CN116801169A

CN116801169A - Vibration assembly and loudspeaker

Info

Publication number: CN116801169A
Application number: CN202210564070.4A
Authority: CN
Inventors: 周文兵; 王庆依; 张磊; 齐心; 廖风云
Original assignee: Shenzhen Voxtech Co Ltd
Current assignee: Shenzhen Voxtech Co Ltd
Priority date: 2022-03-18
Filing date: 2022-05-23
Publication date: 2023-09-22
Also published as: CN116801170A

Abstract

One or more embodiments of the present specification relate to a speaker including: a driving assembly generating vibration based on an electrical signal; a vibration assembly receiving vibration of the driving assembly to generate vibration; wherein the vibration assembly comprises an elastic element and a stiffener; the elastic element comprises a central area, a folding ring area arranged at the periphery of the central area and a fixing area arranged at the periphery of the folding ring area, and the elastic element is configured to vibrate along the direction perpendicular to the central area; the reinforcing member is connected with the central area, the reinforcing member comprises a reinforcing part and a plurality of hollowed-out parts, and the vibration of the reinforcing member and the elastic element generates at least two resonance peaks in the audible range of human ears.

Description

Vibration assembly and loudspeaker

Cross reference

The present application claims priority to chinese application number 202210270065.2 filed at 18, 2022, 03, the contents of which are incorporated herein by reference.

Technical Field

The application relates to the technical field of acoustics, in particular to a vibration assembly and a loudspeaker.

Background

The speaker generally includes three main core portions of a driving portion, a vibrating portion, and a supporting auxiliary portion. The vibration part is also a load part of the loudspeaker and is mainly a vibrating diaphragm component. The diaphragm assembly generally increases the stiffness of the central region of the diaphragm by providing a stiffener. However, setting the stiffener too large increases the load on the speaker, and the driving end and the load end are mismatched in impedance, so that the sound pressure level of the speaker output is reduced; the reinforcing member is set too small, and it is difficult to avoid a state in which sound is canceled due to the split mode formed in the center region of the diaphragm.

Therefore, how to reasonably arrange the reinforcing piece to realize controllable adjustment of the local rigidity of the central area of the vibrating diaphragm is an urgent problem to be solved.

Disclosure of Invention

In one aspect, embodiments of the present disclosure provide a vibration assembly comprising: an elastic element including a central region, a folded ring region disposed at a periphery of the central region, and a fixed region disposed at a periphery of the folded ring region, the elastic element being configured to vibrate in a direction perpendicular to the central region; the reinforcing piece is connected with the central area and comprises a reinforcing part and a plurality of hollowed-out parts; wherein the stiffener is configured such that the vibration assembly has at least a resonance peak at 10000Hz-18000Hz when vibrated.

Another aspect of the embodiments of the present specification provides a speaker, including: a driving assembly generating vibration based on an electrical signal; a vibration assembly receiving vibration of the driving assembly to generate vibration; wherein the vibration assembly comprises an elastic element and a stiffener; the elastic element comprises a central area, a folding ring area arranged at the periphery of the central area and a fixing area arranged at the periphery of the folding ring area, and the elastic element is configured to vibrate along the direction perpendicular to the central area; the reinforcing piece is connected with the central area and comprises a reinforcing part and a plurality of hollowed-out parts; the stiffener is configured such that the vibration assembly has at least a resonance peak at 10000Hz-18000Hz when vibrated.

Drawings

The application will be further described by way of exemplary embodiments, which will be described in detail with reference to the accompanying drawings. The embodiments are not limiting, in which like numerals represent like structures, wherein:

FIG. 1 is a schematic illustration of a vibration assembly and its equivalent vibration model shown in accordance with some embodiments of the present description;

FIG. 2 is a schematic illustration of a deformation of a vibration assembly at a first resonance peak shown in accordance with some embodiments of the present disclosure;

FIG. 3 is a schematic illustration of a deformation of a vibration assembly at a second resonance peak shown in accordance with some embodiments of the present disclosure;

FIG. 4 is a schematic illustration of a deformation of a vibration assembly at a third resonance peak shown in accordance with some embodiments of the present disclosure;

FIG. 5 is a schematic illustration of a deformation of the vibration assembly at a fourth resonance peak shown in accordance with some embodiments of the present disclosure;

FIG. 6 is a schematic diagram of a frequency response curve of a vibration assembly having different third and fourth resonant frequency differences according to some embodiments of the present disclosure;

FIG. 7A is a schematic diagram of a frequency response curve of a vibration assembly according to some embodiments of the present disclosure;

FIG. 7B is a schematic diagram of a frequency response curve of a vibration assembly according to other embodiments of the present disclosure;

FIG. 7C is a schematic diagram of a frequency response curve of a vibration assembly according to other embodiments of the present disclosure;

FIG. 7D is a schematic diagram of a frequency response curve of a vibration assembly according to other embodiments of the present disclosure;

FIG. 8A is a schematic diagram of a vibration assembly according to some embodiments of the present disclosure;

FIG. 8B is a schematic diagram of a frequency response curve of a vibration assembly according to other embodiments of the present disclosure;

FIG. 9A is a schematic partial structural view of a vibration assembly according to some embodiments of the present disclosure;

FIG. 9B is a schematic diagram of a frequency response curve of a vibration assembly according to other embodiments of the present disclosure;

FIG. 9C is a schematic diagram of a frequency response curve of a vibration assembly according to other embodiments of the present disclosure;

FIG. 10A is a schematic diagram illustrating a deformation of a vibration assembly at a fourth resonance peak according to other embodiments of the present disclosure;

FIG. 10B is a schematic diagram of a frequency response curve of a vibration assembly according to other embodiments of the present disclosure;

FIG. 10C is a schematic diagram of a frequency response curve of a vibration assembly according to other embodiments of the present disclosure;

FIG. 11 is a schematic diagram illustrating a deformation of a vibration assembly at a fourth resonance peak according to other embodiments of the present disclosure;

FIG. 12A is a schematic diagram of the frequency response of the vibration assembly of FIG. 11;

FIG. 12B is a schematic diagram of a frequency response curve of a vibration assembly according to other embodiments of the present disclosure;

FIG. 13A is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 13B is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 14A is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 14B is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 14C is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 14D is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 15A is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 15B is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 16A is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 16B is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 16C is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 16D is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 16E is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 16F is a schematic diagram of a frequency response curve of a vibration assembly according to other embodiments of the present disclosure;

FIG. 17A is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 17B is a schematic diagram of a vibration assembly according to other embodiments of the present disclosure;

FIG. 17C is a schematic diagram of a frequency response curve of a vibration assembly according to other embodiments of the present disclosure;

FIG. 18A is a schematic diagram of a vibration assembly according to other embodiments of the present disclosure;

FIG. 18B is a schematic diagram of a vibration assembly according to other embodiments of the present disclosure;

FIG. 18C is a schematic diagram of a vibration assembly according to other embodiments of the present disclosure;

FIG. 19 is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 20A is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 20B is a schematic diagram of a frequency response curve of a vibration assembly according to other embodiments of the present disclosure;

FIG. 21A is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 21B is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 21C is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 21D is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 21E is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 22 is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 23 is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 24A is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 24B is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 24C is a schematic diagram illustrating a frequency response of a vibration assembly according to further embodiments of the present disclosure;

FIG. 25A is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 25B is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 25C is a schematic view of a vibration assembly according to other embodiments of the present disclosure;

FIG. 26A is a schematic diagram of a vibration assembly according to other embodiments of the present disclosure;

FIG. 26B is a schematic diagram of a vibration assembly according to other embodiments of the present disclosure;

FIG. 26C is a schematic diagram of a vibration assembly according to other embodiments of the present disclosure;

FIG. 26D is a schematic diagram of a vibration assembly according to other embodiments of the present disclosure;

FIG. 26E is a schematic cross-sectional view of a stiffener according to some embodiments of the present description;

fig. 27 is an exemplary block diagram of a speaker shown in accordance with some embodiments of the present description.

Reference numerals illustrate: and (3) a vibration assembly: 100 2710; elastic element: 110 2711;112, central region: 2711a,2812; suspended area: 1121 2711E; the folded ring area: 114 2711B; connection region: 115 2711D; fixing area: 116 2711C; reinforcement: 120 2712; the annular structure is as follows: 122, a step of; first annular structure: 1221; second annular structure: 1222; third annular structure: 1223; center connection: 123, a step of; bar-shaped structure: 124; first bar structure: 1241; second bar structure: 1242; third bar structure: 1243; reinforcing portion: 125; local mass structure: 126; hollow part: 127; first resonance peak: 210; second resonance peak: 220; third resonance peak: 230, a step of; fourth resonance peak: 240, a step of; frequency response curve: 710. Frequency response curve: 720, a step of selecting a specific part; frequency response curve: 810 820, 830, 910, 920, 940, 950, 1010, 1020, 1030, 1040, 1050, 1060, 1210, 1220, 1230; a loudspeaker: 2700; and a driving assembly: 2720; a driving unit: 2722; a vibration transmission unit: 2724; a shell: 2730; front cavity: 2731; a first hole portion: 2732; rear cavity: 2733; a second hole portion: 2734; damping net: 27341; support element: 2740.

Detailed Description

In order to more clearly illustrate the technical solution of the embodiments of the present application, the drawings that are required to be used in the description of the embodiments will be briefly described below. It is apparent that the drawings in the following description are only some examples or embodiments of the present application, and it is apparent to those of ordinary skill in the art that the present application may be applied to other similar situations according to the drawings without inventive effort. Unless otherwise apparent from the context of the language or otherwise specified, like reference numerals in the figures refer to like structures or operations.

It will be appreciated that "system," "apparatus," "unit" and/or "module" as used herein is one method for distinguishing between different components, elements, parts, portions or assemblies of different levels. However, if other words can achieve the same purpose, the words can be replaced by other expressions.

As used in the specification and in the claims, the terms "a," "an," "the," and/or "the" are not specific to a singular, but may include a plurality, unless the context clearly dictates otherwise. In general, the terms "comprises" and "comprising" merely indicate that the steps and elements are explicitly identified, and they do not constitute an exclusive list, as other steps or elements may be included in a method or apparatus.

A flowchart is used in the present application to describe the operations performed by a system according to embodiments of the present application. It should be appreciated that the preceding or following operations are not necessarily performed in order precisely. Rather, the steps may be processed in reverse order or simultaneously. Also, other operations may be added to or removed from these processes.

Embodiments of the present disclosure provide a vibration assembly that may be applied to a variety of acoustic output devices. Acoustic output devices include, but are not limited to, speakers, hearing aids, and the like. The vibration assembly provided in the embodiments of the present specification mainly includes an elastic member and a reinforcing member, wherein the elastic member or the reinforcing member may be connected to a driving portion of a speaker, and an edge of the elastic member is fixed (e.g., connected to a housing of the speaker). In the speaker, a driving portion of the speaker serves as an electric-mechanical energy conversion unit that provides driving force to the speaker by converting electric energy into mechanical energy. The vibration assembly can receive the force or displacement transmitted by the driving part to generate corresponding vibration output, so that air motion is pushed to generate sound pressure. The elastic element can be regarded as being connected to the air inertial load part by means of springs, damping, and the radiation of sound pressure is achieved by pushing the air movement.

The elastic element mainly comprises a central area, a folding ring area arranged at the periphery of the central area and a fixing area arranged at the periphery of the folding ring area. In some embodiments, in order to make the speaker have a relatively flat sound pressure level output in a relatively large range (for example, 20Hz-20 kHz), a preset pattern may be designed in the folded ring area of the elastic element, so as to destroy the vibration mode of the folded ring area of the elastic element in a corresponding frequency band, avoid the occurrence of acoustic cancellation caused by local split vibration of the elastic element, and increase the local rigidity of the elastic element through the pattern design. Further, by designing a thickened structure in the central region of the elastic element, the rigidity of the central region of the elastic element is increased, and the situation that the sound is eliminated due to the fact that the split vibration mode is formed in the central region of the elastic element of the loudspeaker in the range of 20Hz-20kHz is avoided. However, the thickening layer is directly designed in the central area of the elastic element, so that the overall mass of the vibration assembly is increased, the load of the loudspeaker is increased, the impedance mismatch between the driving end and the load end is caused, and the sound pressure level of the output of the loudspeaker is reduced. The vibration component provided by the embodiment of the specification is used for structurally designing the elastic element and the reinforcing piece, wherein the reinforcing piece comprises one or more annular structures and one or more strip-shaped structures, and each of the one or more strip-shaped structures is connected with at least one of the one or more annular structures, so that the vibration component can have a required high-order mode at medium and high frequencies (more than 3 kHz), and a plurality of resonance peaks appear on a frequency response curve of the vibration component, and further the vibration component has higher sensitivity in a wider frequency band range; meanwhile, through the structural design of the reinforcing piece, the mass of the vibration component is smaller, the overall sensitivity of the vibration component is improved, and through reasonable arrangement of the reinforcing piece, the central area of the elastic element is provided with a plurality of hollow areas, so that the local rigidity of the central area of the elastic element is controllably adjusted, the resonance peak output by the vibration component is controllably adjusted by utilizing the split vibration modes of the hollow areas of the central area, and the vibration component has a flatter sound pressure level curve. For details of the vibration assembly, the elastic element and the stiffener, reference is made to the following description.

Referring to fig. 1, fig. 1 is a schematic diagram of a vibration assembly and its equivalent vibration model according to some embodiments of the present description.

In some embodiments, the vibration assembly 100 mainly includes an elastic element 110, where the elastic element 110 includes a central region 112, a folded-ring region 114 disposed at the periphery of the central region 112, and a fixing region 116 disposed at the periphery of the folded-ring region 114. The elastic element 110 is configured to vibrate in a direction perpendicular to the central region 112 to transfer the force and displacement received by the vibration assembly 100 to push air movement. The stiffener 120 is coupled to the central region 112, the stiffener 120 including one or more annular structures 122 and one or more bar structures 124, each of the one or more bar structures 124 being coupled to at least one of the one or more annular structures 122; wherein at least one of the one or more bar structures 124 extends toward the center of the central region 112. By reasonably arranging the reinforcing member 120, a plurality of hollowed-out areas are arranged in the central area 112 of the elastic element 110, so that the local rigidity of the central area 112 of the elastic element 110 can be controlled and adjusted, and the resonance peak output by the vibration assembly can be controlled and adjusted by utilizing the split vibration modes of each hollowed-out area of the central area 112, so that the vibration assembly 100 has a flatter sound pressure level curve. Meanwhile, the annular structure 122 and the strip-shaped structure 124 are matched with each other, so that the reinforcing piece 120 is provided with a reinforcing part and a hollowed part (namely a hollowed part) in a proper proportion, the quality of the reinforcing piece 120 is reduced, the overall sensitivity of the vibration assembly 100 is improved, and meanwhile, the positions of a plurality of resonance peaks of the vibration assembly 100 can be adjusted by designing the shape, the size and the number of the annular structure 122 and the strip-shaped structure 124, so that the vibration output of the vibration assembly 100 is controlled.

