibrating assembly 100.

[0170] As shown in Figures 5A and 18, Figure 18 is a diagram of deformation around the frequency of the third resonance peak of the CC cross section of the vibration assembly according to some embodiments of the present disclosure. As can be seen from Figure 5A, the frequency difference between the third resonance peak 240 and the second resonance peak 230 has a significant effect on the flatness of the frequency response curve of the vibration assembly 100 in the high frequency band. In some embodiments, as can be seen from the vibration situation at the CC cross section of the vibration assembly 100 as shown in Figure 18, around the frequency of the third resonance peak, the main deformation location of the vibration assembly 100 is the portion of deformation occurring in the openwork region of the central region 112. In some embodiments, a mass-spring-damping system is formed, and an equivalent mass Mm i , equivalent stiffness Ka i The third resonance peak 240 of the vibrating assembly 100 can be controlled by controlling each openwork area corresponding to the central region 112 of the reinforcing member 120 to correspond to S. For example, the number and dimensions of the elongated structures 124 and the annular structure 122 can be designed to design the area of ​​each openwork area of ​​the central region 112, and the area of ​​each openwork area can be set to S. i 18 shows a deformation diagram of the vibration assembly 100 having a single annular reinforcing member 120 at the third resonance peak, the conclusion still applies to vibration assemblies having multiple annular reinforcing members 120.

[0171] In order to set the third resonance peak in an appropriate frequency range (12000 Hz to 18000 Hz), in this specification, the physical quantity is defined as the area S of one of the openwork regions. i and the thickness H of the diaphragm in each openwork area i The area-to-thickness ratio μ (unit: mm) is defined as the ratio of

[0172] μ=S i / H i (Formula 6)

[0173] By designing μ, the frequency position of the third resonance peak of the vibrating assembly can be adjusted.

[0174] In some embodiments, the area-to-thickness ratio μ is in the range of 100 to 1000. In some embodiments, each openwork region has a corresponding suitable equivalent mass Mm i and equivalent stiffness Ka i In some embodiments, the area-to-thickness ratio μ is in the range of 150 to 700 so that each openwork region has a corresponding appropriate equivalent mass Mm i and equivalent stiffness Ka i In some embodiments, the area-to-thickness ratio μ is in the range of 150 to 950 so that each openwork region has a corresponding appropriate equivalent mass Mm i and equivalent stiffness Ka i In some embodiments, the area-to-thickness ratio μ is in the range of 150 to 900. In some embodiments, the area-to-thickness ratio μ is in the range of 150 to 800. In some embodiments, each openwork region has a corresponding appropriate equivalent mass Mm i and equivalent stiffness Ka i In order to have this, the area-to-thickness ratio μ is in the range of 100 to 700. Preferably, the area-to-thickness ratio μ is in the range of 300 to 500. More preferably, the area-to-thickness ratio μ is in the range of 400 to 600.

[0175] It should be noted that although the structure shown in FIG. 18 is a single ring structure, the above range of area-thickness ratio μ still applies to multiple ring structures.

[0176] As shown in FIG. 19, in some embodiments, the reinforcing member 120 has a double annular structure, and the area of ​​each openwork region of the elastic element 110 inside the first annular structure is defined as S 1i and the area of ​​each openwork region of the elastic element 110 between the first annular structure and the second annular structure is defined as S 2i In some other embodiments, the reinforcing member 120 may have more annular structures 122, and the area of ​​each openwork region of the elastic element 110 between the (n-1)th annular structure and the nth annular structure is defined as S ni In this specification, the physical quantity of the openwork area ratio γ (unit: 1) of the elastic element 110 is defined as the ratio of the area S of any two openwork areaski and S ji It is defined as the ratio of

[0177] γ=S ki / S ji (Formula 7)

[0178] where k>j. By designing γ, the frequency position of the third resonance peak of the vibrating assembly can be adjusted.

[0179] As shown in Figures 19 and 20, Figure 20 is a frequency response curve of the vibration assembly corresponding to Figure 19. In Structures 1 to 4, the area S of each openwork area between the first annular area and the second annular area is 2i and the area S of each openwork area inside the first annular area 1i The area ratios γ of the central region 112 and the openwork region 122 are 5.9, 4.7, 3.9, and 3.2, respectively. As can be seen from FIG. 19 , at the third resonance peak of the vibration assembly 100, in Structures 1 to 4, as γ decreases, the radius ΔR1 of the first openwork region located within the inner annular structure 122 gradually increases, and the radius ΔR2 of the second openwork region located between the inner annular structure 122 and the outer annular structure 122 gradually decreases. In some embodiments, as further shown in FIG. 20 , the frequency response curves of the vibration assemblies of Structures 1 to 4 show that the sound pressure amplitude output at the third resonance peak gradually increases. Therefore, the area ratio of each openwork region in the central region 112 affects the resonant frequency of each openwork region, ultimately resulting in a sound pressure superposition effect in the high-frequency band. That is, by adjusting γ, the high-frequency sensitivity of the vibration assembly 100 can be adjusted.

[0180] In some embodiments, as can be seen from Figure 20, as γ gradually decreases, the third resonance peak appears more prominently and the output sound pressure level of the corresponding frequency band increases. When γ is 5.9 (corresponding to Structure 1), the third resonance peak does not form and the output sound pressure level of the frequency band decreases significantly, resulting in a significant improvement in the output of the frequency band of the third resonance peak compared to when γ is 4.7 or less (e.g., γ = 4.7 corresponding to Structure 2, γ = 3.9 corresponding to Structure 3, and γ = 3.2 corresponding to Structure 4). In some embodiments, the area S of any two openwork regions ki and S ji In some embodiments, to further improve the high frequency sensitivity of the vibrating assembly 100, the ratio γ of the areas S of any two openwork regions is ki and S ji In some embodiments, to further improve the high frequency sensitivity of the vibrating assembly 100, the ratio γ of the areas S of any two openwork regions is ki and S ji In some embodiments, the ratio γ of the areas S of any two openwork regions is in the range of 3.5 or less. ki and S ji In some embodiments, to further improve the high frequency sensitivity of the vibrating assembly 100, the ratio γ of the areas S of any two openwork regions is ki and S ji The ratio γ is in the range of 3 or less.

[0181] In some embodiments, by designing the projected area of ​​the reinforcing member 120 along the vibration direction and the projected area of ​​the maximum contour of the reinforcing member 120 onto the central region 112 along the vibration direction, it is possible to adjust the mass, center of mass, stiffness of the reinforcing member 120, and the mass and stiffness of the suspension region of the central region 112, thereby enabling adjustment of the first resonant peak, second resonant peak, and third resonant peak of the vibration assembly 100.

[0182] In order to facilitate the design of the reinforcing member 120, in this specification, as shown in FIG. 19, the lateral area ratio β (unit: 1) of the groove structure of the reinforcing member 120 to the reinforcing member 120 is defined as the ratio of the projected area S of the groove structure in the vibration direction of the reinforcing member 120 to the projected area S of the reinforcing member 120. r and the projected area S of the maximum contour of the reinforcing member 120 onto the central region 112 t It is defined as the ratio of

[0183] β=S r / S t (Formula 8)

[0184] In some embodiments, the projection of the reinforcing member 120 along the vibration direction is the projection of the groove structure of the reinforcing member 120. The projection of the maximum contour of the reinforcing member 120 coincides with the projection of the central region 112.

[0185] As shown in Fig. 21, Fig. 21 is another frequency response curve diagram of a vibration assembly according to some embodiments of the present disclosure. As can be seen from Fig. 21, the projected area S r and the projected area S of the maximum contour of the reinforcing member 120 t With the change of the ratio β, the output of the third resonance peak of the speaker also changes obviously. When the ratio β is small, the equivalent stiffness Ka' i decreases, and the equivalent mass Mm i increases, the third resonance peak moves forward, and when the ratio β is large, the equivalent stiffness Ka' i The equivalent mass Mm i is reduced and the third resonance peak moves backward.