The elastic member 110 may be a member capable of being elastically deformed by an external load. In some embodiments, the resilient element 110 may be a high temperature resistant material such that the resilient element 110 maintains performance during manufacturing of the vibration assembly 100 when applied to a speaker. In some embodiments, the elastic element 110 has no or little change (e.g., within 5%) in Young's modulus, which may be used to characterize the ability of the elastic element 110 to deform when stretched or compressed, and in shear modulus, which may be used to characterize the ability of the elastic element 110 to deform when sheared, when exposed to an environment of 200-300 ℃. In some embodiments, the elastic element 110 may be a material having good elasticity (i.e., being subject to elastic deformation), such that the vibration assembly 100 has good vibration response capability. In some embodiments, the material of the elastic element 110 may be one or more of organic polymer materials, glue materials, and the like. In some embodiments, the organic polymeric material may be any one or combination of Polycarbonate (PC), polyamide (PA), acrylonitrile-butadiene-styrene (Acrylonitrile Butadiene Styrene, ABS), polystyrene (PAR), high impact Polystyrene (High Impact Polystyrene, HIPS), polypropylene (PP), polyethylene terephthalate (Polyethylene Terephthalate, PET), polyvinyl chloride (Polyvinyl Chloride, PVC), polyurethane (PU), polyethylene (PE), phenolic resin (Phenol Formaldehyde, PF), urea-Formaldehyde resin (Urea-Formaldehyde, UF), melamine-Formaldehyde resin (Melamine-Formaldehyde, MF), polyarylate (PAR), polyether imide (PEI), polyimide (PI), polyethylene naphthalate (Polyethylene Naphthalate two formic acid glycol ester, PEN), polyether ketone (PEEK), carbon fiber, silica gel, and the like. In some embodiments, the organic polymer material may also be various glues including, but not limited to, gels, silicone gels, acrylics, urethanes, rubbers, epoxies, hot melts, photo-curing, etc., preferably silicone adhesives, silicone sealing adhesives.

In some embodiments, the shore hardness of resilient element 110 may be 1-50HA. In some embodiments, the elastomeric element 110 may have a shore hardness of 1-15HA. In some embodiments, the elastomeric element 110 may have a shore hardness of 14.9-15.1HA.

In some embodiments, the Young's modulus of the elastic element 110 ranges from 5E8Pa to 1E10Pa. In some embodiments, the Young's modulus of the elastic element 110 ranges from 1E9Pa to 5E9Pa. In some embodiments, the Young's modulus of the elastic element 110 ranges from 1E9Pa to 4E9Pa. In some embodiments, the Young's modulus of the elastic element 110 ranges from 2E9Pa to 5E9Pa.

In some embodiments, the elastic element 110 has a density in the range of 1E3kg/m ³ -4E3kg/m ³ . In some embodiments, the elastic element 110 has a density in the range of 1E3kg/m ³ -2E3kg/m ³ . In some embodiments, the elastic element 110 has a density in the range of 1E3kg/m ³ -3E3kg/m ³ . In some embodiments, the elastic element 110 has a density in the range of 1E3kg/m ³ -1.5E3kg/m ³ . In some embodiments, the density of the elastic element 110 is in the range of 1.5E3kg/m ³ -2E3kg/m ³ 。

In some embodiments, when the vibration assembly is applied to a speaker, the central region 112 of the elastic element 110 may be directly connected to the driving portion of the speaker. In other embodiments, the stiffener 120 disposed in the central region 112 of the resilient element 110 may be directly coupled to the driving portion of the speaker. The central region 112 of the elastic member 110 and the reinforcement 120 can transmit the force and displacement of the driving part to push the air to move, and output sound pressure.

The central region 112 refers to a region of the elastic member 110 extending from the center (e.g., centroid) to the circumferential side by a certain area, and the reinforcing member 120 is connected to the central region 112. The elastic element 110 is configured to vibrate in a direction perpendicular to the central region 112. The central region 112 serves as the primary vibration region of the elastic element 110, and can transmit force and displacement and output vibration response.

The tuck-ring region 114 is located outside the central region 112. In some embodiments, the folded ring region 114 may be designed with a pattern of a characteristic shape, so as to destroy the vibration mode of the folded ring region 114 of the elastic element 110 in a corresponding frequency band, avoid the occurrence of acoustic cancellation caused by local split vibration of the elastic element 110, and increase the local rigidity of the elastic element 110 through the pattern design.

In some embodiments, the tuck-loop region 114 may include a tuck-loop structure. In some embodiments, by adjusting parameters such as the width and the camber of the folded ring, the rigidity of the folded ring region 114 corresponding to the folded ring structure may be different, and the frequency band of the corresponding high-frequency local split mode may be different. The gimbal width may be the radial width of the projected gimbal region 114 along the vibration direction of the elastic element 110. The camber refers to the height of the bellows region 114 protruding from the central region 112 or the fixing region 116 in the vibration direction of the elastic element 110.

In some embodiments, the maximum area of the one or more annular structures 122 of the stiffener 120 projected in the vibration direction of the elastic element 110 is smaller than the area of the central region 112. That is, there is a region between the outermost projected side of the stiffener 120 and the folded-over region 114 that is not supported by the stiffener 120, and a partial region of the central region 112 between the folded-over region 114 and the stiffener 120 is referred to as a suspended region 1121 in this specification. In some embodiments, the area of the overhanging region 1121 may be adjusted by adjusting the maximum profile of the stiffener 120, thereby adjusting the mode shape of the vibration assembly.

The fixing region 116 is disposed at the periphery of the folded ring region 114. The elastic element 110 can be secured by means of a securing region 116. For example, the elastic element 110 may be connected and fixed to a housing of a speaker or the like through the fixing region 116. In some embodiments, the fixed area 116 is mounted and fixed in the housing of the speaker and may be considered to be not involved in the vibration of the elastic element 110. In some embodiments, the fixed region 116 of the resilient element 110 may be connected to the housing of the speaker by a support element. In some embodiments, the support member may comprise a soft material that is easily deformable such that the support member may also deform when the vibration assembly 100 vibrates, thereby providing a greater amount of displacement for the vibration of the vibration assembly 100. In other embodiments, the support element may also comprise a stiff material that is not easily deformable.

In some embodiments, the elastic element 110 may further include a connection region 115 disposed between the tuck-loop region 114 and the fixation region 116. In some embodiments, the connection region 115 may provide additional stiffness and damping to the vibration of the elastic element 110, thereby adjusting the mode shape of the vibration assembly 100.

In order for the elastic member 110 to provide suitable rigidity, the thickness and elastic coefficient of the elastic member 110 may be set within a reasonable range. In some embodiments, the thickness of the elastic element 110 may range from 3um to 100um. In some embodiments, the thickness of the elastic element 110 may range from 3um to 50um. In some embodiments, the thickness of the elastic element 110 may range from 3um to 30um.

The reinforcement 120 may be an element for increasing the rigidity of the elastic element 110. In some embodiments, the stiffener 120 is coupled to the central region 112, and the stiffener 120 and/or the central region 112 is coupled to the driving portion of the speaker to transmit force and/or displacement to cause the vibration assembly 100 to push air into motion and output sound pressure. The reinforcement 120 may include one or more annular structures 122 and one or more bar structures 124, each of the one or more bar structures 124 being connected to at least one of the one or more annular structures 122 to form a staggered support in the central region 112 of the elastic element 110. Wherein at least one of the one or more bar structures 124 extends toward the center of the central region 112. In some embodiments, one or more bar structures 124 may pass through the center of the central region 112, thereby providing support to the center of the central region 112. In some embodiments, the stiffener 120 may further include a central connecting portion 123, and the one or more bar structures 124 may not pass through the center of the central region 112, but rather cover the center of the central region 112 with the central connecting portion 123, and the one or more bar structures 124 are connected with the central connecting portion 123.

The annular structure 122 may be a structure that extends around a particular 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 other locations on the central region 112 that are off-center. In some embodiments, the annular structure 122 may be a contoured line-closed structure. In some embodiments, the projected shape of the annular structure 122 along the vibration direction of the elastic element 110 may include, but is not limited to, one or more of a circular ring, a polygonal ring, a curvilinear ring, or an elliptical ring. In other embodiments, the annular structure 122 may also be a structure in which the outline is not closed. For example, the annular structure 122 may be a ring with a notch, a polygonal ring, a curvilinear ring, an elliptical ring, or the like. In some embodiments, the number of ring structures 122 may be 1. In some embodiments, the number of annular structures 122 may also be plural, and the plural annular structures may have the same centroid. In some embodiments, the number of ring structures 122 may range from 1-10. In some embodiments, the number of ring structures 122 may range from 1-5. In some embodiments, the number of ring structures 122 may range from 1-3. If the number of annular structures 122 is excessive, it may result in excessive mass of the stiffener 120, which in turn may result in reduced overall sensitivity of the vibration assembly 100. In some embodiments, the mass, stiffness adjustment of the stiffener 120 may be achieved by designing the number of annular structures 122. In some embodiments, the size of the annular structure 122 located at the outermost periphery of the stiffener 120 may be considered the largest dimension of the stiffener. In some embodiments, the size (or area) of the overhanging region 1121 between the gimbal region 114 and the stiffener 120 may be adjusted by sizing the outermost annular structure 122 to change the mode shape of the vibration assembly 100.

In some embodiments, the one or more annular structures 122 may include a first annular structure and a second annular structure, the radial dimension of the first annular structure being less than the radial dimension of the second annular structure. In some embodiments, the first annular structure is disposed inboard of the second annular structure. In some embodiments, the centroids of the first and second annular structures may coincide. In other embodiments, the centroids of the first and second annular structures may not coincide. In some embodiments, the first annular structure and the second annular structure may be connected by one or more bar structures 124. In some embodiments, the first annular structure and the second annular structure may be adjacent annular structures. In some embodiments, the first annular structure and the second annular structure may also be non-adjacent annular structures, and one or more annular structures may be disposed between the first annular structure and the second annular structure.

The bar-shaped structures 124 may be structures having a certain extension law. In some embodiments, the bar structures 124 may extend along a straight line. In some embodiments, the bar-shaped structures 124 may also extend along a curve. In some embodiments, the curvilinear extension may include, but is not limited to, an arcuate extension, a spiral extension, a spline-curved extension, a circular arc extension, an S-shaped extension, and the like. In some embodiments, the strip-shaped structure 124 is connected with the annular structure 122 to divide the reinforcement member 120 into a plurality of hollowed-out portions. In some embodiments, the region of the central region 112 corresponding to the hollowed-out portion may be referred to as a hollowed-out region. In some embodiments, the number of bar structures 124 may be 1. For example, 1 bar structure 124 may be disposed along any one of the diameters of annular structures 122 (e.g., any one of the annular structures). In some embodiments, the bar structure 124 may connect the center of the central region (i.e., the centroid of the annular structure 122) and the annular structure 122 at the same time. In some embodiments, the number of bar structures 124 may also be multiple. In some embodiments, a plurality of bar structures 124 may be disposed along a plurality of diametric directions of the annular structure 122. In some embodiments, at least a portion of the plurality of bar structures 124 may extend toward a central location of the central region 112, which may be the centroid of the elastic element 110. In some embodiments, the plurality of bar structures 124 may include another portion that extends toward other directions. In some embodiments, at least a portion of the plurality of bar 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 portion 123 may also be a separate structure, and at least a portion of the plurality of bar-shaped structures 124 may be connected to the central connection portion 123. In some embodiments, the shape of the central connection 123 may include, but is not limited to, circular, square, polygonal, oval, or the like. In some embodiments, the shape of the central connecting portion 123 may also be arbitrarily set. In some embodiments, when the number of annular structures 122 is multiple, adjacent annular structures 122 may be connected by one or more bar structures 124. In some embodiments, the bar structures 124 connected between adjacent ring structures 122 may or may not extend toward the center of the center region 112.

In some embodiments, the number of bar structures 124 may range from 1-100. In some embodiments, the number of bar structures 124 may range from 1-50. In some embodiments, the number of bar structures 124 may range from 1-50. In some embodiments, the number of bar structures 124 may range from 1-30. By providing the number of bar structures 124, the overall mass of the vibration assembly 100, the stiffness of the stiffener 120, and the area of the hollowed out area of the elastic element 110 can be adjusted to change the mode shape of the vibration assembly.

In some embodiments, the projected shape of the bar-shaped structure 124 along the vibration direction of the elastic element 110 includes at least one of a rectangle, a trapezoid, a curve, an hourglass, and a petal. By designing the bar-shaped structures 124 with different shapes, the mass distribution (such as the mass center position) of the reinforcement member 120, the rigidity of the reinforcement member 120, and the area size of the hollowed-out area can be adjusted, so that the mode shape of the vibration component can be changed.

It should be noted that the structural descriptions of the annular structure 122 and the strip-shaped structure 124 in the embodiment of the present disclosure are only optional structures selected to facilitate the reasonable arrangement of the structures of the reinforcing member 120, and should not be construed as limiting the shape of the reinforcing member 120 and its respective parts. In fact, the reinforcement member 120 in the embodiment of the present disclosure may form the reinforcement portion by the annular structure 122 and the bar-shaped structure 124 and the hollowed-out portion (i.e., hollowed-out portion corresponding to the hollowed-out area of the central area 112) between the annular structure 122 and the bar-shaped structure 124. The region of the one or more annular structures 122 and the region of the one or more bar structures 124 together form a reinforcing portion. The area of the reinforcement 120, which is not covered by the one or more ring structures 122 and the one or more strip structures 124, forms a hollow out section in the projection of the maximum contour of the reinforcement 120 in the vibration direction of the elastic element 110. The vibration characteristics (e.g., the number of resonance peaks and the frequency range) of the vibration assembly 100 can be adjusted by adjusting the parameters (e.g., the area, the thickness of the reinforcement portion, etc.) of the reinforcement portion and the hollowed-out portion. In other words, any shape of the reinforcing member having the reinforcing portion and the hollowed portion may be set using the parameter setting manners provided in the present specification regarding the reinforcing portion and the hollowed portion, for the purpose of adjusting the vibration performance (for example, the number and the position of the resonance peaks, the shape of the frequency response curve, etc.) of the vibration assembly, and these schemes should be included in the scope of the present application.

In some embodiments, referring to fig. 1, a connection region 115 between a fixing region 116 and a hinge region 114 of the elastic element 110 is suspended, and the partial region has an equivalent mass Mm ₁ And since the elastic element 110 can provide elasticity and damping, this region can be equivalently fixedly connected with the housing by the spring Km, the damping Rm, while the connection region 115 is fixedly connected with the housing by the spring Ka ₁ Damping Ra ₁ Is connected with the front air load of the elastic element 110, and transmits force and displacement to push air to move.