[0186] By designing β, the equivalent stiffness Ka' i and equivalent mass Mm i can be adjusted to place the high-frequency third resonance peak of the vibrating assembly in an appropriate frequency range, and to place the resonance frequency difference between each openwork structure in an appropriate range (e.g., 4000 Hz or less). In some embodiments, the lateral area ratio β of the groove structure of the reinforcing member 120 to the reinforcing member 120 is 0.15 to 0.8. Preferably, the lateral area ratio β of the groove structure of the reinforcing member 120 to the reinforcing member 120 is 0.35 to 0.65.

[0187] 22A and 22B, which are schematic diagrams of vibration assemblies having different numbers of elongated structures, according to some embodiments of the present disclosure. In some embodiments, adjusting the number of elongated structures 124 can adjust the overall mass of the vibration assembly 100, thereby changing the total equivalent mass Mt formed by combining the mass of the stiffening member 120, the mass of the elastic element 110, the equivalent air mass, and the equivalent driving end mass, thereby changing the resonant frequency of the formed mass Mt-spring Kt-damping Rt system, which in turn changes the primary resonant frequency of the vibration assembly 100, changing the sensitivity of the vibration assembly 100 in the low frequency band before the first resonant frequency and the mid frequency band after the first resonant frequency. In some embodiments, the number of elongated structures 124 can be designed to increase the total equivalent mass Mt, thereby shifting the first resonant frequency of the vibrating assembly 100 forward and improving sensitivity to low frequency bands before the first resonant frequency of the vibrating assembly 100, e.g., frequency bands before 3000 Hz, 2000 Hz, 1000 Hz, 500 Hz, and 300 Hz. In some embodiments, the number of elongated structures 124 can be designed to decrease the total equivalent mass Mt, thereby shifting the first resonant frequency of the vibrating assembly 100 backward and improving sensitivity to mid frequency bands after the first resonant frequency of the vibrating assembly 100, e.g., frequency bands after 3000 Hz. Also, sensitivity may be improved, for example, in frequency bands after 2000 Hz. Also, sensitivity may be improved, for example, in frequency bands after 1000 Hz. Also, sensitivity may be improved, for example, in frequency bands after 500 Hz. Also, for example, the sensitivity of the frequency band after 300 Hz may be increased.

[0188] In some embodiments, the stiffness of the reinforcing member 120 can be further adjusted by adjusting the number of elongated structures 124, thereby changing the stiffness Kt1 provided to the system by the reinforcing member 120 and the elastic element 110; the reinforcing member 120, the connection region 115, the edge region 114, the suspension region between the region of the central region 112 surrounded by the reinforcing member 120 and the edge region 114, the equivalent air mass, and the drive end equivalent mass are combined to form a total equivalent mass Mt1, and the equivalent damping of each part forms a total equivalent damping Rt1; the formed mass Mt1-spring Kt1-damping Rt1 system has an equivalent fixed support at a certain annular region in the diameter direction of the reinforcing member 120, and by changing the resonant frequency of the reversal motion by the ring, the second resonance position of the vibration assembly 100 is changed.

[0189] In some embodiments, by adjusting the number of elongated structures 124, and further adjusting the area of ​​one or more suspension regions corresponding to the central region 112 of the reinforcing member 120, the equivalent mass Mm of each openwork region can be increased. i , equivalent stiffness Ka i , Ka' i , equivalent damping Ra i , Ra' i can be varied, thereby varying the location of the third resonant peak of the vibrating assembly. In some embodiments, adjusting the number of elongated structures 124 can further adjust the area-to-thickness ratio μ of the vibrating assembly and the lateral area ratio β of the groove structure of the stiffening member 120 to the stiffening member 120 to adjust the location of the third resonant peak of the vibrating assembly.

[0190] In some embodiments, the number of elongated structures 124 of the reinforcing member 120 is adjustable, and the positions of the first resonant peak, the second resonant peak, and the third resonant peak of the vibration assembly 100 can be adjusted according to actual application needs, thereby realizing controllable adjustment of the frequency response of the vibration assembly 100.

[0191] In some embodiments, the shape of the projection of the elongated structure 124 along the vibration direction of the elastic element 110 includes at least one of a rectangle, a trapezoid, a curved shape, an hourglass shape, and a petal shape. Therefore, by adjusting the shape of the elongated structure 124, the area of ​​the openwork area of ​​the reinforcing element 120 (corresponding to the suspension area of ​​the central region 112 within the projection range of the reinforcing element 120) can be changed to adjust the relationship between the area of ​​the openwork area and the thickness of the elastic element 110 (area-thickness ratio μ), thereby achieving the purpose of adjusting the third resonance peak. By changing the relationship between the areas of the openwork areas between different annular structures 122 of the reinforcing member 120 (openwork area area ratio γ), the purpose of adjusting the third resonance peak can be achieved; and further, by changing the relationship between the groove structure of the reinforcing member 120 and the lateral area of ​​the reinforcing member 120 (lateral area ratio β between the groove structure of the reinforcing member 120 and the reinforcing member 120), the purpose of adjusting the first resonance peak, the second resonance peak, and the third resonance peak can be achieved.

[0192] 23A-23D, which are schematic diagrams of vibrating assemblies having elongated structures with different widths, according to some embodiments herein, the elongated structure 124 in FIG. 23A is an inverted trapezoid (i.e., the shorter side of the trapezoid is close to the center of the stiffening member 120), the elongated structure 124 in FIG. 23B is a trapezoid (i.e., the shorter side of the trapezoid is away from the center of the stiffening member 120), the elongated structure 124 in FIG. 23C is an outwardly arcing elongated structure, and the elongated structure 124 in FIG. 23D is an inwardly arcing elongated structure. In some embodiments, designing the elongated structures 124 with different lateral widths can effectively adjust the location of the center of mass of the stiffening member 120. In some embodiments, changing the stiffness of the reinforcing member 120 itself without changing the mass of the reinforcing member 120 changes the stiffness Kt1 provided to the system by the reinforcing member 120, the elastic element 110 (particularly the area covered by the reinforcing member 120 in the central region 112), and further changes the resonant frequency of the reversal motion of the mass Mt1-spring Kt1-damping Rt1 system, thereby changing the second resonant frequency of the vibrating assembly 100.

[0193] In some embodiments, by changing the design of the width of the elongated structure 124, the local stiffness can be varied at different locations extending from the center to the periphery of the elongated structure 124. When the driving end frequency is close to the resonance frequency of the mass Mt1-spring Kt1-damping Rt1 system, the connection region 115 between the fixed region 116 and the edge region 114, the edge region 114, and the suspension region between the region of the central region 112 covered by the reinforcing member 120 and the edge region 114 are driven to vibrate by the reinforcing member 120, resulting in a resonant peak adjustable with a 3 dB bandwidth.

[0194] 23A-23D , in some embodiments, by designing the elongated structure 124 to have an inverted trapezoidal shape or an outer arc shape (an outwardly protruding arc is defined as an outer arc and an inwardly concave arc is defined as an inner arc, and the outer arc may be a circular arc, an ellipse, a high-order function arc, or any other outer arc), the second resonance peak of the vibrating assembly 100 can be obtained with a wide 3 dB bandwidth, which is applicable to scenarios requiring a low Q factor and a wide bandwidth. In some embodiments, by designing the elongated structure 124 to have a trapezoidal shape, a rectangular shape, or an inner arc shape (an outwardly protruding arc is defined as an outer arc and an inwardly concave arc is defined as an inner arc, and the inner arc may be a circular arc, an ellipse, a high-order function arc, or any other inner arc), the second resonance peak of the vibrating assembly 100 can be obtained with high sensitivity and a small 3 dB bandwidth, which is applicable to scenarios requiring a high Q factor and high local sensitivity.

[0195] By designing the elongated structures 124 with different lateral widths, it is possible to further adjust the area of ​​one or more suspension regions corresponding to the central region 112 of the stiffening member 120, thereby adjusting the area of ​​each equivalent mass Mm i , equivalent stiffness Ka i , Ka' i , equivalent damping Ra i , Ra' i Additionally, the third resonance peak position of the vibrating assembly 100 changes.

[0196] Therefore, by designing elongated structures 124 with different lateral widths, the frequency location of the second resonant peak of the vibrating assembly 100, the 3 dB bandwidth at the resonant peak, the sensitivity of the vibrating assembly 100 at the resonant peak, and the location of the third resonant peak of the vibrating assembly 100 can be achieved.

[0197] 24A and 24B, which are schematic diagrams of vibrating assemblies having different shapes of elongated structures according to some embodiments herein, the elongated structure 124 in FIG. 24A is a rotational shape, and the elongated structure 124 in FIG. 24B is an S-shape. In some embodiments, by designing the elongated structure 124 with different lateral shapes, the stiffness of the stiffening member 120 can be adjusted to change the stiffness Kt1 provided to the system by the stiffening member 120 and the elastic element 110 (particularly the area covered by the stiffening member 120 in the central region 112), which in turn changes the resonant frequency of the reversal motion of the mass Mt1-spring Kt1-damper Rt1 system, thereby changing the second resonance position of the vibrating assembly 100. In some embodiments, the area of ​​one or more suspension regions corresponding to the central region 112 of the stiffening member can be further adjusted to change the stiffness Kt1 of each equivalent mass Mt1. i , equivalent stiffness Ka i , Ka' i , equivalent damping Ra i , Ra' i , which changes the third resonance peak position of the vibrating assembly 100. In some embodiments, designing the elongated structures 124 with different lateral shapes can further adjust the stress distribution within the stiffening member 120 and control the processing deformation of the stiffening member 120.

[0198] 25A-25E are schematic diagrams of reinforcement members having elongated structures of different shapes, according to some embodiments herein. In some embodiments, to precisely adjust the influence of the elongated structures of different shapes on the resonant peaks (e.g., the first resonant peak, the second resonant peak, and the third resonant peak) of the vibrating assembly, an included spoke angle θ is defined for an elongated structure 124 whose width gradually decreases from the center to the edge, and setting θ can adjust the resonant peak of the vibrating assembly. In some embodiments, for an elongated structure 124 with straight sides (as shown in FIGS. 25A-25D), the included angle θ is the included angle between two sides of the spoke. In some embodiments, for an elongated structure 124 with arc-shaped sides (as shown in FIG. 25E), the included angle θ is the included angle between tangents to the two sides of the elongated structure 124. In some embodiments, to precisely adjust the contribution of differently shaped elongated structures to the resonant peaks (e.g., the first resonant peak, the second resonant peak, and the third resonant peak) of the vibrating assembly, the included spoke angle may be set to θ for a spoke structure with a gradually increasing width from the center to the edge, as shown in FIG. 25D. i and θ i In some embodiments, for an elongated structure 124 with straight sides, the included angle θ i is the included angle between the two sides of the spoke. In some embodiments, for elongated structures 124 whose sides are arcs, the included angle θ i is the included angle between the tangents to the two sides of the spoke.

[0199] In some embodiments, the included angle θ (or θ i), the stiffness Kt1 provided to the system by the stiffening member 120 and the elastic element 110 can be changed by changing the stiffness of the stiffening member 120 itself while keeping the mass of the stiffening member 120 unchanged or changed. This in turn changes the resonant frequency of the reversal motion of the mass Mt1-spring Kt1-damping Rt1 system, thereby changing the second resonance position of the vibrating assembly 100 and controlling the 3 dB bandwidth of the second resonance peak of the vibrating assembly 100. In some embodiments, the included angle θ (or θ i ) can effectively increase the 3 dB bandwidth of the third resonance peak of the vibrating assembly 100.

[0200] In response to the frequency response of some vibrating assemblies 100 requiring a low Q factor and a wide bandwidth, the included angle θ (or θ i ) can be designed to be large. In some embodiments, the included angle θ of the elongated structures 124 can be in the range of 0 to 150°. In some embodiments, the included angle θ of the elongated structures 124 can be in the range of 0 to 120°. In some embodiments, the included angle θ of the elongated structures 124 can be in the range of 0 to 90°. In some embodiments, the included angle θ of the elongated structures 124 can be in the range of 0 to 80°. In some embodiments, the included angle θ of the elongated structures 124 can be in the range of 0 to 60°. In some embodiments, the included angle θ of the elongated structures 124 can be in the range of 0 to 60°. i may range from 0 to 90 degrees. In some embodiments, the included angle θ of the elongated structure 124 i may range from 0 to 80°. In some embodiments, the included angle θ of the elongated structure 124 i may be in the range of 0 to 70°. In some embodiments, the included angle θ of the elongated structure 124 i may be in the range of 0 to 60°. In some embodiments, the included angle θ of the elongated structure 124 i may be in the range of 0 to 45°.

[0201] In response to the frequency response of some vibrating assemblies 100 requiring a high Q and narrow bandwidth, the included angle θ (or θ i ) can be designed to be small. In some embodiments, the included angle θ of the elongated structures 124 can be in the range of 0 to 90°. In some embodiments, the included angle θ of the elongated structures 124 can be in the range of 0 to 80°. In some embodiments, the included angle θ of the elongated structures 124 can be in the range of 0 to 70°. In some embodiments, the included angle θ of the elongated structures 124 can be in the range of 0 to 60°. In some embodiments, the included angle θ of the elongated structures 124 can be in the range of 0 to 45°. In some embodiments, the included angle θ of the elongated structures 124 can be in the range of 0 to 45°. i may be in the range of 0 to 60°. In some embodiments, the included angle θ of the elongated structure 124 i may range from 0 to 80°. In some embodiments, the included angle θ of the elongated structure 124 i may range from 0 to 90 degrees. In some embodiments, the included angle θ of the elongated structure 124 i may range from 0 to 120°. In some embodiments, the included angle θ of the elongated structure 124 i may be in the range of 0 to 150°.

[0202] In some embodiments, θ and θ i The relationship between is defined as follows:

[0203] θ=-θi (Equation 9)

[0204] To accommodate the frequency response of some speakers requiring a low Q factor and a wide bandwidth, the included angle θ of the elongated structure 124 can be designed to be large. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of −90° to 150°. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of −45° to 90°. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of 0° to 60°.

[0205] To accommodate the high-Q, narrow-bandwidth frequency response of some speakers, the included angle θ of the elongated structure 124 can be designed to be small. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of −150° to 90°. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of −90° to 45°. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of −60° to 0°.

[0206] In some embodiments, for an irregularly shaped elongated structure 124, the included angle of the elongated structure 124 cannot be designed. In this case, the area method can be used for design. By changing the stiffness of the stiffening member 120 itself while keeping the mass of the stiffening member 120 unchanged or changing it, the stiffness Kt1 provided to the system by the stiffening member 120 and the elastic element 110 can be changed. Furthermore, by changing the resonant frequency of the reversal motion of the mass Mt1-spring Kt1-damping Rt1 system, the second resonance position of the vibrating assembly 100 can be changed, and the 3 dB bandwidth of the second resonance peak of the vibrating assembly 100 can be controlled.