In some embodiments, the folded-over region 114 of the elastic element 110 has a local equivalent mass Mm ₂ And this area is passed through the spring Ka ₁ ' damping Ra ₁ ' connected to the connection region 115 of the elastic element 110, while the bellows region 114 is connected to the spring Ka ₂ Damping Ra ₂ Is connected with the front air load of the elastic element 110, and transmits force and displacement to push air to move.

In some embodiments, the central region 112 of the elastic element 110 is provided with a reinforcing member 120, the reinforcing member 120 is connected with the central region 112 of the elastic element 110, and the contact area between the reinforcing member 120 and the central region 112 is smaller than the area of the central region 112, so that a part of the suspended region 1121 is located between the region of the central region 112 of the elastic element 110 supported by the reinforcing member 120 and the folded ring region 114. The region having a local equivalent mass M m ₃ And this area is passed through the spring Ka ₂ ' damping Ra ₂ ' is connected to the bellows region 114, while the region of the reinforcement 120 is connected to the front air load of the elastic element 110 by means of a spring Ka3, a damper Ra3, and force and displacement are transmitted to thereby push air movement.

In some embodiments, due to the design of the reinforcement member 120, the central region 112 of the elastic element 110 corresponding to the reinforcement member 120 has at least one hollowed-out region, each hollowed-out region can be equivalent to a mass-spring-damper system with equivalent mass Mm _i Equivalent stiffness Ka _i And Ka _i ' equivalent damping Ra _i And (3) with Ra (Ra) _i '. The hollowed-out area is provided with a spring Ka _i ' damping Ra _i ' connect with adjacent hollowed-out areas. The hollow area is also provided with a spring Ka _i ' damping Ra _i ' connected to the suspended region 1121 between the region of the central region 112 supported by the stiffener 120 and the folded-over region 114, with the suspended region 1121 passing through the spring Ka _i Damping Ra _i Is connected with the front air load of the elastic element 110, and transmits force and displacement to push air to move.

In some embodiments, the stiffener 120 itself has an equivalent mass Mm _n And the reinforcement 120 is passed through the spring Ka _n ' damping Ra _n ' connected to the central region 112, while the reinforcement 120 is connected by a spring Ka _n Damping Ra _n And is connected with the front air load of the elastic element 110, when the reinforcing element 120 generates resonance, the central area 112 is driven to drive the elastic element 110 to generate larger movement speed and displacement, so that a larger sound pressure level is generated.

Depending on the dynamics of the mass-spring-damper systems, each mass-spring-damper system has its own resonant peak frequency f0, and a large movement speed and displacement can occur at f0, by designing different parameters of the vibration assembly 100 (e.g., structural parameters of the elastic element 110 and/or the stiffener 120), the mass-spring-damper system formed by the structures at different positions of the vibration assembly 100 can resonate at a desired frequency band, thereby providing multiple resonant peaks on the frequency response curve of the vibration assembly 100, resulting in a large expansion of the effective frequency band of the vibration assembly 100, while by designing the stiffener 120, the vibration assembly 100 can have a lighter mass, resulting in a higher sound pressure level output of the vibration assembly 100.

Fig. 2 is a first formant deformation graph of a vibration assembly according to some embodiments of the present disclosure, fig. 3 is a second formant deformation graph of a vibration assembly according to some embodiments of the present disclosure, fig. 4 is a third formant deformation graph of a vibration assembly according to some embodiments of the present disclosure, and fig. 5 is a fourth formant deformation graph of a vibration assembly according to some embodiments of the present disclosure.

According to the schematic diagram of the equivalent vibration model of the vibration assembly 100 shown in fig. 1, each part of the vibration assembly 100 generates velocity resonance in different frequency bands and outputs a larger velocity value in the corresponding frequency band, so that the frequency response curve of the vibration assembly 100 outputs a larger sound pressure value in the corresponding frequency band and has a corresponding resonance peak; at the same time, the frequency response of the vibration assembly 100 is made to have a high sensitivity in the audible range (e.g., 20Hz-20 kHz) by the plurality of resonance peaks.

Please refer to fig. 1 and fig. 2. In some embodiments, the mass of the stiffener 120, the mass of the elastic element 110, the equivalent air mass, and the equivalent mass of the drive end combine to form a total equivalent mass Mt, the partial equivalent damping forms a total equivalent damping Rt, the elastic element 110 (particularly the elastic element 110 in the region of the gimbal 114, and the suspended region between the stiffener 120) has a greater compliance, providing stiffness Kt to the system, thus forming a mass Mt-spring Kt-damped Rt system having a resonant frequency that resonates when the drive end excitation frequency approaches the system's velocity resonant frequency (as shown in FIG. 2) and outputs a greater velocity value v in a frequency band near the velocity resonant frequency of the Mt-Kt-Rt system _a Since the vibration assembly 100 outputs a positive correlation of the sound pressure amplitude and the sound velocity (p _a ∝v _a ) Thus, a resonance peak appears in the frequency response curve, which is defined herein as the first resonance peak of the vibration assembly 100. In some embodiments, referring to FIG. 2, FIG. 2 showsThe vibration of the vibration assembly 100 is illustrated at the A-A cross-sectional position, with the white structure in fig. 2 showing the shape and position of the stiffening member 120 prior to deformation and the black structure showing the shape and position of the stiffening member 120 at the first resonance peak. It should be noted that fig. 2 only shows the structural case of the vibration assembly 100 from the center of the reinforcing member 120 to one side edge of the elastic member 110 in the A-A section, that is, half of the A-A section, and the other half of the A-A section, which is not shown, is symmetrical to the case shown in fig. 2. As can be seen from the vibration of the vibration assembly 100 at the A-A section, the main deformation of the vibration assembly 100 is the portion of the elastic element 110 that is connected to the fixing region 116 at the position of the first resonance peak. In some embodiments, the frequency of the first resonant peak of the vibration assembly 100 (also referred to as the first resonant frequency) may be related to the ratio of the mass of the vibration assembly 100 and the elastic coefficient of the elastic element 110. In some embodiments, the frequency range of the first resonant peak includes 180Hz-3000Hz. In some embodiments, the frequency range of the first resonant peak includes 200Hz-3000Hz. In some embodiments, the frequency range of the first resonant peak includes 200Hz-2500Hz. In some embodiments, the frequency range of the first resonant peak includes 200Hz-2000Hz. In some embodiments, the frequency range of the first resonant peak includes 200Hz-1000Hz. In some embodiments, the first resonance peak of the vibration assembly 100 may be located within the above-described frequency range by providing the structure of the reinforcement member 120.

Please refer to fig. 1 and 3. The connection region 115 between the fixed region 116 and the folded-over region 114 of the elastic element 110 is in a floating state, and the partial region has an equivalent mass Mm ₁ And this region is fixedly connected to the housing by means of a spring Km, a damping Rm, while the connection region 115 is connected by means of a spring Ka ₁ Damping Ra ₁ Is connected with the front air load of the elastic element 110, and transmits force and displacement to push air to move.

The folded-over region 114 has a locally equivalent mass Mm ₂ And this area is passed through the spring Ka ₁ ' damping Ra ₁ ' connect with the connection area 115 while the folded-over area 114 is connected by the spring Ka ₂ Damping Ra ₂ Is connected with the front air load of the elastic element 110 to transmit force and displacement to push the airMovement of qi.

A suspended region 1121 is provided between the region of the central region 112 where the stiffener 120 is provided and the tuck-ring region 114. Suspended region 1121 has a local equivalent mass Mm ₃ And this area is passed through the spring Ka ₂ ' damping Ra ₂ ' is connected to the bellows region 114, while the region of the reinforcement 120 is connected to the front air load of the elastic element 110 by means of a spring Ka3, a damper Ra3, and force and displacement are transmitted to thereby push air movement.

The above 3 parts can form equivalent mass Ms, equivalent stiffness Ks and equivalent damping Rs to form a mass Ms-spring Ks-damping Rs system, further, the system has a resonant frequency, when the driving end excitation frequency is close to the speed resonant frequency of the Ms-Ks-Rs system, the system generates resonance, and a larger speed value v is output in a frequency band near the speed resonant frequency of the Ms-Ks-Rs system _a Since the vibration assembly 100 outputs a positive correlation of the sound pressure amplitude and the sound velocity (p _a ∝v _a ) Thus, one resonance peak appears in the frequency response curve, which is defined herein as the second resonance peak of the vibration assembly 100. The resonance peak is mainly generated by vibration modes of the connection region 115, the folded ring region 114, the region where the reinforcing member 120 is provided in the central region 112, and the suspended region between the folded ring region 114, see fig. 3, and fig. 3 shows deformation positions of the vibration assembly 100 before the second resonance peak (the upper structural diagram in fig. 3) and after the second resonance peak (the lower structural diagram in fig. 3), respectively. In some embodiments, referring to FIG. 3, as can be seen from the vibration of the vibration assembly 100 at the A-A cross-sectional location, the primary deformation locations of the vibration assembly 100 are the gimbal region 114 and the flying region 1121, before and after the frequency of the second resonant peak. In some embodiments, the frequency of the second resonance peak of the vibration assembly 100 (also referred to as the second resonance frequency) may be related to the ratio of the mass of the elastic element 110 to the elastic coefficient of the elastic element 110. In some embodiments, the frequency range of the second resonant peak of vibration assembly 100 may include 1000Hz-10000Hz. In some embodiments, the frequency range of the second resonant peak of vibration assembly 100 may include 3000Hz-7000Hz. In some embodiments, the frequency range of the second resonant peak of the vibration assembly 100 may be To include 3000Hz-6000Hz. In some embodiments, the frequency range of the second resonant peak of vibration assembly 100 may include 4000Hz-6000Hz. In some embodiments, the second resonance peak of the vibration assembly 100 may be in the above frequency range by providing the structure of the reinforcement member 120.

Please refer to fig. 1 and fig. 4. The reinforcement 120 itself has an equivalent mass Mm _n And the reinforcement 120 is passed through the spring Ka _n ' damping Ra _n ' connected to the central region 112, while the reinforcement 120 is connected by a spring Ka _n Damping Ra _n And is connected with the front air load of the elastic element 110, when the reinforcing element 120 generates resonance, the central area 112 is driven to drive the elastic element 110 to generate larger movement speed and displacement, so that a larger sound pressure level is generated.

The reinforcement 120, the connection region 115, the folded ring region 114, the suspended region 1121 between the region of the central region 112 where the reinforcement 120 is arranged and the folded ring region 114, the equivalent air mass, and the equivalent driving end mass are combined to form the total equivalent mass Mt ₁ The equivalent damping of each part forms the total equivalent damping Rt ₁ The stiffener 120, the elastic element 110 (particularly the region of the central region 112 covered by the stiffener 120) has a greater stiffness, providing the stiffness Kt to the system ₁ Thus forming a mass Mt ₁ Spring Kt ₁ Damping Rt ₁ The system has one ring area in the diameter direction of the central area 112 as equivalent fixed fulcrum, and the ring area moves in the opposite direction to the outside of the ring area to form the vibration mode of turning motion, and the connection area 115, the folded ring area 114, the area of the central area 112 with the reinforcing member 120 and the suspended area 1121 between the folded ring area 114 vibrate under the driving of the reinforcing member 120 to realize one resonance mode with turning motion as vibration mode (as shown in fig. 4), and the resonance is also equivalent mass Mt ₁ Spring Kt ₁ Damping Rt ₁ A resonance frequency point of the system, when the drive end excitation frequency is close to the speed resonance frequency of the system, the Mt ₁ -Kt ₁ -Rt ₁ The system resonates and at Mt ₁ -Kt ₁ -Rt ₁ Speed of the systemThe frequency band near the resonance frequency outputs a larger velocity value v _a Since the vibration assembly 100 outputs a positive correlation of the sound pressure amplitude and the sound velocity (p _a ∝v _a ) Thus, a resonance peak appears in the frequency response curve, which is defined herein as the third resonance peak of the vibration assembly 100. In some embodiments, referring to fig. 4, fig. 4 shows the deformation positions of the vibration assembly 100 before the third resonance peak (the upper structural diagram in fig. 4) and after the third resonance peak (the lower structural diagram in fig. 4), respectively, and as can be seen from the vibration condition of the vibration assembly 100 at the A-A section position, the main deformation position of the vibration assembly 100 is the overturning deformation of the reinforcing member 120 before and after the frequency of the third resonance peak (also referred to as the third resonance frequency). In some embodiments, the third resonance peak of the vibration assembly 100 may be related to the stiffness of the stiffener 120. In some embodiments, the frequency range of the third resonance peak may include 5000Hz-12000Hz. In some embodiments, the frequency range of the third resonance peak may include 6000Hz-12000Hz. In some embodiments, the frequency range of the third resonance peak may include 6000Hz-10000Hz. In some embodiments, the third resonance peak of the vibration assembly 100 may be in the above frequency range by providing the structure of the reinforcement member 120.

Please refer to fig. 1 and fig. 5. The stiffener 120 has at least one hollow area corresponding to the central area 112, each hollow area being a mass-spring-damper system having an equivalent mass Mm _i Equivalent stiffness Ka _i And Ka _i ' equivalent damping Ra _i And (3) with Ra (Ra) _i '. The hollowed-out area is provided with a spring Ka _i ' damping Ra _i ' connect with adjacent hollow area, and the hollow area passes through spring Ka _i ' damping Ra _i ' connected to the suspended region 1121 between the region of the central region 112 supported by the stiffener 120 and the folded-over region 114 and at the same time the hollowed-out region is spring Ka _i Damping Ra _i Is connected with the front air load of the elastic element 110, and transmits force and displacement to push air to move.

Because the hollow areas are separated by the strip-shaped structures 124 of the reinforcing piece 120, the hollow areas can form different resonant frequencies and independently push the air domains connected with the hollow areas to move so as to generate corresponding sound pressure; further, by designing the position, size, and number of each bar-shaped structure 124 of the reinforcement member 120, each hollowed-out area having different resonance frequencies can be realized, so that there are not less than 1 high-frequency resonance peak (i.e., fourth resonance peak) on the frequency response curve of the vibration assembly 100. In some embodiments, the range of not less than 1 high frequency resonance peak (i.e., fourth resonance peak) as described above may include 10000Hz to 18000Hz.

Further, in order to raise the sound pressure level of the vibration assembly 100 output at high frequency (10000 Hz-20000 Hz), the positions, sizes and numbers of the bar structures 124 are designed so that the resonance frequencies of the hollow areas are equal or close. In some embodiments, the resonance frequency difference of each hollowed-out area is within 4000Hz, so that there is a high-frequency resonance peak with a larger output sound pressure level on the frequency response curve of the vibration assembly 100, which is defined as the fourth resonance peak of the vibration assembly 100 (as shown in fig. 5). In some embodiments, referring to fig. 5, it can be seen from the vibration condition of the vibration assembly 100 at the B-B section position that, near the frequency of the fourth resonance peak (also referred to as the fourth resonance frequency), the main deformation position of the vibration assembly 100 is the deformation generated by the hollowed-out area of the central area 112. In some embodiments, the frequency range of the fourth resonance peak may include 8000Hz-20000Hz. In some embodiments, the frequency range of the fourth resonance peak may include 10000Hz-18000Hz. In some embodiments, the frequency range of the fourth resonance peak may include 12000Hz-18000Hz. In some embodiments, the frequency range of the fourth resonance peak may include 15000Hz-18000Hz. In some embodiments, by designing the area of one or more hollowed-out regions and the thickness of the elastic element 110, the resonance frequency of each hollowed-out region can be adjusted, so that the fourth resonance peak of the vibration assembly 100 is located in the above frequency range. In some embodiments, in order to make the range of the fourth resonance peak of the vibration assembly 100 within the above frequency range, the ratio of the area of each hollowed-out area to the thickness of the elastic element 110 ranges from 100mm to 1000mm. In some embodiments, in order to make the range of the fourth resonance peak of the vibration assembly 100 within the above frequency range, the ratio of the area of each hollowed-out area to the thickness of the elastic element 110 ranges from 120mm to 900mm. In some embodiments, in order to make the range of the fourth resonance peak of the vibration assembly 100 within the above frequency range, the ratio of the area of each hollowed-out area to the thickness of the elastic element 110 ranges from 150mm to 800mm. In some embodiments, in order to make the range of the fourth resonance peak of the vibration assembly 100 within the above frequency range, the ratio of the area of each hollowed-out area to the thickness of the elastic element 110 ranges from 150mm to 700mm.

Referring to fig. 6, fig. 6 is a graph of frequency response of a vibration assembly 100 having different third and fourth resonant frequency differences according to some embodiments of the present disclosure, wherein the abscissa indicates frequency (in Hz) and the ordinate indicates Sensitivity (SPL). By designing the structures of the reinforcement member 120 and the elastic element 110, it is possible to realize the vibration assembly 100 having a plurality of resonance peaks in the audible sound range, and further, by combining the plurality of resonance peaks, etc., the vibration assembly 100 has a higher sensitivity in the entire audible sound range. By designing the bar-shaped structure 124 and the ring-shaped structure 122 of the stiffener 120, it is achieved that the fourth resonance peak 240 of the vibration assembly 100 is located in a different frequency range. By designing the frequency difference Δf between the fourth resonance peak 240 and the third resonance peak 230, a relatively flat frequency response curve and a relatively high sound pressure level can be output between the fourth resonance peak 240 and the third resonance peak 230 in the frequency band, so as to avoid the occurrence of a valley in the frequency response curve. As shown in fig. 6, an excessively large frequency difference Δf between the fourth and third resonance peaks 240 and 230 (Δf2 as shown in fig. 6) may cause a low valley in the frequency band between the fourth and third resonance peaks 240 and 230 and a decrease in the output sound pressure level, and an excessively small frequency difference Δf between the fourth and third resonance peaks 240 and 230 (Δf1 as shown in fig. 6) may cause a decrease in the frequency of the fourth resonance peak 240 and a decrease in the sound pressure level in the high frequency band (e.g., 12kHz-20 kHz), thereby narrowing the frequency band of the vibration assembly 100. By adjusting the structures of the reinforcement 120 and the elastic element 110, the third resonance peak 230 may be shifted left and/or the fourth resonance peak 240 may be shifted right, thereby increasing the frequency difference Δf between the fourth resonance peak 240 and the third resonance peak 230. In some embodiments, the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230 ranges from 80Hz to 15000Hz. In some embodiments, the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230 ranges from 100Hz to 13000Hz. In some embodiments, the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230 ranges from 200Hz to 12000Hz. In some embodiments, the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230 ranges from 300Hz to 11000Hz. In some embodiments, the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230 is in the range of 400Hz-10000Hz. In some embodiments, the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230 ranges from 500Hz to 9000Hz. In some embodiments, the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230 ranges from 200Hz to 11000Hz. In some embodiments, the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230 is in the range of 200Hz-10000Hz. In some embodiments, the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230 ranges from 2000Hz to 15000Hz. In some embodiments, the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230 ranges from 3000Hz to 14000Hz. In some embodiments, the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230 ranges from 4000Hz to 13000Hz.

Referring to fig. 7A, by designing the reinforcement member 120 and the elastic element 110, a required high-order mode of the vibration assembly 100 can be generated in the audible range of the human ear (20 Hz-20000 Hz), and the first resonant peak 210, the second resonant peak 220, the third resonant peak 230 and the fourth resonant peak 240 appear on the frequency response curve of the vibration assembly 100, that is, the number of resonant peaks of the frequency response curve of the vibration assembly 100 in the frequency range of 20Hz-20000Hz is 4, so that the vibration assembly 100 has a higher sensitivity in a wider frequency band range.

In some embodiments, by designing the structure of the stiffener 120 and the elastic element 110, the vibration assembly 100 may have only 3 resonance peaks in the audible sound range (20 Hz-20000 Hz). For example, when the frequency difference between the second resonance peak and the third resonance peak of the vibration assembly 100 is less than 2000Hz, the second resonance peak and the third resonance peak are embodied as one resonance peak on the sound pressure level curve of the frequency response of the vibration assembly 100. For another example, the reinforcing member 120 has at least one suspended area corresponding to the central area 112, and when the resonance frequency of each hollow area is higher than the audible sound range, or the resonance frequencies of the hollow areas are different, and the vibration phases of the suspended areas in different frequency ranges of the high-frequency range (10000 Hz-18000 Hz) are different, so as to form the effect of cancellation of the superposition of sound, an effect of high-frequency roll-off can be obtained, and the fourth resonance peak is not reflected in the sound pressure level frequency response curve of the vibration assembly 100.

Referring to fig. 7B, fig. 7B is a schematic diagram illustrating overlapping second and third resonance peaks according to some embodiments of the present disclosure. In some embodiments, the frequency difference between the second resonant peak 220 and the third resonant peak 230 of the vibration component 100 can be designed by designing the structure and the size of the stiffener 120, including the overall size of the stiffener 120, the number and size of the bars 124, the arrangement position of the bars 124, the area of the suspended area 1121 between the area of the center area 112 where the stiffener 120 is disposed and the folded-over area 114, the pattern design of the folded-over area 114 (e.g., the width, the height, the arch of the folded-over), and the area of the connection area 115. In some embodiments, when the frequency difference between the second resonant peak 220 and the third resonant peak 230 of the vibration assembly 100 is in the range of 2000Hz-3000Hz, there is no valley between the second resonant peak 220 and the third resonant peak 230 on the frequency-response sound pressure level curve (such as the frequency-response curve 710) of the vibration assembly 100, and the second resonant peak 220 and the third resonant peak 230 can still be distinguished on the frequency-response curve (corresponding to the dashed line in the figure). In some embodiments, when the frequency difference between the second resonant peak 220 and the third resonant peak 230 of the vibration assembly 100 is further reduced, for example, less than 2000Hz, the second resonant peak 220 and the third resonant peak 230 are embodied as one resonant peak (corresponding to the solid line in the figure) on the frequency response sound pressure level curve (such as the frequency response curve 720) of the vibration assembly 100, so that the middle-high frequency band (3000 Hz-10000 Hz) has higher sensitivity.

The annular structure 122 and the strip-shaped structures 124 of the reinforcement 120 are designed, so that the reinforcement 120 has at least one hollow area corresponding to the central area 112, each hollow area is a mass-spring-damping system, and the positions, the sizes and the number of the strip-shaped structures 124 of the reinforcement 120 are designed, so that the resonance frequencies of the hollow areas are equal or close. In some embodiments, the resonance frequency difference of each hollowed-out area is within 4000Hz, so that there may be one or more high-frequency resonance peaks (i.e., a fourth resonance peak) with a larger output sound pressure level on the frequency response curve of the vibration assembly 100.

In some embodiments, referring to fig. 7C, by designing the position, size, and number of each bar-shaped structure 124 of the stiffener 120 so that the resonant frequency of each hollow area is higher than the audible sound range, or so that the resonant frequencies of each hollow area are different, and the vibration phases of different hollow areas in different frequency ranges of the high frequency range (10000 Hz-18000 Hz) are different, an effect of sound superposition cancellation is formed, an effect of high-frequency roll-off can be obtained, and a fourth resonance peak is not reflected in the sound pressure level frequency response curve of the vibration assembly 100.

Referring to fig. 7D, fig. 7D is a schematic diagram illustrating a frequency response curve of the vibration assembly 100 having two resonance peaks according to some embodiments of the present disclosure. In some embodiments, by designing the structure of the reinforcement member 120, when the frequency difference between the second resonant peak 220 and the third resonant peak 230 of the vibration assembly 100 is less than 2000Hz, the second resonant peak 220 and the third resonant peak 230 are embodied as one resonant peak on the frequency-ringing voltage level curve of the vibration assembly 100. On the other hand, by designing the positions, sizes and numbers of the bar structures 124 of the reinforcement 120, the resonance frequency of each hollow area is higher than the audible sound range, or the resonance frequency of each hollow area is different, and the vibration phases of different hollow areas in different frequency ranges of the high-frequency range (10000 Hz-18000 Hz) are different, so that the effect of sound superposition cancellation is formed, the effect of high-frequency roll-off can be obtained, and the fourth resonance peak is not reflected in the sound pressure level frequency response curve of the vibration assembly 100. At this time, the vibration assembly 100 has an output characteristic of a certain bandwidth and a high sensitivity in a middle-high frequency band (3000 Hz to 10000 Hz).

In some embodiments, the area and thickness of the suspended region 1121 and the folded-ring region 114 of the elastic element 110 can be designed to ensure that the second resonance peak of the vibration component 100 is within a desired frequency range. In some embodiments, the second resonance peak of vibration assembly 100 may range from 1000Hz to 10000Hz. In some embodiments, the second resonance peak of vibration assembly 100 may range from 3000Hz to 7000Hz. In some embodiments, when designing the frequency difference between the second and third resonant peaks of vibration assembly 100, the frequency difference between the second and third resonant peaks of vibration assembly 100 is less than 3000Hz.

Referring to fig. 8A, fig. 8A is a schematic structural view of a vibration assembly having a stiffener with a single ring structure according to some embodiments of the present description. In some embodiments, a horizontal plane projection area of the suspension region 1121 (i.e., a projection area of the suspension region 1121 along the vibration direction of the elastic element 110) is defined as S _v The projected area of the horizontal plane of the hinge region 114 (i.e., the projected area of the hinge region 114 along the vibration direction of the elastic element 110) is S _e Suspended area 1121 horizontal projection area S _v Projected area S in horizontal plane with the annular region 114 _e The sum is S _s . Define the physical quantity α (in mm) as S _s Ratio to thickness Hi of the elastic element 110 (also called diaphragm):

in some embodiments, to provide the second resonant peak of vibration assembly 100 with a frequency range of 3000 Hz-70000 Hz, S _s And the thickness H of the vibrating diaphragm _i The value of the ratio alpha of (a) can be in the range of 5000mm-12000mm. In some embodiments, to have the frequency range of the second resonant peak of vibration assembly 100 between 3000Hz and 7000Hz, α is in the range of 6000mm to 10000mm. In some embodiments, to further tune the frequency range of the second resonant peak of vibration assembly 100 to shift to high frequencies, alpha may range from 6000mm to 9000mm. In some embodiments, to further tune the frequency range of the second resonant peak of vibration assembly 100 to shift to high frequencies, α may range from 6000mm to 8000mm. In some embodiments, to further tune the frequency range of the second resonance peak of the vibration assembly 100 to shift to high frequencies, the value of α may range from 6000mm to 7000mm.

In some embodimentsIn this case, the relationship between the areas of the suspended region 1121 and the folded-ring region 114 and the thickness of the elastic element 110 affects the local equivalent mass Mm ₃ Equivalent to local equivalent mass Mm ₂ Local area stiffness Ka ₂ ' and local area stiffness Ka ₁ ' and further affects the equivalent mass Ms, equivalent stiffness Ks, and equivalent damping Rs formed by the connection region 115, the folded ring region 114, and the suspended region 1121, thereby controlling the range of the second resonance peak of the vibration assembly 100. In some embodiments, control of the second resonance peak of vibration assembly 100 may also be achieved by the high camber design of the bellows of bellows region 114.

Fig. 8B is a schematic diagram of a frequency response curve of a vibration assembly according to other embodiments of the present disclosure. In some embodiments, as shown in fig. 8B, the frequency response curve 810 in the figure represents the frequency response curve of the vibrating assembly when α=8190mm; frequency response curve 820 represents the frequency response curve of the vibrating assembly when α=7146 mm; frequency response curve 830 represents the frequency response curve of the vibrating assembly when α=12360 mm. As can be seen from the frequency response curve 820, the second resonance peak 220 of the vibration assembly 100 has a frequency of about 7000Hz at α=7146 mm. As can be seen from the frequency response curve 810, the second resonant peak 220 frequency of the vibration assembly 100 is approximately 5000Hz at α=8190mm; and the amplitude of the second formant 220 of the frequency response curve 810 is similar to the amplitude of the second formant 220 of the frequency response curve 820. That is, as α increases, the resonant frequency of the second resonant peak 220 decreases, and the amplitude remains substantially unchanged. As can be seen from the frequency response curve 820, when α=12360 mm, the vibration assembly 100 has no distinct second resonance peak, and the amplitude of the vibration assembly 100 in the range of 3000Hz-7000Hz is reduced compared to the frequency response curve 810 and the frequency response curve 820, that is, when α=12360 mm, the output sound pressure level of the vibration assembly 100 is lower. Therefore, when the value of α ranges from 6000mm to 10000mm, the frequency range of the second resonance peak of the vibration assembly 100 can be better controlled to 3000Hz to 7000Hz, so that the vibration assembly 100 has a higher output sound pressure level in the range of 3000Hz to 7000Hz.