[0207] 26A and 26B, which are schematic diagrams of a reinforcing member having an irregular elongated structure according to some embodiments of the present disclosure. In some embodiments, to precisely design the irregular elongated structure to adjust the resonance peak of the vibrating assembly, as shown in FIG. 26A, a circle with a radius R is defined by the maximum outline of the reinforcing member 120, and half of the radius R of the circle defined by the maximum outline is defined as radius R / 2. The horizontal projection area of ​​the reinforcing member 120 within the radius R / 2 range is defined as S. in and the horizontal projection area (i.e., projection along the vibration direction of the vibrating assembly) of the reinforcing member 120 within the range between the circle of radius R / 2 and the circle of radius R is defined as S out and the physical quantity τ is defined as the horizontal projection area S of the reinforcing member 120. out and the horizontal projection area S of the reinforcing member 120 in It is defined as the ratio of

[0208] τ=S out / S in (Formula 10)

[0209] In some embodiments, the horizontal projected area S of the reinforcing member 120 out and the horizontal projection area S of the reinforcing member 120 in By adjusting the ratio τ to control the mass distribution of the reinforcing member 120, it is possible to control the bandwidth of the third resonance peak of the vibrating assembly 100. In the case of other types of regular reinforcing member 120 structures, such as elliptical, rectangular, square, or other polygonal structures as shown in FIG. 26B, a figure similar to the reinforcing member 120 is defined and enveloped by the maximum outline of the reinforcing member 120, and the central region of the figure is defined as the reference point, and the distance from the reference point to each point on the outline envelope is R (as shown in FIG. 26B, the distances from the reference point to the four sides of the rectangular outline envelope are R, respectively). i , R i+1 , R i+2 , R i+3 ), and all corresponding R / 2 (as shown in Figure 26B, the distance is R i / 2, R i+1 / 2, R i+2 / 2, R i+3 The horizontal projection area of ​​the reinforcing member 120 in the region formed by the points (points S1 / S2) is defined as S in The horizontal projection area of ​​the reinforcing member 120 within the range between the distance R / 2 and the distance R is S out In the case of the structure of another irregular reinforcing member 120, the maximum contour is enveloped by a regular shape of a structure that is more similar to the maximum contour, and S in , S out , and define the ratio τ.

[0210] To accommodate the frequency response of some vibrating assemblies 100 requiring a low Q factor and a wide bandwidth, the stiffening member 120 can be designed to have a large mass concentrated in a central region. In some embodiments, to increase the mass in the central region of the stiffening member 120, the horizontal projected area S out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 0.3 to 2. In some embodiments, to increase the mass of the central region of the reinforcing member 120,out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 0.5 to 1.5. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 0.5 to 1.2. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 0.5 to 1.3. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 0.5 to 1.4. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 0.3 to 1.2. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 0.3 to 1.6. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 0.5 to 2. In some embodiments, to increase the mass of the central region of the reinforcing member 120, out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 0.5 to 2.2. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 0.3 to 2.2. out and horizontal projection area S in The ratio τ to may be in the range of 0.3 to 2.

[0211] To accommodate the high Q, narrow bandwidth required for some vibrating assemblies 100, the stiffening member 120 can be designed with a large mass concentrated at the edge region. In some embodiments, the stiffening member 120 can be designed with a large horizontal projected area S out and horizontal projection area S in The ratio τ of the horizontal projected area S to the horizontal projected area S may range from 1 to 3. In some embodiments, to increase the mass of the edge region of the reinforcing member 120, out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 1.2 to 2.8. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 1.4 to 2.6. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 1.6 to 2.4. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 1.8 to 2.2. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 1.2 to 2. In some embodiments, to increase the mass of the edge region of the reinforcing member 120, out and horizontal projection area S in The ratio τ of the horizontal projected area S to the horizontal projected area S may be in the range of 1 to 2. In some embodiments, to increase the mass of the edge region of the reinforcing member 120, out and horizontal projection area S in The ratio τ of the horizontal projected area S to the horizontal projected area S may be in the range of 2 to 2.8. out and horizontal projection area S in The ratio τ to may be in the range of 2 to 2.5.

[0212] In some embodiments, the purpose of adjusting the third resonance peak can be achieved by adjusting the number of annular structures 122 (in the range of 1 to 10) and changing the area of ​​the openwork area of ​​the reinforcing member 120 (the suspension area corresponding to the central area 112 within the projection range of the reinforcing member 120) to adjust the relationship between the area of ​​the openwork area and the thickness of the elastic element 110 (area-thickness ratio μ); the purpose of adjusting the third resonance peak can be achieved by changing the relationship between the areas of the openwork areas of different annular structures 122 of the reinforcing member 120 (openwork area area ratio γ); and the purpose of adjusting the first resonance peak, the second resonance peak, and the third resonance peak can be achieved by changing the relationship between the groove structure of the reinforcing member 120 and the lateral area of ​​the reinforcing member 120 (lateral area ratio β between the groove structure of the reinforcing member 120 and the reinforcing member 120).

[0213] In some embodiments, annular structure 122 may include a first annular structure and a second annular structure having overlapping centers of gravity, wherein the radial dimension of the first annular structure is smaller than the radial dimension of the second annular structure. In some embodiments, elongated structure 124 may further include at least one first elongated structure and at least one second elongated structure, wherein the at least one first elongated structure is disposed inside and connected to the first annular structure, and the at least one second elongated structure is disposed between and connected to the first and second annular structures, respectively, to form a plurality of distinct openwork regions in reinforcing member 120.

[0214] 27A-27C are schematic diagrams of vibration assemblies having different numbers of annular structures according to some embodiments herein. The annular structure 122 in FIG. 27A is a single annular structure, the annular structure 122 in FIG. 27B is a double annular structure, and the annular structure 122 in FIG. 27C is a triple annular structure. By designing the number of annular structures 122, it is possible to adjust the mass and stiffness of the reinforcing member 120 and the area of ​​the openwork region in the central region 112. In some embodiments, the number of annular structures 122 may be in the range of 1 to 10. In some embodiments, the number of annular structures 122 may be in the range of 1 to 5. In some embodiments, the number of annular structures 122 may be in the range of 1 to 3.

[0215] In some embodiments, by adjusting the number of annular structures 122, the mass of the stiffening member 120 can be adjusted to change the total equivalent mass Mt formed by combining the mass of the stiffening member 120, the mass of the elastic element 110, the equivalent air mass, and the equivalent drive end mass, thereby changing the resonant frequency of the formed mass Mt-spring Kt-damping Rt system, which in turn changes the primary resonant frequency of the vibrating assembly 100.

[0216] In some embodiments, adjusting the number of annular structures 122 can further adjust the stiffness of the stiffening member 120 to change the stiffness Kt1 provided to the system by the stiffening member 120 and the elastic element 110 (especially the area covered by the stiffening member 120 in the central region 112), which in turn changes the resonant frequency of the reversal motion of the mass Mt1-spring Kt1-damping Rt1 system, thereby changing the second resonance position of the vibrating assembly 100. In some embodiments, adjusting the number of annular structures 122 can further vary the stiffness distribution at different positions extending from the center to the periphery of the elongated structure 124, and when the driving end frequency is close to the resonant frequency of the mass Mt1-spring Kt1-damping Rt1 system, the connection region 115, the edge region 114, and the local suspension region between the area covered by the stiffening member 120 in the central region 112 and the edge region 114 can be driven by the stiffening member 120 to vibrate, resulting in a tunable resonance peak with a 3 dB bandwidth.

[0217] In some embodiments, the number of annular structures 122 can be adjusted, and the area of ​​the openwork regions in the central region 112 can be adjusted to adjust the equivalent mass Mm i , equivalent stiffness Ka i , Ka' i , equivalent damping Ra i , Ra' i can be varied, thereby varying the third resonant peak position of the vibrating assembly 100.

[0218] In some embodiments, by adjusting the number of annular structures 122, the third resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and the area S of each openwork region is i and the thickness of the diaphragm in each openwork area H i The area-thickness ratio μ, which is the ratio of the area-thickness ratio μ to the area S of any two elastic elements 110, is in the range of 150 to 700. ki and S jiThe ratio γ of the groove structure of the reinforcing member 120 to the lateral area of ​​the reinforcing member 120 is in the range of 0.25 to 4, and the ratio β of the groove structure of the reinforcing member 120 to the lateral area of ​​the reinforcing member 120 is in the range of 0.2 to 0.7. In some embodiments, by adjusting the number of the annular structures 122, the third resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and the area S of each openwork region is i and the thickness of the diaphragm in each openwork area H i The area-thickness ratio μ is in the range of 100 to 1000, and the openwork area S of any two elastic elements 110 ki and S ji The ratio γ of the groove structure of the reinforcing member 120 to the area of ​​the reinforcing member 120 in the horizontal direction is in the range of 0.1 to 10, and the ratio β of the groove structure of the reinforcing member 120 to the area of ​​the reinforcing member 120 in the horizontal direction is in the range of 0.1 to 0.8.