Referring to fig. 9A, fig. 9A is a schematic partial structure of a vibration assembly according to some embodiments of the present disclosure. In the present specification, the ring arch height Δh of the ring region 114 may be defined, and the object is definedThe quantity delta (unit is mm) is S _s Ratio of arch height to diaphragm ring is deltah:

in some embodiments, delta may range from 50mm to 600mm. In some embodiments, delta may range from 100mm to 500mm. In some embodiments, delta may range from 200mm to 400mm in order for the second resonant peak of vibration assembly 100 to have a frequency range of 3000Hz to 7000 Hz. In some embodiments, delta may be in the range of 300mm-400mm in order to further shift the frequency range of the second resonant peak of vibration assembly 100 to a low frequency within the range of 3000Hz-7000 Hz. In some embodiments, delta may be in the range of 350mm-400mm in order to further shift the frequency range of the second resonant peak of vibration assembly 100 to a low frequency within the range of 3000Hz-7000 Hz. In some embodiments, delta may be in the range of 200mm-300mm in order to shift the frequency range of the second resonant peak of vibration assembly 100 to high frequencies within the range of 3000Hz-7000 Hz. In some embodiments, delta may be in the range of 200mm-250mm in order to further shift the frequency range of the second resonant peak of vibration assembly 100 to high frequencies within the range of 3000Hz-7000 Hz.

In some embodiments, by designing the camber of the folded ring, the three-dimensional size of the folded ring region 114 can be changed under the condition that the horizontal projection area of the folded ring region 114 and the suspended region 1121 is unchanged, thereby changing the rigidity Ka of the folded ring region 114 ₁ ' and further control of the second resonance peak of the loudspeaker. In some embodiments, the output sound pressure level of the speaker may also be regulated by co-ordinating the dimensions of the stiffening portion.

Fig. 9B is a schematic diagram of a frequency response curve of a vibration assembly according to other embodiments of the present disclosure. In some embodiments, as shown in fig. 9B, the frequency response curve 910 in the figure represents the frequency response curve of the vibrating assembly when δ=262 mm; the frequency response curve 920 represents the frequency response curve of the vibrating assembly when δ=197 mm. As can be seen from the frequency response curve 910, when δ=262 mm, the second resonance peak 220 frequency of the vibration assembly 100 is about 5000Hz; as can be seen from the frequency response curve 920, when δ=197 mm, the second resonance peak 220 of the vibration assembly 100 has a frequency of about 7000Hz. Therefore, as δ increases, the resonance frequency of the second resonance peak 220 decreases, and when δ ranges from 200mm to 400mm, the frequency range of the second resonance peak of the vibration assembly 100 can be well controlled to 3000Hz to 7000Hz.

In the present specification, the horizontal projection area of the center region 112 is defined as S _c Maximum profile horizontal projection area S of stiffener 120 _rm The horizontal plane projection area of the suspended area 1121 is S _v Wherein: s is S _rm ＝S _c -S _v 。

In the present specification, a physical quantity is defined(unit is 1) is the projected area S of the horizontal plane of the suspended region 1121 _v Horizontal projected area S with central region 112 _c Ratio of (3):

in some embodiments of the present invention, in some embodiments,the value range is 0.05-0.7. In some embodiments, ->The value range is 0.1-0.5. In some embodiments, in order to make the frequency range of the second resonance peak of the vibration assembly 100 3000Hz-7000Hz, -, a second resonance peak is located at the same frequency as the first resonance peak>The value range is 0.15-0.35. In some embodiments, to further shift the second resonance peak of the vibration assembly 100 towards high frequencies within the frequency range 3000Hz-7000Hz, +.>The value range is 0.15-0.25. In some embodiments, ->The value range is 0.15-0.2. In some embodiments, to further shift the second resonance peak of the vibration assembly 100 towards low frequencies in the frequency range 3000Hz-7000Hz, +.>The value range is 0.25-0.35. In some embodiments, to further shift the second resonance peak of the vibration assembly 100 towards low frequencies in the frequency range 3000Hz-7000Hz, +. >The value range is 0.3-0.35.

In some embodiments, when the vibration component deforms near the frequency corresponding to the second resonance peak, the suspended region 1121 and the folded ring region 114 generate local resonance, and at this time, by designing the size of the reinforcement member 120 (i.e. the maximum outline size of the reinforcement member 120), the reinforcement member 120 can realize certain bending deformation in the frequency band, so that the sound pressure superposition of different regions of the diaphragm is increased, and thus, the output of the vibration component or the speaker at the maximum sound pressure level of the second resonance peak is realized.

Fig. 9C is a schematic diagram of a frequency response curve of a vibration assembly according to other embodiments of the present disclosure. In some embodiments, as shown in FIG. 9C, the plot 940 represents whenA frequency response curve of the vibration assembly; frequency response curve 950 indicates when->A frequency response curve of the vibration assembly. From the frequency response curve 940, the +.>At the time, the vibration groupThe second resonant peak 220 frequency of member 100 is 4000Hz; from the frequency response curve 950, the +.>When the second resonant peak 220 frequency of the vibration assembly 100 is about 6000Hz. Thus, with->The resonance frequency of the second resonance peak 220 increases and when +.>When the value range is 0.15-0.35, the frequency range of the second resonance peak of the vibration assembly 100 can be well controlled to be 3000-7000 Hz.

In some embodiments, the bar-shaped structures 124 may have different widths, shapes and numbers to change the hollowed-out area (corresponding to the suspended area of the central area 112) of the stiffener 120, so as to adjust the frequency response of the speaker. For details, refer to fig. 13A-18C and the related description.

In some embodiments, the resonant frequency of the vibration assembly 100 can be adjusted by designing the area of the hollowed-out area (e.g., designing the number and position of the bar-shaped structures 124, the number and position of the ring-shaped structures 122, etc. of the reinforcement members 120), so as to improve the service performance of the vibration assembly 100. In some embodiments, the fourth resonance peak of the vibration assembly 100 may range from 8000Hz to 20000Hz. In some embodiments, the fourth resonance peak of the vibration assembly 100 may range from 10000Hz to 18000Hz.

Referring to fig. 6 and 10A, fig. 10A is a deformation diagram of a C-C section of a vibration assembly having a stiffener with a single ring structure around a fourth resonant peak frequency according to some embodiments of the present disclosure. As can be seen from fig. 6, the frequency difference Δf between the fourth resonance peak 240 and the third resonance peak 230 has a large influence on the flatness of the high-frequency band response curve of the vibration assembly 100. In some embodiments, referring to FIG. 10A, it can be seen that the vibration of the vibration assembly 100 at the C-C cross-sectional location is near the frequency of the fourth harmonic peak, the vibration assembly 100 The main deformation position is the deformation generated in the hollowed-out area of the central area 112. In some embodiments, the corresponding equivalent mass Mm can be achieved by controlling each hollowed-out area of the stiffener 120 corresponding to the central area 112 to be a mass-spring-damper system _i Equivalent stiffness Ka _i To achieve control of the fourth harmonic peak 240 of the vibration assembly 100. For example, the number and size of the bar structures 124 and the area of each hollowed-out area of the central area 112 can be designed by the annular structure 122, and the area of each hollowed-out area is defined as S _i . It should be noted that, although fig. 10A shows a fourth resonance peak deformation diagram of the vibration assembly 100 having the stiffener 120 with the single ring structure, the conclusion is still applicable to the vibration assembly having the stiffener 120 with the multi-ring structure (the vibration assembly 100 shown in fig. 5).

In order to make the fourth resonance peak in the appropriate frequency range (10000 Hz-18000 Hz), the present specification defines a physical quantity: any one of the hollow areas (i.e. the projection area of the hollow portion along the vibration direction of the elastic element 110) S _i And the thickness H of the diaphragm (such as the elastic element 110) of each hollowed-out area _i The ratio is the area thickness ratio mu (in mm):

in some embodiments, when the young's modulus and density of the diaphragm (e.g., the elastic element 110) are within a predetermined range, the frequency position of the fourth resonance peak of the vibration component can be adjusted by designing the magnitude of the μ value. In some embodiments, the predetermined range of Young's modulus of the diaphragm is 5 x 10≡8Pa-1 x 10≡10Pa. In some embodiments, the predetermined range of Young's modulus of the diaphragm is 1 x 10 Pa-5 x 10Pa 9Pa. In some embodiments, the predetermined range of diaphragm density is 1 x 10≡3kg/m3-4 x 10≡3kg/m3. In some embodiments, the predetermined range of diaphragm density is 1 x 10≡3kg/m3-2 x 10≡3kg/m3.

In some embodiments, the area to thickness ratio μ ranges from 1000mm to 10000mm. In some embodiments, the area to thickness ratio μ ranges from 1500mm to 9000mm. In some embodiments, the area to thickness ratio μ ranges from 2000mm to 8000mm. In some embodiments, the area to thickness ratio μ ranges from 2500mm to 7500mm. In some embodiments, the area to thickness ratio μ ranges from 3000mm to 7000mm. In some embodiments, the area to thickness ratio μ ranges from 3500mm to 6500mm. In some embodiments, the area to thickness ratio μ ranges from 4000mm to 6000mm.

In some embodiments, the equivalent mass Mm of each hollowed-out region can be controlled by designing the area of each hollowed-out region and the thickness of the vibrating diaphragm _i Equivalent stiffness Ka _i And further realizing the control of the fourth resonance peak of the loudspeaker.

Fig. 10B is a schematic diagram of a frequency response curve of a vibration assembly according to other embodiments of the present disclosure. In some embodiments, as shown in fig. 10B, the frequency response curve 1010 in the figure represents the frequency response curve of the vibrating assembly when μ=5230mm; frequency response curve 1020 represents the frequency response curve of the vibrating assembly when μ=4870 mm; frequency response curve 1030 represents the frequency response curve of the vibrating assembly when μ=5330 mm; frequency response curve 1040 represents the frequency response curve of the vibrating assembly when μ=5440 mm. As shown in fig. 10B, the fourth resonance peak frequency of the frequency response curve 1010 corresponding to μ=5230mm is about 15000Hz, the fourth resonance peak frequency of the frequency response curve 1020 corresponding to μ=4870 mm is about 12000Hz, the fourth resonance peak frequency of the frequency response curve 1030 corresponding to μ=5330 mm is about 16000Hz, and the fourth resonance peak frequency of the frequency response curve 1040 corresponding to μ=5440 mm is about 17000Hz. Therefore, when μ ranges from 4000mm to 6000mm, the frequency range of the fourth resonance peak of the vibration assembly 100 can be well controlled from 10000Hz to 18000Hz.

As shown in fig. 11, in some embodiments, the stiffener 120 has a multi-annular structure (e.g., a double annular structure), i.e., the stiffener 120 includes a plurality of radially adjacently disposed annular structures (e.g., a first annular structure, a second annular structure, etc.), each annular structure having a different diameter, the smaller diameter annular structure being disposed inside the larger diameter annular structure. The present disclosure defines that the area of each hollowed-out area of the elastic element 110 in the first annular structure is S _1i When the first annular structure and the second annular structure are adjacent annular structures, the first annular structure and the second annular structureThe area of each hollow area of the elastic element 110 is S _2i . In other embodiments, the reinforcement member 120 may further have more ring-shaped structures 122, and the area of each hollow region of the elastic element 110 between the n-1 ring and the n-th ring is defined as S _ni . The hollowed-out areas between the annular structures with different diameters can comprise a first hollowed-out area and a second hollowed-out area, and the distance between the centroid of the first hollowed-out area and the center of the center area is different from the distance between the centroid of the second hollowed-out area and the center of the center area. The present specification defines the hollowed-out area ratio γ (unit is 1) of the physical quantity elastic element 110 as the first hollowed-out area S _ki And the second hollowed-out area S _ji Ratio of:

where k > j. The frequency position of the fourth resonance peak of the vibration component and the output sound pressure level can be adjusted by designing the gamma value.

As shown in fig. 11 and 12A, fig. 12A is a frequency response curve of the vibration module corresponding to fig. 11. In the first to fourth structures, the area of each hollowed-out area between the first and second annular areas is S _2i The area of each hollowed-out area in the first annular area is S _1i The area ratio gamma of the second hollow area is 5.9, 4.7, 3.9 and 3.2 in sequence. As can be seen from fig. 11, in the fourth resonance peak position of the vibration assembly 100, from structure one to structure four, the radius Δr of the first hollowed-out area inside the annular structure 122 is smaller along with the decrease of γ ₁ Gradually increasing the radius DeltaR of the second hollowed-out area between the inner annular structure 122 and the outer annular structure 122 ₂ Gradually decreasing. In some embodiments, with further reference to fig. 12A, the sound pressure amplitude output of the frequency response curves of the vibration components of structures one through four at the fourth resonance peak position increases gradually. Therefore, the ratio of the areas of the hollow areas of the central area 112 affects the resonance frequency of each hollow area, and finally the effect of superposition of sound pressure in the high frequency band is obtained, namely the communication By setting the magnitude of γ, the high frequency sensitivity of the vibration assembly 100 can be adjusted.

In some embodiments, the ratio of the areas of the central region 112 to the areas of the first and second hollow regions S is as small as possible _ki And S is equal to _ji The ratio gamma is in the range of 0.1-10. In some embodiments, the first hollowed-out area and the second hollowed-out area are _ki And S is equal to _ji The ratio gamma is in the range of 0.16-6. In some embodiments, the first hollowed-out area and the second hollowed-out area are _ki And S is equal to _ji The ratio gamma is in the range of 0.2-5. In some embodiments, the first hollowed-out area and the second hollowed-out area are _ki And S is equal to _ji The ratio gamma is in the range of 0.25-4. In some embodiments, the first hollowed-out area and the second hollowed-out area are _ki And S is equal to _ji The ratio gamma is in the range of 0.25-1. In some embodiments, the first hollowed-out area and the second hollowed-out area are _ki And S is equal to _ji The ratio gamma is in the range of 0.25-0.6. In some embodiments, the first hollowed-out area and the second hollowed-out area are _ki And S is equal to _ji The ratio gamma is in the range of 0.1-4. In some embodiments, the first hollowed-out area and the second hollowed-out area are _ki And S is equal to _ji The ratio gamma is in the range of 0.1-3. In some embodiments, the first hollowed-out area and the second hollowed-out area are _ki And S is equal to _ji The ratio gamma is in the range of 0.1-2. In some embodiments, the first hollowed-out area and the second hollowed-out area are _ki And S is equal to _ji The ratio gamma is in the range of 0.1-1.

In some embodiments, the ratio of the areas of the respective hollow areas of the elastic element 110 affects the resonance frequency difference of the respective hollow areas, and the resonance frequencies of the respective hollow areas are equal or close to each other, so that the sound pressures of the respective hollow areas can be superimposed, thereby increasing the output sound pressure level of the speaker at the fourth resonance peak position.

Fig. 10C is a schematic diagram of a frequency response curve of a vibration assembly according to other embodiments of the present disclosure. In some embodiments, as shown in fig. 10C, the frequency response curve 1050 represents the frequency response curve of the vibrating assembly when γ=0.6; the frequency response curve 1060 represents the frequency response curve of the vibrating assembly when γ=0.2. As shown in fig. 10C, the output sound pressure level (amplitude) of the frequency response curve 1050 at the fourth resonance peak is high, and the output sound pressure level (amplitude) of the frequency response curve 1060 at the fourth resonance peak is relatively low. Therefore, when the value of γ is in the range of 0.25-4, the vibration assembly 100 can have a high output sound pressure level in a high frequency range (e.g., 10000Hz-18000 Hz).