[0219] 28, which is a schematic diagram of a vibrating assembly in which the inner and outer ring elongated structures are discontinuous, according to some embodiments herein. In some embodiments, when the vibrating assembly 100 includes at least two annular structures, the annular structure 122 divides the elongated structure 124 into multiple regions along the extension direction from the center to the periphery, and the elongated structures 124 within each region may be continuous or discontinuous. In some embodiments, the annular structure 122 may include a first annular structure 1221 and a second annular structure 1222 whose centers of gravity overlap, and the radial dimension of the first annular structure 1221 is smaller than the radial dimension of the second annular structure 1222. The elongated structure 124 may include at least one first elongated structure 1241 and at least one second elongated structure 1242, where the at least one first elongated structure 1241 is disposed inside and connected to the first annular structure 1221, and the at least one second elongated structure 1242 is disposed between and connected to the first annular structure 1221 and the second annular structure 1222. In some embodiments, the at least one first elongated structure 1241 and the at least one second elongated structure 1242 may be connected to the first annular structure 1221 at different locations. In some embodiments, the first elongated structure 1241 and the second elongated structure 1242 may be the same in number or different in number.

[0220] By discontinuously arranging the elongated structures 124 in the inner and outer regions of the annular structure 122, it is possible to achieve different numbers of elongated structures 124 in the inner and outer regions of the annular structure 122, different lateral widths of the elongated structures 124 in the inner and outer regions, and different lateral shapes of the elongated structures 124 in the inner and outer regions, thereby making it possible to adjust the mass, stiffness, and center of mass distribution of the reinforcing member 120, and the number and area of ​​the openwork regions in the central region 112, over a wide range.

[0221] In some embodiments, adjusting the mass of the stiffening member 120 can adjust and change the total equivalent mass Mt, thereby changing the resonant frequency of the formed mass Mt-spring Kt-damping Rt system, which in turn changes the primary resonant frequency of the vibrating assembly 100. Adjusting the stiffness of the stiffening member 120 can adjust the resonant frequency of the reversing motion of the mass Mt1-spring Kt1-damping Rt1 system, thereby changing the second resonant position of the vibrating assembly 100, and by varying the stiffness distribution at different positions extending from the center to the periphery of the elongated structure 124, a second resonant peak of the vibrating assembly 100 that can be adjusted with a 3 dB bandwidth can be obtained. Adjusting the number and area of ​​the openwork regions in the central region 112 can change the third resonant peak position and sensitivity of the vibrating assembly 100.

[0222] In some embodiments, by discontinuously placing the elongated structures 124 in the inner and outer regions of the annular structure 122, the third resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and each openwork region area S i and the thickness H of the elastic element 110 in each openwork area portion. i The area-thickness ratio μ, which is the ratio of the area-thickness ratio μ to the area S of any two elastic elements 110, is in the range of 150 to 700. ki and S ji The ratio γ of the groove structure of the reinforcing member 120 to the transverse area ratio β of the reinforcing member 120 is in the range of 0.25 to 4. In some embodiments, by discontinuously placing the elongated structures 124 in the inner and outer regions of the annular structure 122, the third resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and the area S of each openwork region is i and the thickness of the diaphragm in each openwork area H i The area-thickness ratio μ is in the range of 100 to 1000, and the openwork area S of any two elastic elements 110 ki and S ji The ratio γ of the groove structure of the reinforcing member 120 to the area of ​​the reinforcing member 120 in the horizontal direction is in the range of 0.1 to 10, and the ratio β of the groove structure of the reinforcing member 120 to the area of ​​the reinforcing member 120 in the horizontal direction is in the range of 0.1 to 0.8.

[0223] 29, which is a schematic diagram of a vibration assembly having multiple annular structures, according to some embodiments of the present disclosure. In some embodiments, the multiple annular structures 122 can be designed to have different spacing regions between the multiple annular structures 122, and the number of elongated structures 124 in different spacing regions can be designed to achieve mass distribution design for the stiffening member 120. Note that the elongated structures 124 designed for the spacing regions of each annular structure 122 may be different in number, shape, or position.

[0224] In some embodiments, the annular structures 122 are defined from the center outward as the first annular structure 1221, the second annular structure 1222, the third annular structure 1223, ... the nth annular structure, and the elongated structures 124 in the interval region between the nth annular structure and the n-1th annular structure are defined as the nth elongated structures (e.g., the first elongated structure 1241, the second elongated structure 1242, the third elongated structure 1243), and the number of the nth elongated structures is Q n where n is a natural number. The physical quantity q can be defined as the number Q of any i-th long structures. i and the number of jth long structures Q j It is defined as the ratio of

[0225] q=Q i / Q j (Formula 11)

[0226] In some embodiments, the number Q of any i-th elongated structure i and the number of jth long structures Q j The ratio q of the number of elongated structures Q to the number of elongated structures Q may range from 0.05 to 20. i and the number of j-th long structures Q j The ratio q of the number of elongated structures Q to the number of elongated structures Q may range from 0.1 to 10. i and the number of jth long structures Q j The ratio q of the number of elongated structures Q to the number of elongated structures Q may range from 0.1 to 8. i and the number of jth long structures Qj The ratio q of the number of elongated structures Q to the number of elongated structures Q may range from 0.1 to 6. i and the number of jth long structures Q j The ratio q of the number of elongated structures Q to the number of elongated structures Q may range from 0.5 to 6. i and the number of jth long structures Q j The ratio q of the number of elongated structures Q to the number of elongated structures Q may range from 1 to 4. i and the number of jth long structures Q j The ratio q of the number of elongated structures Q to the number of elongated structures Q may range from 1 to 2. i and the number of jth long structures Q j The ratio q may be in the range of 0.5 to 2.

[0227] In some embodiments, the shape of the annular structure 122 may include at least one of a circular annular structure, an elliptical annular structure, a polygonal annular structure, and a curved annular structure. By designing the annular structures 122 with different shapes and / or different dimensions, the mass and stiffness of the reinforcing member 120 can be adjusted, and the area of ​​the openwork region of the central region 112 can be adjusted.

[0228] In some embodiments, the relationship between the dimensions of the suspension region 1121 and the area of ​​the central region 112 allows the stiffening member 120 to undergo a constant bending deformation in the frequency band, realizing enhancement and cancellation due to the superposition of sound pressures in different regions of the elastic element 110, thereby realizing maximum sound pressure level output. v and the horizontal projection area S of the center of the vibration membrane of the vibration assembly 100 c Relative to

[0229]

number

[0230] may be in the range of 0.05 to 0.7. In some embodiments, the horizontal projection area S of the suspension area 1121v and the horizontal projection area S of the center of the vibration membrane of the vibration assembly 100 c Relative to

[0231]

number

[0232] may be in the range of 0.1 to 0.5. In some embodiments, the horizontal projection area S of the suspension area 1121 v and the horizontal projection area S of the center of the vibration membrane of the vibration assembly 100 c Relative to

[0233]

number

[0234] may be in the range of 0.15 to 0.35.

[0235] 30A-30E, which are schematic diagrams of vibrating assemblies having different structures, according to some embodiments of the present disclosure. In some embodiments, the outer contour of the reinforcing member 120 may be a structure with outwardly extending spokes (as shown in FIG. 30A), a circular, elliptical, or curved ring structure (as shown in FIG. 30B), a polygon, other irregular ring structure, etc., and the polygon may include a triangle, a square, a pentagon, a hexagon (as shown in FIGS. 30C and 30D), a heptagon, an octagon, a nonagon, a decagon, etc. In some embodiments, the elastic element 110 may be a polygon, such as a triangle, a square (as shown in Figures 30D and 30E), a pentagon, a hexagon, a heptagon, an octagon, a nonagon, a decagon, etc., and other irregular shapes, and accordingly, the reinforcing member 120 may be designed to have a similar or dissimilar structure, thereby controlling the shape of the suspension region 1121 by the shape of the edges of the reinforcing member 120, the central region 112, and the edge region 114, thereby achieving adjustment of the performance of the vibration assembly 100.

[0236] As shown in FIG. 31, FIG. 31 is a schematic diagram of a vibration assembly with annular structures of unequal widths, according to some embodiments herein. In some embodiments, designing local structures of unequal widths at different positions of any of the annular structures 122 can effectively adjust the mass of the stiffening member 120 and adjust and change the total equivalent mass Mt, thereby changing the resonant frequency of the formed mass Mt-spring Kt-damping Rt system and further changing the primary resonant frequency of the vibration assembly 100. Designing local structures of unequal widths at different positions (e.g., adjacent positions) of any of the annular structures 122 can adjust the stiffness and center of mass distribution of the stiffening member 120, thereby adjusting the resonant frequency of the reversal motion of the mass Mt1-spring Kt1-damping Rt1 system and changing the second resonant position of the vibration assembly 100. Designing the annular structures 122 with unequal widths further results in different stiffness distributions at different positions extending from the center to the periphery of the elongated structure 124, resulting in a second resonant peak of the vibration assembly 100 that can be adjusted with a 3 dB bandwidth. Additionally, the design of the unequal width annular structure 122 can further adjust the number and area of ​​the suspension regions in the central region 112 to change the third resonance peak position and sensitivity of the vibrating assembly 100 .

[0237] In some embodiments, by designing a local structure with unequal width at any position (e.g., adjacent positions) of any of the annular structures 122, the third resonance peak of the vibrating assembly 100 is in the range of 15 kHz to 18 kHz, and each openwork area S i and the thickness H of the elastic element 110 in each openwork area portion. i The area-thickness ratio μ, which is the ratio of the area-thickness ratio μ to the area S of any two elastic elements 110, is in the range of 150 to 700. ki and S ji The ratio γ of the groove structure of the reinforcing member 120 to the transverse area ratio β of the reinforcing member 120 is in the range of 0.25 to 4. In some embodiments, by designing a local structure with an unequal width at any position of any of the annular structures 122, the third resonance peak of the vibrating assembly 100 is in the range of 15 kHz to 18 kHz, and the area S of each openwork region is iand the thickness of the diaphragm in each openwork area H i The area-thickness ratio μ is in the range of 100 to 1000, and the openwork area S of any two elastic elements 110 ki and S ji The ratio γ of the groove structure of the reinforcing member 120 to the area of ​​the reinforcing member 120 in the horizontal direction is in the range of 0.1 to 10, and the ratio β of the groove structure of the reinforcing member 120 to the area of ​​the reinforcing member 120 in the horizontal direction is in the range of 0.1 to 0.8.

[0238] 32, which is a schematic diagram of a vibration assembly having an irregular annular structure according to some embodiments of the present disclosure. In some embodiments, by designing local structures at different positions of different annular structures 122, such as circular, rectangular, square, triangular, hexagonal, octagonal, other polygonal, elliptical, and other irregular annular structures 122, the size, position, and shape of the local area of ​​the annular structure 122 can be more flexibly controlled, and the mass of the stiffening member 120 can be effectively adjusted, and the total equivalent mass Mt can be adjusted and changed, thereby changing the resonant frequency of the formed mass Mt-spring Kt-damping Rt system, and further changing the first resonant frequency of the vibration assembly 100. By adjusting the stiffness of the stiffening member 120 and the distribution of the center of mass of the stiffening member 120, the resonant frequency of the inverted motion of the mass Mt1-spring Kt1-damping Rt1 system can be adjusted, thereby changing the second resonant peak position of the vibrating assembly 100. The stiffness distribution at different positions extending from the center to the periphery of the elongated structure 124 is different, and the second resonant peak of the vibrating assembly 100 can be adjusted with a 3 dB bandwidth. And by effectively adjusting the number and area of ​​the suspension regions in the central region 112, the third resonant peak position and sensitivity of the vibrating assembly 100 can be changed. In addition, by designing an irregular structure, stress concentration can be effectively avoided, and the deformation of the stiffening member 120 can be made smaller.

[0239] In some embodiments, as shown in FIG. 32 , the reinforcing member 120 includes a double annular structure, which includes an inner first annular structure 1221 and an outer second annular structure 1222. In some embodiments, the first annular structure 1221 and the second annular structure 1222 may have different shapes. In some embodiments, the first annular structure 1221 may be a curved annular structure, and the second annular structure 1222 may be a circular annular structure. In some embodiments, by designing the irregular annular structure 122, the third resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and each openwork area S i and the thickness of the diaphragm in each openwork area H i The area-thickness ratio μ, which is the ratio of the area of ​​the openwork region of any two diaphragms, is in the range of 150 to 700. ki and S ji The ratio γ of the groove structure of the reinforcing member 120 to the transverse area of ​​the reinforcing member 120 is in the range of 0.25 to 4, and the ratio β of the groove structure of the reinforcing member 120 to the transverse area of ​​the reinforcing member 120 is in the range of 0.2 to 0.7. In some embodiments, by designing the irregular annular structure 122, the third resonance peak of the vibrating assembly 100 is in the range of 15 kHz to 18 kHz, and each openwork area S i and the thickness of the diaphragm in each openwork area H i The area-thickness ratio μ is in the range of 100 to 1000, and the openwork area S of any two elastic elements 110 ki and S ji The ratio γ of the groove structure of the reinforcing member 120 to the area of ​​the reinforcing member 120 in the horizontal direction is in the range of 0.1 to 10, and the ratio β of the groove structure of the reinforcing member 120 to the area of ​​the reinforcing member 120 in the horizontal direction is in the range of 0.1 to 0.8.

[0240] 33A-33B, FIG. 33A is a schematic diagram of a vibration assembly including a stepped elongated structure according to some embodiments of the present disclosure. FIG. 33B is a schematic diagram of a vibration assembly including a stepped elongated structure according to other embodiments of the present disclosure. In some embodiments, as shown in FIG. 33A, by designing a reinforcing member 120 including a stepped elongated structure 124, it is possible to ensure that the stiffness, mass, and center of mass distribution of the reinforcing member 120 are changed without controlling and changing the openwork area (affecting the third resonance peak of the vibration assembly 100) and the suspension area 1121 of the central region 112. This can effectively adjust the first resonance peak position, second resonance peak position, and bandwidth of the vibration assembly 100 without changing the third resonance peak of the vibration assembly 100, thereby adjusting different frequency response curves according to actual application needs.

[0241] In some embodiments, by designing the thickness of different regions of the reinforcing member 120 in the thickness direction (i.e., along the vibration direction of the vibration assembly 100), the mass of the reinforcing member 120 can be left unchanged or changed according to the actually required mass distribution, while the stiffness of the reinforcing member 120 itself can be changed, so that the stiffness Kt1 provided to the system by the reinforcing member 120 and the elastic element 110 changes, and further the resonant frequency of the inversion motion of the mass Mt1-spring Kt1-damping Rt1 system changes, thereby changing the position of the second resonant peak of the vibration assembly 100, and further controlling the 3 dB bandwidth of the second resonant peak of the vibration assembly 100.

[0242] 33B shows the structure of a reinforcing member 120 having a step-shaped elongated structure 124 and its cross-sectional structure in the DD cross section. The thickness of the outermost step in the structure of the reinforcing member 120 is defined as h1, the thickness of the step most inward from the edge as h2..., and the thickness of the central step as hn, and the physical quantity ε is defined as the ratio of the thicknesses of any two steps hj and hk (k>j).