In some embodiments, the adjustment of the mass, centroid, and stiffness of the stiffener 120, and the mass and stiffness of the hollowed-out area of the center area 112 can be achieved by designing the projected area of the stiffener 120 along the vibration direction and the projected area of the largest contour of the stiffener 120 along the vibration direction at the center area 112, thereby achieving the adjustment of the first, third, and fourth resonance peaks of the vibration assembly 100.

In the present specification, referring to fig. 11, a reinforcing portion-to-reinforcing member 120 transverse area ratio β (unit is 1) is defined as a reinforcing portion projected area S in a projected shape of the reinforcing member 120 in the vibration direction _r Projected area S at central region 112 with the largest contour of stiffener 120 _t Ratio of:

in some embodiments, the reinforcement portion of the reinforcement 120 to the reinforcement 120 has a transverse area ratio β of 0.1-0.8. In some embodiments, the reinforcement portion of the reinforcement 120 to the transverse area ratio β of the reinforcement 120 is 0.2-0.7. In some embodiments, the reinforcement portion of the reinforcement 120 to the transverse area ratio β of the reinforcement 120 is 0.1-0.7. In some embodiments, the reinforcement portion of the reinforcement 120 to the reinforcement 120 has a transverse area ratio β of 0.2-0.6. In some embodiments, the reinforcement portion of the reinforcement 120 to the transverse area ratio β of the reinforcement 120 is 0.3-0.6. In some embodiments, the reinforcement portion of the reinforcement 120 to the reinforcement 120 has a transverse area ratio β of 0.4-0.5. In some embodiments, the reinforcement portion of the reinforcement 120 to the reinforcement 120 has a transverse area ratio β of 0.3-0.5. In some embodiments, the reinforcement portion of the reinforcement 120 to the reinforcement 120 has a transverse area ratio β of 0.2-0.5. In some embodiments, the reinforcement portion of the reinforcement 120 to the reinforcement 120 has a transverse area ratio β of 0.1-0.5.

In some embodiments, by designing the projection area of the reinforcement 120 along the vibration direction and the projection area of the maximum contour of the reinforcement 120 along the vibration direction, the control of the mass, the mass center and the rigidity of the reinforcement 120 and the adjustment of the mass and the rigidity of the hollowed-out area of the central area 112 can be realized, so that the control of the total equivalent mass Mt formed by combining the mass of the reinforcement 120, the mass of the elastic element 110, the equivalent air mass and the equivalent driving end mass is realized, and the adjustment of the first resonance peak, the third resonance peak and the fourth resonance peak of the loudspeaker is further realized.

Fig. 12B is a schematic diagram of a frequency response curve of a vibration assembly according to other embodiments of the present disclosure. In some embodiments, as shown in fig. 12B, an intermediate frequency curve 1210 represents the frequency response curve of the vibrating assembly when β=0.16; frequency response curve 1220 represents the frequency response curve of the vibrating assembly when β=0.17; frequency response curve 1230 represents the frequency response curve of the vibrating assembly when β=0.26. As shown in fig. 12B, the frequency response curve 1210, the frequency response curve 1220 and the frequency response curve 1230 have the first resonance peak 210, the second resonance peak 220, the third resonance peak 230 and the fourth resonance peak 240, and when the value of β is changed, the frequencies of the first resonance peak 210, the third resonance peak 230 and the fourth resonance peak 240 are changed greatly, and the frequency change of the second resonance peak 220 is small. When β=0.16, the frequency response curve 1210 does not exhibit the fourth resonance peak 240. When β increases to 0.17, the first and second resonance peaks 210 and 220 of the vibration assembly have small changes, the third resonance peak 230 moves to a high frequency, and the high frequency output sound pressure level increases, showing an obvious fourth resonance peak 240. When β increases to 0.26, the first resonance peak 210 moves to a low frequency, the third resonance peak 230 moves to a high frequency, the fourth resonance peak 240 moves to a high frequency, and the overall output sound pressure level of the vibration assembly decreases. Accordingly, when the value of β is changed, the first, third, and fourth resonance peaks of the vibration assembly 100 may be adjusted, and the value range of β may be set to 0.1 to 0.5 in order to locate the first, third, and fourth resonance peaks of the vibration assembly 100 within an appropriate range (e.g., the range shown in the embodiment of the present specification) and to have a higher output sound pressure level.

Referring to fig. 13A and 13B, fig. 13A and 13B are schematic views of vibration assemblies having different numbers of bar structures according to some embodiments of the present disclosure. In some embodiments, by adjusting the number of bar structures 124, the overall mass of the vibration assembly 100 may be adjusted such that the combined mass of the stiffener 120, the mass of the elastic element 110, the equivalent air mass, and the equivalent mass of the driving end form a total equivalent mass Mt, so that the resonant frequency of the mass Mt-spring Kt-damping Rt system is changed, and thus the first order resonant frequency of the vibration assembly 100 is changed, such that the sensitivity of the low frequency band before the first resonant frequency and the mid frequency band after the first resonant frequency of the vibration assembly 100 is changed. In some embodiments, a greater number of bar structures 124 may be designed such that the total equivalent mass Mt increases, and the first resonant frequency of the vibration assembly 100 advances, such that the low-band sensitivity of the vibration assembly 100 before the first resonant frequency increases, e.g., 3000Hz front frequency band, 2000Hz front frequency band, 1000Hz front frequency band, 500Hz front frequency band, 300Hz front frequency band. In some embodiments, a smaller number of bar structures 124 is designed such that the total equivalent mass Mt is reduced, the first resonant frequency of the vibration assembly 100 is shifted backward, such that the mid-band sensitivity after the first resonant frequency of the vibration assembly 100 is increased, e.g., the frequency band sensitivity after 3000Hz may be increased. For another example, the frequency band sensitivity after 2000Hz may be increased. For another example, the frequency band sensitivity after 1000Hz may be increased. For another example, the sensitivity of the frequency band after 500Hz can be increased. For another example, the sensitivity of the frequency band after 300Hz can be increased.

In some embodiments, by adjusting the number of bar structures 124, the stiffness of the stiffener 120 may also be adjusted such that the stiffener 120, the elastic element 110, provides stiffness Kt to the system ₁ When the change occurs, the reinforcement 120, the connection region 115, the folded ring region 114, the central region 112 and the suspended region between the folded ring region 114 and the region covered by the reinforcement 120 are equivalent to the empty spaceThe equivalent mass of the gas mass and the driving end are combined to form the total equivalent mass Mt ₁ The equivalent damping of each part forms the total equivalent damping Rt1, the mass Mt ₁ Spring Kt ₁ Damping Rt ₁ In the system, a certain annular area in the diameter direction of the reinforcing member 120 is taken as an equivalent fixed fulcrum, and the resonant frequency of the overturning motion formed by the annular is changed, so that the third resonant position of the vibration assembly 100 is changed.

In some embodiments, by adjusting the number of the bar-shaped structures 124, the area of the reinforcing member 120 corresponding to the central region 112 can be adjusted to be not less than one suspended region, so that the equivalent mass Mm of each hollowed-out region _i Equivalent stiffness Ka _i And Ka _i ' equivalent damping Ra _i And (3) with Ra (Ra) _i ' changes, thereby changing the fourth resonance peak position of the vibration assembly. In some embodiments, by adjusting the number of bar-shaped structures 124, the area to thickness ratio μ of the vibration assembly and the reinforcement portion of the reinforcement member 120 to the transverse area ratio β of the reinforcement member 120 can also be adjusted, thereby adjusting the location of the fourth resonance peak of the vibration assembly.

In some embodiments, the number of the bar-shaped structures 124 of the reinforcement member 120 may be adjustable, so that the positions of the first resonance peak, the third resonance peak, and the fourth resonance peak of the vibration assembly 100 may be adjusted according to the actual application requirements, thereby enabling a controllable adjustment of the frequency response of the vibration assembly 100.

In some embodiments, since the projection shape of the strip-shaped structure 124 along the vibration direction of the elastic element 110 includes at least one of rectangle, trapezoid, curve, hourglass shape, and petal shape, the area of the hollowed-out area (the suspended area corresponding to the central area 112 in the projection range of the stiffener 120) of the stiffener 120 can be changed by adjusting the shape of the strip-shaped structure 124, so as to adjust the relation (area thickness ratio μ) between the hollowed-out area and the thickness of the elastic element 110, thereby achieving the purpose of adjusting the fourth resonance peak; the relationship of the hollow area (the hollow area ratio gamma) between the different annular structures 122 of the reinforcement 120 can also be changed, so that the purpose of adjusting the fourth resonance peak is achieved; the relationship between the reinforcing portion of the reinforcing member 120 and the transverse area of the reinforcing member 120 (the ratio β of the reinforcing portion of the reinforcing member 120 to the transverse area of the reinforcing member 120) may be changed to achieve the purpose of adjusting the first resonance peak, the third resonance peak, and the fourth resonance peak.

Referring to fig. 14A-14D, fig. 14A-14D are schematic views of vibration components having different widths according to some embodiments of the present disclosure, wherein the bar-shaped structure 124 in fig. 14A is inverted trapezoid (i.e. the short side of the trapezoid is close to the center of the stiffener 120), the bar-shaped structure 124 in fig. 14B is trapezoid (i.e. the short side of the trapezoid is far from the center of the stiffener 120), the bar-shaped structure 124 in fig. 14C is outer arc, and the bar-shaped structure 124 in fig. 14D is inner arc. In some embodiments, the centroid position of the stiffener 120 may be effectively adjusted by designing the bar structures 124 with different lateral widths. In some embodiments, the stiffness of the stiffener 120 itself may also be varied without changing the mass of the stiffener 120, such that the stiffener 120, the elastic element 110 (and particularly the area of the central region 112 covered by the stiffener 120) provides stiffness Kt to the system ₁ Change to further make the mass Mt ₁ Spring Kt ₁ Damping Rt ₁ The resonant frequency of the system rollover motion changes, thereby changing the third resonant frequency of the vibration assembly 100.

In some embodiments, the local stiffness of the bar structure 124 may be varied at different locations extending from the center to the periphery by varying the width design of the bar structure 124. When the driving end frequency is close to Mt ₁ Spring Kt ₁ Damping Rt ₁ At the system resonance frequency, the connection region 115 between the fixed region 116 and the folded ring region 114, and the suspended region between the central region 112 covered by the reinforcement 120 and the folded ring region 114 vibrate under the driving of the reinforcement 120, and a resonance peak with an adjustable 3dB bandwidth is realized.

As shown in fig. 14A-14D. In some embodiments, by designing the inverted trapezoidal bar structure 124, the outer arc (defining an outward bulge as an outer arc, an inward recess as an inner arc, the outer arc may be an arc, an ellipse, a higher order function arc, and any other unexpected arc) bar structure 124, a larger third resonance peak of the 3dB bandwidth vibration assembly 100 may be obtained, which may be applicable to scenarios requiring low Q values, wide bandwidths. In some embodiments, by designing the bar-shaped structure 124 of trapezoid, rectangle, inner arc (defining outward convex as outer arc, inward concave as inner arc, inner arc may be arc, ellipse, higher order function arc, and any other inner arc), the third resonance peak of the vibration component 100 with high sensitivity and small 3dB bandwidth can be obtained, and the method can be applied to the scene requiring high Q value and local high sensitivity.

By designing the bar-shaped structures 124 with different lateral widths, the area of the reinforcing member 120 corresponding to the central region 112 with at least one suspended region can be adjusted so that each has an equivalent mass Mm _i Equivalent stiffness Ka _i And Ka _i ' equivalent damping Ra _i And (3) with Ra (Ra) _i ' change occurs. Further causing the fourth resonance peak position of the vibration assembly 100 to change.

Thus, by designing the bar structures 124 with different lateral widths, a third resonant peak frequency position of the vibration assembly 100, a 3dB bandwidth at the resonant peak, a sensitivity of the vibration assembly 100 at the resonant peak, a fourth resonant peak position of the vibration assembly 100 can be achieved.

Referring to fig. 15A and 15B, fig. 15A and 15B are schematic views of vibration assemblies having bar-shaped structures with different shapes according to some embodiments of the present disclosure, wherein the bar-shaped structure 124 in fig. 15A is in a rotating shape, and the bar-shaped structure 124 in fig. 15B is in an S shape. In some embodiments, by designing the bar-shaped structures 124 with different transverse shapes, the stiffness of the stiffener 120 may be adjusted such that the stiffener 120, the elastic element 110 (and particularly the area of the central region 112 covered by the stiffener 120) provides the stiffness Kt to the system ₁ Change to further make the mass Mt ₁ Spring Kt ₁ Damping Rt ₁ The system changes the resonant frequency of the flipping motion, thereby changing the third resonant position of the vibration assembly 100. In some embodiments, the area of the stiffener corresponding to the central region 112 having no less than one suspended region may also be adjusted so that each has an equivalent mass Mm _i Equivalent stiffness Ka _i And Ka _i ' equivalent damping Ra _i And (3) with Ra (Ra) _i ' is changed such that the fourth resonance peak position of the vibration assembly 100 is changed. In some embodiments, by designing the bar-shaped structures 124 with different lateral shapes, it is also possible to adjust the stress distribution inside the stiffener 120, control the tooling deformation of the stiffener 120.

Referring to fig. 16A-16E, fig. 16A-16E are schematic structural views of a reinforcement member having a bar-shaped structure with different shapes according to some embodiments of the present disclosure. In some embodiments, in order to accurately adjust the influence of the strip-shaped structures with different shapes on the resonance peak (such as the first resonance peak, the third resonance peak and the fourth resonance peak) of the vibration component, for the strip-shaped structure 124 with gradually decreasing width from the center to the edge, the spoke included angle θ is defined as the included angle between two sides of the projection shape of the strip-shaped structure on the projection plane perpendicular to the vibration direction, and the resonance peak of the vibration component can be adjusted by setting the magnitude of θ. In some embodiments, for a bar-shaped structure 124 with straight sides (as shown in fig. 16A-16C), the included angle θ is the included angle between two sides of the spoke. In some embodiments, for a strip-shaped structure 124 with sides that are arc edges (as shown in fig. 16E), the included angle θ is the included angle of tangents to two sides of the strip-shaped structure 124. In some embodiments, to accurately adjust the influence of different shaped bar-shaped structures on the resonance peaks (e.g., first, third, and fourth resonance peaks) of the vibration assembly, as shown in FIG. 16D, for spoke structures with increasing width from center to edge, a spoke angle θ is defined _i By setting theta _i The resonance peak of the vibration component can be adjusted. In some embodiments, for a bar-shaped structure 124 with straight sides, the included angle θ _i Namely the included angle between the two sides of the spoke. In some embodiments, for a bar-shaped structure 124 with straight sides, the included angle θ _i Namely the included angle of the tangent lines of the two side edges of the spoke.