[0243] ε=hj / hk (Equation 12)

[0244] The physical quantity φ is defined as the ratio of the thickness h1 of the outermost step in the structure of the reinforcing member 120 to the thickness hn of the central step.

[0245] φ=h1 / hn (Equation 13)

[0246] In some embodiments, to ensure the strength of the reinforcing member 120, the ratio ε between the thicknesses hj and hk of any two steps is in the range of 0.1 to 10. In some embodiments, to ensure the strength of the reinforcing member 120, the ratio ε between the thicknesses hj and hk of any two steps is in the range of 0.1 to 8. In some embodiments, to ensure the strength of the reinforcing member 120, the ratio ε between the thicknesses hj and hk of any two steps is in the range of 0.2 to 8. In some embodiments, to ensure the strength of the reinforcing member 120, the ratio ε between the thicknesses hj and hk of any two steps is in the range of 0.1 to 7. In some embodiments, to ensure the strength of the reinforcing member 120, the ratio ε between the thicknesses hj and hk of any two steps is in the range of 0.1 to 6. In some embodiments, to ensure the strength of the reinforcing member 120, the ratio ε between the thicknesses hj and hk of any two steps is in the range of 0.2 to 6. In some embodiments, to ensure the strength of the reinforcing member 120, the ratio ε of the thicknesses hj and hk of any two steps is in the range of 0.2 to 5.

[0247] To accommodate the frequency response of some vibration assemblies 100 requiring a low Q factor and a wide bandwidth, the stiffening member 120 can be designed to have a large mass concentrated near the center. In some embodiments, to increase the mass of the central region of the stiffening member 120, the ratio φ of the thickness h1 of the outermost step of the structure of the stiffening member 120 to the thickness h of the central step is in the range of 0.1 to 1. In some embodiments, to increase the mass of the central region of the stiffening member 120, the ratio φ of the thickness h1 of the outermost step of the structure of the stiffening member 120 to the thickness h of the central step is in the range of 0.2 to 0.8. In some embodiments, to increase the mass of the central region of the stiffening member 120, the ratio φ of the thickness h1 of the outermost step of the structure of the stiffening member 120 to the thickness h of the central step is in the range of 0.2 to 0.6. In some embodiments, to increase the mass of the central region of the stiffening member 120, the ratio φ of the thickness h1 of the outermost step of the structure of the stiffening member 120 to the thickness h of the central step is in the range of 0.2 to 0.4.

[0248] To accommodate the frequency response of some vibration assemblies 100 requiring a high Q factor and narrow bandwidth, the stiffening member 120 can be designed to have a large mass concentrated at its edge region. In some embodiments, to increase the mass at the edge region of the stiffening member 120, the ratio φ of the thickness of the outermost step h1 of the stiffening member 120 to the thickness of the central step h1 is in the range of 1 to 10. In some embodiments, to increase the mass at the edge region of the stiffening member 120, the ratio φ of the thickness of the outermost step h1 of the stiffening member 120 to the thickness of the central step h1 is in the range of 1.2 to 6. In some embodiments, to increase the mass at the edge region of the stiffening member 120, the ratio φ of the thickness of the outermost step h1 of the stiffening member 120 to the thickness of the central step h1 is in the range of 2 to 6. In some embodiments, to increase the mass at the edge region of the stiffening member 120, the ratio φ of the thickness of the outermost step h1 of the stiffening member 120 to the thickness of the central step h1 is in the range of 3 to 6. In some embodiments, to increase the mass of the edge regions of the reinforcing member 120, the ratio φ of the thickness h1 of the most edge step to the thickness hn of the central step of the structure of the reinforcing member 120 is in the range of 4 to 6. In some embodiments, to increase the mass of the edge regions of the reinforcing member 120, the ratio φ of the thickness h1 of the most edge step to the thickness hn of the central step of the structure of the reinforcing member 120 is in the range of 5 to 6.

[0249] 34A-34C, which are schematic diagrams of vibration assemblies having reinforcing members of different shapes, according to some embodiments herein. In FIG. 34A, the reinforcing member 120 has a rectangular shape, the annular structure 122 has a single annular rectangular structure, and the elongated structure 124 has a trapezoidal structure. In FIG. 34B, the reinforcing member 120 has a rectangular shape, the annular structure 122 has a double annular rectangular structure, and the elongated structure 124 has a trapezoidal structure. In FIG. 34C, the reinforcing member 120 has a hexagonal shape, the annular structure 122 has a single annular hexagonal structure, and the elongated structure 124 has a trapezoidal structure. In some embodiments, the shape of the reinforcing member 120 of the vibration assembly 100 may match the shape of the elastic element 110. The elastic element 110 may have various shapes, such as a circular shape, a square shape, a polygonal shape, etc. The shape of the corresponding reinforcing member 120 may be designed in different shapes, including, but not limited to, circular, rectangular (e.g., rectangular, square), triangular, hexagonal, octagonal, other polygonal, elliptical, and other irregular structures.

[0250] The resonant frequency of the vibration assembly 100 can be changed by flexibly designing different shapes of the reinforcing member 120 and different shapes of the elastic element 110 to change the mass and stiffness of the reinforcing member 120 and the mass and stiffness of the vibration assembly 100, etc.

[0251] In some embodiments, the shape of the reinforcing member 120 and the shape of the elastic element 110 may both include a plurality of different shapes, such as designing different lateral widths and shapes for the elongated structures 124 extending from the central region 112 to the periphery, designing annular structures 122, designing annular structures 122 with different shapes, numbers, and sizes, and designing annular structures 122 to be generally annular or to be local annular structures 122. The different annular structures 122 divide the elongated structure 124 into different regions, and in the different regions, the elongated structures 124 in the different regions from the center to the periphery may be continuous, intersecting, and may be equal or unequal in number. In some embodiments, the annular structures 122 may be designed to be circular, rectangular (e.g., rectangular, square), triangular, hexagonal, octagonal, other polygonal, elliptical, and other irregularly shaped structures.

[0252] In some embodiments, by designing the vibrating assembly 100 to include stiffening members 120 with different shapes, the third resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and each openwork area S i and the thickness H of the elastic element 110 in each openwork area portion. i The area-thickness ratio μ, which is the ratio of the area-thickness ratio μ to the area S of any two elastic elements 110, is in the range of 150 to 700. ki and S ji The ratio γ of the groove structure to the reinforcing member 120 is in the range of 0.25 to 4, and the lateral area ratio β of the groove structure to the reinforcing member 120 is in the range of 0.2 to 0.7. In some embodiments, by designing the vibrating assembly 100 including the reinforcing member 120 with different shapes, the third resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and the area S of each openwork region is i and the thickness H of the elastic element 110 in each openwork area portion. i The area-thickness ratio μ is in the range of 100 to 1000, and the openwork area S of any two elastic elements 110 ki and S ji The ratio γ of the groove structure to the reinforcing member 120 is in the range of 0.1 to 10, and the lateral area ratio β of the groove structure to the reinforcing member 120 is in the range of 0.1 to 0.8.

[0253] 35A-35D, which are schematic diagrams of vibration assemblies including localized mass structures, according to some embodiments herein. FIG. 35A illustrates a double elastically connected localized mass structure 126, FIG. 35B illustrates a quadruple elastically connected localized mass structure 126, FIG. 35C illustrates a quadruple S-shaped elastically connected localized mass structure 126, and FIG. 35D illustrates an irregular quadruple S-shaped elastically connected localized mass structure 126. In some embodiments, the localized mass structures 126 are designed in the suspension region of the central region 112 to provide an equivalent mass Mm of each openwork region. i , equivalent stiffness Ka i , Ka' i , equivalent damping Ra i , Ra' i By flexibly adjusting the stiffness of the stiffening member 120, the third resonance peak of the vibrating assembly 100 can be effectively adjusted. Furthermore, by designing the local mass structure 126, the mass and stiffness of the stiffening member 120 can be further adjusted in a wide range to adjust the first resonance peak and the second resonance peak of the vibrating assembly 100.