In some embodiments, the angle θ (or θ) of the bar structures 124 may be designed by designing _i ) The rigidity of the stiffener 120 itself can be changed without changing or changing the mass of the stiffener 120 so that the stiffener 120, the elastic element 110 are tiedThe system provides rigidity Kt ₁ Change to further make the mass Mt ₁ Spring Kt ₁ Damping Rt ₁ The system changes the resonant frequency of the flipping motion, thereby changing the third resonant position of the vibration assembly 100, and controlling the 3dB bandwidth of the third resonant peak of the vibration assembly 100. In some embodiments, the angle θ (or θ) of the bar structures 124 may be increased by increasing _i ) Effectively increasing the 3dB bandwidth of the third harmonic of vibration assembly 100.

Corresponding to the frequency response of some vibration assemblies 100 requiring low Q and wide bandwidth, a larger included angle θ (or θ) of the bar-shaped structure 124 may be designed _i ). In some embodiments, the angle θ of the bar structures 124 may range from 0 to 150 °. In some embodiments, the angle θ of the bar-shaped structures 124 may range from 0 to 120 °. In some embodiments, the angle θ of the bar-shaped structures 124 may range from 0 to 90 °. In some embodiments, the angle θ of the bar-shaped structures 124 may range from 0 to 80 °. In some embodiments, the angle θ of the bar-shaped structures 124 may range from 0 ° to 60 °. In some embodiments, the bar-shaped structures 124 have an included angle θ _i May range from 0 to 90. In some embodiments, the bar-shaped structures 124 have an included angle θ _i May range from 0 to 80. In some embodiments, the bar-shaped structures 124 have an included angle θ _i May range from 0 to 70. In some embodiments, the bar-shaped structures 124 have an included angle θ _i May range from 0 to 60. In some embodiments, the bar-shaped structures 124 have an included angle θ _i May range from 0 to 45.

Corresponding to the frequency response of certain vibration assemblies 100 requiring a high Q narrow bandwidth, smaller angles θ (or θ) of the bar-shaped structures 124 may be designed _i ). In some embodiments, the angle θ of the bar-shaped structures 124 may range from 0 to 90 °. In some embodiments, the angle θ of the bar-shaped structures 124 may range from 0 to 80 °. In some embodiments, the angle θ of the bar-shaped structures 124 may range from 0 to 70 °. In some embodiments, the angle θ of the bar-shaped structures 124 may range from 0 to 60 °. In some embodiments, the bar-shaped structures 124 have an included angle θThe range may be 0 to 45 °. In some embodiments, the bar-shaped structures 124 have an included angle θ _i May range from 0 to 60. In some embodiments, the bar-shaped structures 124 have an included angle θ _i May range from 0 to 80. In some embodiments, the bar-shaped structures 124 have an included angle θ _i May range from 0 to 90. In some embodiments, the bar-shaped structures 124 have an included angle θ _i May range from 0 to 120. In some embodiments, the bar-shaped structures 124 have an included angle θ _i May range from 0 to 150.

In some embodiments, the relationship of θ to θi is defined as:

θ＝-θ _i . (equation 7)

The angle θ of the bar structure 124 may be designed to be larger for certain speaker frequency responses requiring low Q and wide bandwidth. In some embodiments, the angle θ of the bar-shaped structures 124 may range from-90 ° to 150 °. In some embodiments, the angle θ included by the bar-shaped structures 124 may range from-45 ° to 90 °. In some embodiments, the angle θ of the bar-shaped structures 124 may range from 0 ° to 60 °.

For certain speaker frequencies requiring a high Q and a narrow bandwidth, a smaller included angle θ of the bar 124 may be designed, and in some embodiments, the included angle θ of the bar 124 may range from-150 ° to 90 °. In some embodiments, the angle θ included by the bar-shaped structures 124 may range from-90 ° to 45 °. In some embodiments, the angle θ of the bar-shaped structures 124 may range from-60 ° to 0 °.

In some embodiments, for some irregularly shaped bar structures 124, the method of forming the included angle between the bar structures 124 cannot be designed, and at this time, the method of designing the included angle can be adopted, and the mass of the reinforcing member 120 can be unchanged or changed while the self-stiffness of the reinforcing member 120 is changed, so that the reinforcing member 120 and the elastic element 110 provide the stiffness Kt for the system ₁ Change to further make the mass Mt ₁ Spring Kt ₁ Damping Rt ₁ A system in which the resonant frequency of the flipping motion is changed, thereby changing the third resonant position of the vibration assembly 100; further, vibration can be controlledThe 3dB bandwidth of the third resonance peak of the movable assembly 100.

Fig. 16F is a schematic diagram of a frequency response curve of a vibration assembly according to other embodiments of the present disclosure, where the vibration assembly is configured such that the second resonant peak 220 and the third resonant peak 230 of the vibration assembly are combined, so that the frequency response curve of the vibration assembly only shows two resonant peaks. Fig. 16F shows the frequency response curves of the vibration assembly when the included angle θ of the bar-shaped structure 124 is 20 °, 10 ° and 1 °, respectively, and as shown in fig. 16F, the 3dB bandwidth of the middle-high frequency resonance peak (e.g., the resonance peak after the second resonance peak 220 and the third resonance peak 230 are combined) of the vibration assembly gradually increases as the included angle θ increases. Therefore, by adjusting the value of the included angle θ of the bar-shaped structure 124, the 3dB bandwidth of the middle-high frequency resonance peak of the vibration component can be adjusted. In some embodiments, the 3dB bandwidth of the high frequency resonance peak in at least one of the vibration assemblies may be made not less than 1000Hz by setting the included angle θ of the bar-shaped structure 124 to a value in the range of-60 to 60.

Referring to fig. 17A-17B, fig. 17A-17B are schematic structural views of a stiffener having an irregular bar structure according to some embodiments of the present description. In some embodiments, for the purpose of accurately designing the irregular bar-shaped structure for the purpose of adjusting the resonance peak of the vibration assembly, referring to fig. 17A, a circle with a radius R is defined by the maximum contour of the stiffener 120, 1/2 of the radius R of the circle defined by the maximum contour is defined as R/2, and the horizontal projection area of the stiffener 120 within the range of R/2 is defined as S _in The area of the stiffener 120 projected horizontally (i.e., projected in the direction of vibration of the vibration assembly) between the radius R/2 and the radius R circle is S _out Define the physical quantity τ as the horizontal projection area of the stiffener 120 as S _out The horizontal projection area with the reinforcement 120 is S _in Ratio of (3):

in some embodiments, the stiffener 120 may be adjusted to have a horizontal projected area S _out The horizontal projection area with the reinforcement 120 is S _in Controlling the reinforcement 120 by ratio τThereby achieving bandwidth control of the third resonance peak of the vibration assembly 100. For other types of regular stiffener 120 structures, see fig. 17B, e.g., oval, rectangular, square, other polygonal structures, the stiffener 120 is enveloped with a maximum profile defining a pattern similar to the stiffener 120 and defining the center region of the pattern as a reference point, the reference point to profile envelope each point distance R (e.g., R _i 、…、R _i+3 ) All corresponding R/2 (e.g., R _i /2、…、R _i+3 (2) Point formation zone reinforcement 120 has a horizontal projected area S _in The horizontal projection area of the reinforcement 120 in the range between the distance R/2 and the distance R is S _out The method comprises the steps of carrying out a first treatment on the surface of the For other irregular stiffener 120 structures, envelope with its maximum profile in a regular pattern of similar structures, and define S in the same manner as above _in 、S _out Ratio τ.

Corresponding to certain vibration assemblies 100 that require a low Q and wide bandwidth, a larger mass concentration in the center region of the stiffener 120 may be designed. In some embodiments, the horizontal projection area is S _out And the horizontal projection area is S _in The value range of the ratio tau can be 0.3-2. In some embodiments, the horizontal projection area is S _out And the horizontal projection area is S _in The value range of the ratio tau can be 0.5-1.5. In some embodiments, the horizontal projection area is S _out And the horizontal projection area is S _in The value range of the ratio tau can be 0.5-1.2; in some embodiments, the horizontal projection area is S _out And the horizontal projection area is S _in The value range of the ratio tau can be 0.5-1.3; in some embodiments, the horizontal projection area is S _out And the horizontal projection area is S _in The value range of the ratio tau can be 0.5-1.4; in some embodiments, the horizontal projection area is S _out And the horizontal projection area is S _in The value range of the ratio tau can be 0.3-1.2; in some embodiments, the horizontal projection area is S _out And the horizontal projection area is S _in The value range of the ratio tau can be 0.3-1.6; in some embodiments, the horizontal projection area is S _out And the horizontal projection area is S _in The value range of the ratio tau can be 0.5-2; in some embodiments, the horizontal projection area is S _out And the horizontal projection area is S _in The value range of the ratio tau can be 0.5-2.2; in some embodiments, the horizontal projection area is S _out And the horizontal projection area is S _in The value range of the ratio tau can be 0.3-2.2; in some embodiments, the horizontal projection area is S _out And the horizontal projection area is S _in The value range of the ratio tau can be 0.3-2.

Corresponding to certain vibration assembly 100 frequency responses requiring a high Q-value narrow bandwidth, a greater mass concentration at the edge region of the stiffener 120 may be designed. In some embodiments, the horizontal projection area is S _out And the horizontal projection area is S _in The ratio τ can range from 1 to 3. In some embodiments, the horizontal projection area is S _out And the horizontal projection area is S _in The value range of the ratio tau can be 1.2-2.8. In some embodiments, the horizontal projection area is S _out And the horizontal projection area is S _in The value range of the ratio tau can be 1.4-2.6. In some embodiments, the horizontal projection area is S _out And the horizontal projection area is S _in The value range of the ratio tau can be 1.6-2.4. In some embodiments, the horizontal projection area is S _out And the horizontal projection area is S _in The value range of the ratio tau can be 1.8-2.2. In some embodiments, the horizontal projection area is S _out And the horizontal projection area is S _in The value range of the ratio tau can be 1.2-2. In some embodiments, the horizontal projection area is S _out And the horizontal projection area is S _in The ratio τ can range from 1 to 2. In some embodiments, the horizontal projection area is S _out And the horizontal projection area is S _in The ratio τ can range from 2 to 2.8. In some embodiments, the horizontal projection area is S _out And the horizontal projection area is S _in The ratio τ can range from 2 to 2.5.

In some embodiments, the horizontal projection area is adjusted to S _out And the horizontal projection area is S _in The value range of the ratio tau can also lead the turning motion of the vibrating assembly to be harmonic when vibratingThe frequency of the oscillation changes, so that the position of the third resonance peak changes. Fig. 17C is a schematic diagram of a frequency response curve of a vibration assembly according to other embodiments of the present disclosure. As shown in fig. 17C, the frequency response curves of the vibration component when τ takes a value of 1.68 and 1.73, respectively, and the 3dB bandwidths at the third resonance peak 230 of the two frequency response curves are both narrower. When τ increases from 1.68 to 1.73, the third resonance peak 230 shifts to a low frequency. Therefore, as τ increases, the frequency corresponding to the third resonant peak 230 decreases, and by adjusting τ of the vibration component, the bandwidth and position of the third resonant peak can be effectively adjusted.

In some embodiments, the relationship between the area of the hollowed-out area (corresponding to the suspended area of the central area 112 in the projection range of the stiffener 120) and the thickness of the elastic element 110 (the area-thickness ratio μ) can be adjusted by adjusting the number of the annular structures 122 (for example, in the range of 1-10), so as to achieve the purpose of adjusting the fourth resonance peak; the relationship of the hollow area (the hollow area ratio gamma) between the different annular structures 122 of the reinforcement 120 can also be changed, so that the purpose of adjusting the fourth resonance peak is achieved; the relationship between the reinforcing portion of the reinforcing member 120 and the lateral area of the reinforcing member 120 (the ratio β of the reinforcing portion of the reinforcing member 120 to the lateral area of the reinforcing member 120) may be changed, and the purposes of the first resonance peak, the third resonance peak, and the fourth resonance peak may be adjusted.

In some embodiments, the annular structure 122 may include a first annular structure and a second annular structure with coincident centroids, where the radial dimension of the first annular structure is less than the radial dimension of the second annular structure. In some embodiments, the strip-shaped structure 124 may further include at least one first strip-shaped structure and at least one second strip-shaped structure, where the at least one first strip-shaped structure is disposed inside and connected to the first annular structure, and the at least one second strip-shaped structure is disposed between and connected to the first annular structure and the second annular structure, respectively, so that the stiffener 120 forms a plurality of different hollowed-out areas.

Referring to fig. 18A-18C, fig. 18A-18C are schematic views of vibration assembly structures having different numbers of ring structures according to some embodiments of the present disclosure, wherein the ring structure 122 of fig. 18A is a single ring structure, the ring structure 122 of fig. 18B is a double ring structure, and the ring structure 122 of fig. 18C is a triple ring structure. The mass and rigidity of the reinforcement 120 can be adjusted by designing the number of the annular structures 122, and the size of the hollow area of the central area 112 can be adjusted. In some embodiments, the number of ring structures 122 may range from 1 to 10. In some embodiments, the number of ring structures 122 may range from 1 to 5. In some embodiments, the number of ring structures 122 may range from 1 to 3.

In some embodiments, by adjusting the number of annular structures 122, the mass of the stiffener 120 may be adjusted such that the combined total equivalent mass Mt formed by the stiffener 120 mass, the elastic element 110 mass, the equivalent air mass, and the drive end equivalent mass changes, thereby changing the resonant frequency of the mass Mt-spring Kt-damping Rt system and thus changing the first order resonant frequency of the vibration assembly 100.

In some embodiments, the stiffness of the stiffener 120 may also be adjusted by adjusting the number of annular structures 122 such that the stiffener 120, the elastic element 110 (and particularly the area of the central region 112 covered by the stiffener 120) provides stiffness Kt to the system ₁ Change to further make the mass Mt ₁ Spring Kt ₁ Damping Rt ₁ The system changes the resonant frequency of the flipping motion, thereby changing the third resonant position of the vibration assembly 100. In some embodiments, the rigidity distribution of the strip-shaped structure 124 at different positions extending from the center to the periphery can be made different by adjusting the number of the annular structures 122, when the driving end frequency is close to Mt ₁ Spring Kt ₁ Damping Rt ₁ At the system resonant frequency, the areas of the connection area 115, the folded ring area 114 and the local suspension area between the area of the central area 112 covered by the reinforcing member 120 and the folded ring area 114 vibrate under the driving of the reinforcing member 120, and a resonance peak with adjustable 3dB bandwidth is realized.