[0254] In some embodiments, a local mass structure 126 may be circumferentially connected to an adjacent elongate structure 124 by a dual elastic structure (as shown in FIG. 35A ), or may be circumferentially connected to an adjacent annular structure 122 by a dual elastic structure. In other embodiments, each local mass structure 126 may not be connected to either an elongate structure 124 or annular structure 122, but may be connected only to the elastic element 110.

[0255] In some embodiments, the localized mass structure 126 may be connected to both adjacent elongated structures 124 and annular structures 122 by a four-fold elastic structure (shown in FIG. 35B). In some embodiments, the planar shape of the elastic structure may be a regular shape (shown in FIGS. 35A and 35B) or an irregular shape (shown in FIG. 35C). In some embodiments, the localized mass structure 126 may have a regular shape (shown in FIGS. 35A-35C) or an irregular shape (shown in FIG. 35D).

[0256] In some embodiments, by designing the dimensions, location, number, and shape of the local mass structures 126 and the dimensions, location, number, and shape of the elastically connected structures, the third resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and each openwork area S i and the thickness H of the elastic element 110 in each openwork area portion. i The area-thickness ratio μ, which is the ratio of the area-thickness ratio μ to the area S of any two elastic elements 110, is in the range of 150 to 700. ki and S ji The ratio γ of the groove structure to the reinforcing member 120 is in the range of 0.25 to 4, and the lateral area ratio β of the groove structure to the reinforcing member 120 is in the range of 0.2 to 0.7. In some embodiments, by designing the dimensions, location, number, and shape of the local mass structure 126 and the dimensions, location, number, and shape of the elastically connected structures, the third resonant peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and the area S of each openwork region is i and the thickness H of the elastic element 110 in each openwork area portion. i The area-thickness ratio μ is in the range of 100 to 1000, and the openwork area S of any two elastic elements 110 ki and S ji The ratio γ of the groove structure to the reinforcing member 120 is in the range of 0.1 to 10, and the lateral area ratio β of the groove structure to the reinforcing member 120 is in the range of 0.1 to 0.8.

[0257] Although the basic concepts have been described above, it will be apparent to those skilled in the art that the above detailed disclosure is merely provided as an example and is not intended to limit the present application. Although not expressly described herein, those skilled in the art may make various changes, improvements, and modifications to the present application. These changes, improvements, and modifications are intended to be suggested by the present application and therefore remain within the spirit and scope of the exemplary embodiments of the present application.

[0258] Additionally, certain terms are used herein to describe embodiments of the present application. For example, "one embodiment," "one embodiment," and / or "some embodiments" refer to particular features, structures, or characteristics associated with at least one embodiment of the present application. Therefore, it is emphasized and understood that the appearances of "one embodiment" or "one embodiment" or "one alternative embodiment" more than once in various parts of this specification do not necessarily all refer to the same embodiment. Furthermore, particular features, structures, or characteristics of one or more embodiments of the present application may be combined as appropriate.

[0259] Furthermore, unless expressly stated in the claims, the recitation order, use of alphanumeric characters, or use of other designations of process elements or sequences described herein does not limit the order of the procedures and methods of the present application. While the foregoing disclosure has set forth through various examples what are presently believed to be various useful embodiments of the invention, it is to be understood that such details are merely illustrative, and that the appended claims are not limited to only the disclosed embodiments, but on the contrary, are intended to cover all modifications and equivalent combinations falling within the spirit and scope of the embodiments of the present application.

[0260] Similarly, in the foregoing description of embodiments of the present application, it should be understood that various features may be grouped together in a single embodiment, drawing, or description for the purpose of simplifying the description of the present disclosure and facilitating an understanding of one or more embodiments of the present invention. However, this method of disclosure should not be interpreted as reflecting an intention that the present subject matter requires more features than are recited in each claim. In fact, an embodiment may include fewer than all features of a single embodiment disclosed above.

[0261] In some examples, numbers describing the number of components and attributes are used; it should be understood that the numbers describing such examples are, in some instances, modified by the modifiers "about," "approximately," or "generally." Unless otherwise specified, "about," "approximately," or "generally" indicates that the number may vary by ±20%. Thus, in some examples, all numerical parameters used in the specification and claims are approximations that may vary depending on the specific requirements of a particular example. In some examples, numerical parameters should be calculated using the specified number of significant digits and ordinary rounding techniques. While in some examples, the numerical ranges and parameters used to determine ranges are approximations, in specific examples, such numerical values ​​are determined as precisely as possible.

[0262] Finally, it should be understood that the embodiments described herein are merely illustrative of the principles of the present embodiments. Other variations may be within the scope of the present application. Thus, by way of example, but not of limitation, alternative configurations of the present embodiments may be considered consistent with the teachings of the present application. Thus, the present embodiments are not limited to the embodiments expressly introduced and described herein. [Explanation of symbols]

[0263] 100 Vibration Assembly 110 Elastic element 112 Central area 114 Edge Area 116 Fixed area 120 Reinforcement member 121 Groove structure 122 Ring Structure 124 Long structure

Claims

1. 1. A vibration assembly comprising: an elastic element, the elastic element including a central region, an edge region disposed on the outer periphery of the central region, and a fixed region disposed on the outer periphery of the edge region, the elastic element being configured to vibrate along a direction perpendicular to the central region; the central region including an elastic member and a reinforcing member stacked along a vibration direction; the reinforcing member having a plurality of groove structures with openings facing the elastic member; and an openwork structure disposed on the reinforcing member in an area other than the plurality of groove structures.

2. 2. The vibration assembly according to claim 1, wherein a ratio of a projected area of ​​the reinforcing member to a projected area of ​​the central region in the vibration direction is in a range of 0.15 to 0.

8.

3. 10. The vibrating assembly of claim 1, wherein when vibrating, a resonant peak appears in the range of at least 10,000 Hz to 20,000 Hz.

4. 2. The vibration assembly of claim 1, wherein the groove structure has a height dimension along the vibration direction, a sidewall of the groove structure has a thickness dimension, and a ratio of the height dimension to the thickness dimension is in the range of 7.14 or greater.

5. The vibrating assembly of claim 4, wherein when vibrating, a resonant peak appears in the range of at least 5000 Hz to 10000 Hz.

6. The vibration assembly according to claim 1 , wherein the groove structure has a height dimension along the vibration direction, and the value of the height dimension is in the range of 50 μm to 500 μm.

7. The vibratory assembly of claim 1 , wherein the sidewalls of the groove structure have a thickness dimension, the thickness dimension having a value in the range of 50 μm or less.

8. The vibrating assembly of claim 1 , wherein an opening of the groove structure is provided with a skirt structure extending along the surface of the elastic member, and the width of the skirt structure is in the range of 100 μm to 300 μm.

9. The vibratory assembly of claim 1 , wherein the shape of the groove structure includes at least one of a U-shape, a T-shape, an U-shape, and a cone-shape.

10. The vibrating assembly of claim 1 , wherein the Young's modulus of the material of the stiffening member is higher than the Young's modulus of the material of the elastic member.

11. The vibrating assembly of claim 1 , wherein the material of the stiffening member is the same as the material of the elastic member.

12. The vibratory assembly of claim 1 , wherein a filler material is disposed within the groove structure, and the filler material has a Young's modulus that is less than the Young's modulus of the material of the reinforcing member.

13. A vibration assembly comprising an elastic element, the elastic element including a central region, an edge region disposed on the outer periphery of the central region, and a fixing region disposed on the outer periphery of the edge region, the elastic element being configured to vibrate along a direction perpendicular to the central region, the central region including a reinforcing region and an elastic region arranged in parallel, the reinforcing region having a plurality of groove structures with openings facing the vibration direction, and the reinforcing region having an openwork structure in an area other than the plurality of groove structures.

14. 14. The vibration assembly according to claim 13, wherein a ratio of a projected area of ​​the reinforced region to a projected area of ​​the central region in the vibration direction is in a range of 0.15 to 0.8.

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