In some embodiments, by adjusting the number of ring structures 122, it is also possible toThe size of the hollow area of the central area 112 is adjusted so that each hollow area has equivalent mass Mm _i Equivalent stiffness Ka _i And Ka _i ' equivalent damping Ra _i And (3) with Ra (Ra) _i ' is changed such that the fourth resonance peak position of the vibration assembly 100 is changed.

In some embodiments, the size of the outermost annular structure 122 may be adjusted by adjusting the number of annular structures 122, so as to adjust and control the area of the partially hollowed-out region between the region of the central region 112 covered by the reinforcing member 120 and the folded-ring region 114, and the three parts of the region, the connection region 115 and the folded-ring region 114 may form equivalent mass Ms, equivalent rigidity Ks and equivalent damping Rs. The mass Ms-spring Ks-damping Rs system resonant frequency is varied by the area of the localized suspended region between the region of the central region 112 covered by the stiffener 120 and the gimbal region 114, thereby effecting adjustment of the second resonant peak position of the vibration assembly 100.

In some embodiments, by adjusting the number of the annular structures 122, the fourth resonance peak of the vibration component 100 can be located in the range of 10kHz-18kHz, and the ratio of the area Si of each hollowed-out area to the thickness Hi of the diaphragm of each hollowed-out area is in the range of 150mm-700mm; hollow area S of any two elastic elements 110 _ki And S is equal to _ji The ratio gamma is in the range of 0.25-4; the ratio β of the reinforcing portion of the reinforcing member 120 to the transverse area of the reinforcing member 120 is 0.2 to 0.7. In some embodiments, by adjusting the number of the annular structures 122, the fourth resonance peak of the vibration component 100 can be located in the range of 10kHz-18kHz, and the ratio of the area Si of each hollowed-out area to the thickness Hi of the diaphragm of each hollowed-out area is in the range of 100mm-1000mm; hollow area S of any two elastic elements 110 _ki And S is equal to _ji The ratio gamma is in the range of 0.1-10; the ratio β of the reinforcing portion of the reinforcing member 120 to the transverse area of the reinforcing member 120 is 0.1 to 0.8.

Referring to fig. 19, fig. 19 is a schematic view of a vibration assembly with discontinuous inner and outer annular ring structures according to some embodiments of the present disclosure. In some embodiments, when the vibration assembly 100 includes at least 2 annular structures, the annular structures 122 divide the strip-shaped structures into a plurality of regions extending circumferentially along the center of the strip-shaped structures 124, and the strip-shaped structures 124 in each region may or may not be disposed continuously. In some embodiments, the one or more annular structures 122 of the vibration assembly 100 may include at least a first annular structure 1221. For example, the annular structure 122 may include a first annular structure 1221 and a second annular structure 1222 having coincident centroids, the radial dimension of the first annular structure 1221 being smaller than the radial dimension of the second annular structure 1222. In some embodiments, the bar structure 124 may include at least one first bar structure 1241 and at least one second bar structure 1242, where any one first bar structure 1241 is disposed at a first location inside the first ring structure 1221 and connected to the first ring structure 1221, and any one second bar structure 1242 is connected to a second location outside the first ring structure 1221. The first plurality of bar structures 1241 are connected to the first plurality of locations and the second plurality of bar structures 1242 are connected to the second plurality of locations, and in some embodiments, the line connecting at least one of the first locations to the center of the first ring structure 1221 does not pass through any one of the second locations. In some embodiments, the line connecting the at least one second location to the center of the first annular structure 1221 does not pass through any one of the first locations. In some embodiments, the plurality of first locations and the plurality of second locations are different, i.e., the first locations, the second locations, and the center of the first annular structure 1221 are all non-collinear, and the connection locations of the first and second strip-shaped structures 1241, 1242 on the first annular structure 1221 may be different. In some embodiments, the number of first and second bar structures 1241 and 1242 may be the same or different.

By discontinuously arranging the strip-shaped structures 124 in the inner and outer areas of the annular structure 122, the strip-shaped structures 124 in the inner and outer areas of the annular structure 122 can be different in number, the strip-shaped structures 124 in the inner and outer areas are different in transverse width, and the strip-shaped structures 124 in the inner and outer areas are different in transverse shape, so that the mass, rigidity and mass center distribution of the reinforcing member 120, the number of hollowed-out areas in the central area 112 and the area size can be adjusted in a large range.

In some embodiments, by adjusting the quality of the stiffener 120The amount can regulate and control the total equivalent mass Mt to change, so that the resonance frequency of the mass Mt-spring Kt-damping Rt system is changed, and the first-order resonance frequency of the vibration assembly 100 is changed. By adjusting the stiffness of the stiffener 120, mt can be adjusted ₁ Spring Kt ₁ Damping Rt ₁ A system that reverses the resonant frequency of the motion, thereby changing the third resonant position of the vibration assembly 100; the rigidity distribution of the strip-shaped structure 124 at different positions extending from the center to the periphery is different, so that a third resonance peak of the vibration assembly 100 with adjustable 3dB bandwidth is realized. By adjusting the number and the size of the hollowed-out areas of the central area 112, the fourth resonance peak position and the sensitivity of the vibration assembly 100 can be changed.

In some embodiments, the fourth resonance peak of the vibration assembly 100 is located in the range of 10kHz-18kHz by the discontinuous arrangement of the strip-shaped structures 124 in the inner and outer regions of the annular structure 122, each hollowed-out region having an area S _i Thickness H of the elastic element 110 corresponding to each hollow region _i The ratio is the area thickness ratio mu, the range is 150mm-700mm, and the hollow area S of any two elastic elements 110 _ki And S is equal to _ji The ratio gamma is in the range of 0.25-4 and the ratio beta of the reinforcing portion of the reinforcing member 120 to the transverse area of the reinforcing member 120 is in the range of 0.2-0.7. In some embodiments, the fourth resonance peak of the vibration component 100 may be located in the range of 10kHz-18kHz by discontinuously disposing the strip-shaped structures 124 in the inner and outer regions of the annular structure 122, each hollowed-out region having an area S _i And the thickness H of the vibrating diaphragm of each hollowed-out area _i The ratio is the area thickness ratio mu and the range is 100mm-1000mm; hollow area S of any two elastic elements 110 _ki And S is equal to _ji The ratio gamma is in the range of 0.1-10; the ratio β of the reinforcing portion of the reinforcing member 120 to the transverse area of the reinforcing member 120 is 0.1 to 0.8.

Referring to fig. 20A, fig. 20A is a schematic structural view of a vibration assembly having a plurality of ring structures according to some embodiments of the present disclosure. In some embodiments, mass distribution design of the stiffener 120 may be achieved by designing a plurality of annular structures 122 such that the spacing areas of the plurality of annular structures 122 are designed, and by designing the number of bar structures 124 for different spacing areas. It should be noted that the number of the strip-shaped structures 124 designed in the interval region of each annular structure 122 may be different, the shape may be different, or the positions may not be corresponding.

In some embodiments, each annular structure 122 from the center to the outside may be defined as a first annular structure 1221, a second annular structure 1222, a third annular structure 1223, … …, an nth annular structure, a stripe structure 124 of a space region between the nth annular structure and the n-1 th annular structure is defined as an nth stripe structure (e.g., a first stripe structure 1241, a second stripe structure 1242, a third stripe structure 1243), and the number of the nth stripe structures (i.e., stripe structures connected to the inner side of the nth annular structure) is defined as Q _n Wherein n is a natural number. Defining the physical quantity Q as the quantity Q of any ith bar-shaped structure _i The number of the bar structures with the j is Q _j Ratio of (3):

in some embodiments, the number Q of any ith stripe-like structure _i Number Q of bar-shaped structures with j _j The value range of the ratio q can be 0.05-20. In some embodiments, the number Q of any ith stripe-like structure _i Number Q of bar-shaped structures with j _j The ratio q can be in the range of 0.1-10. In some embodiments, the number Q of any ith stripe-like structure _i Number Q of bar-shaped structures with j _j The ratio q can be in the range of 0.1-8. In some embodiments, the number Q of any ith stripe-like structure _i Number Q of bar-shaped structures with j _j The ratio q can be in the range of 0.1-6. In some embodiments, the number Q of any ith stripe-like structure _i Number Q of bar-shaped structures with j _j The ratio q can be in the range of 0.2-5. In some embodiments, the number Q of any ith stripe-like structure _i Number Q of bar-shaped structures with j _j The ratio q can be in the range of 0.3-4. In some embodiments, the number Q of any ith stripe-like structure _i Number Q of bar-shaped structures with j _j The ratio q can be in the range of 0.5-6. In some embodimentsNumber Q of arbitrary ith bar-like structures _i Number Q of bar-shaped structures with j _j The ratio q can range from 1 to 4. In some embodiments, the number Q of any ith stripe-like structure _i Number Q of bar-shaped structures with j _j The ratio q can be in the range of 1-2. In some embodiments, the number Q of any ith stripe-like structure _i Number Q of bar-shaped structures with j _j The value range of the ratio q can be 0.5-2.

In some embodiments, the mass distribution design of the stiffener 120 is achieved by designing the plurality of annular structures 122 such that the spacing areas of the plurality of annular structures 122 are designed, and by designing the number of bar structures 124 of different spacing areas, and further the stiffness of the stiffener 120 is changed under the condition that the mass of the stiffener 120 is not changed or changed, so that the equivalent stiffness Kt of the stiffener 120, the diaphragm ₁ Change to further make the mass Mt ₁ Spring Kt ₁ Damping Rt ₁ The resonant frequency of the flipping motion of the system is changed, thereby changing the third resonance peak position of the speaker.

Fig. 20B is a schematic diagram of a frequency response curve of a vibration assembly according to some embodiments of the present disclosure. The two frequency response curves shown in fig. 20B are frequency response curves of the vibration component when q=0.67 and q=0.1, respectively, and the frequencies of the third resonance peaks 230 of the two frequency response curves are close, but the amplitude of the third resonance peak 230 of the frequency response curve corresponding to q=0.67 is higher than the amplitude of the third resonance peak of the frequency response curve corresponding to q=0.1. Therefore, as can be seen from fig. 20B, by adjusting the value of q, the amplitude change of the third resonance peak can be controlled, thereby adjusting the sensitivity of the vibration element. In some embodiments, the vibrating assembly has a higher sensitivity when q has a value in the range of 0.2-5.

In some embodiments, the shape of the annular structure 122 may include at least one of a circular ring, an elliptical ring, a polygonal ring, and a curvilinear ring. By designing the annular structures 122 in different shapes and/or different sizes, the mass and rigidity of the reinforcement 120 can be adjusted, and the area of the hollow area of the central area 112 can be adjusted.

In some embodiments, the size and shape of the overhanging region 1121 may be regulated by the size and shape of the region of the central region 112 that is covered by the stiffener 120, and the size and shape of the stiffener 120. In some embodiments, the area and shape of the ring-folded region 114 can be adjusted to adjust the total horizontal projection (i.e. the projection along the vibration direction of the vibration component) area of the suspended region 1121 and the ring-folded region 114, and the second resonance peak of the vibration component 100 can be precisely controlled to be located in the required frequency band by controlling the total horizontal projection area of the suspended region 1121 and the ring-folded region 114, the thickness of the elastic element 110, the ring-folded camber, and the like. In some embodiments, the second resonance peak of vibration assembly 100 may be located in the range of 3000Hz-7000 Hz. In some embodiments, by controlling the area ratio of the suspended region 1121 to the folded-over region 114, the vibrational displacement of the vibration assembly 100 in that localized region of its second formant frequency band can be adjusted to maximize the output sensitivity of the vibration assembly 100 at the second formant location.

In some embodiments, the local equivalent mass Mm can be achieved by the size of the folded-over region 114 and the suspended region 1121 of the vibration assembly 100 and the thickness of the elastic element 110 ₃ Equivalent to local equivalent mass Mm ₂ Local area stiffness Ka ₂ ' and local area stiffness Ka ₁ ' control, in turn, ensures that the second resonant peak of the vibration assembly 100 is in the desired frequency range. In some embodiments, S is caused by changing the shape of the annular structure 122 _s And the thickness H of the vibrating diaphragm _i The ratio alpha of (a) is in the range of 5000mm to 12000mm, so that the second resonance peak of the vibration assembly 100 can be located in the range of 3000Hz to 7000 Hz. In some embodiments, S is caused by changing the shape of the annular structure 122 _s And the thickness H of the vibrating diaphragm _i The value of the ratio alpha of the vibration component 100 is 6000mm-10000mm, so that the second resonance peak of the vibration component 100 can be positioned in the range of 3000Hz-7000 Hz.

In some embodiments, the horizontal projection surfaces of the folded ring region 114 and the suspended region 1121 can be realized by the relationship between the dimensions of the folded ring region 114 and the suspended region 1121 and the folded ring arch height of the folded ring region 114 and by the arch height design of the folded ringThe three-dimensional size of the folded-over region 114 of the elastic member 110 is changed without changing the product, thereby changing the rigidity Ka of the folded-over region 114 ₁ ' and thus control of the second resonance peak of the vibration assembly 100. In some embodiments, S _s The value range of the ratio delta between the arch height of the folded ring and the arch height delta h can be 50mm-600mm. In some embodiments, S _s The value range of the ratio delta between the arch height of the folded ring and the arch height delta h can be 100mm-500mm. In some embodiments, S _s The value range of the ratio delta between the arch height of the folded ring and the arch height delta h can be 200mm-400mm.

In some embodiments, the size of the suspended area 1121 and the area of the central area 112 are related, so that the reinforcement 120 realizes a certain bending deformation in the frequency band, and the sound pressure superposition of different areas of the elastic element 110 is increased and decreased, thereby realizing the maximum sound pressure level output. In some embodiments, the suspended region 1121 has a horizontal projected area S _v The horizontal projection area of the vibration component 100 and the central part of the vibration film is S _c Ratio of (2)The value range can be 0.05-0.7. In some embodiments, the suspended region 1121 has a horizontal projected area S _v The horizontal projection area of the vibration component 100 and the central part of the vibration film is S _c Ratio of (2)The value range can be 0.1-0.5. In some embodiments, the suspended region 1121 has a horizontal projected area S _v The horizontal projection area of the vibration component 100 and the central part of the vibration film is S _c Ratio of->The value range can be 0.15-0.35.

Referring to fig. 21A-21E, fig. 21A-21E are schematic structural views of vibration components having different structures according to some embodiments of the present disclosure. In some embodiments, the outer profile of the stiffener 120 may be a structure with outwardly extending spokes (as shown in fig. 21A), a circular ring structure, an oval ring structure or a curvilinear ring structure (as shown in fig. 21B), a polygon, other irregular ring structures, etc., wherein the polygon may include a triangle, a quadrilateral, a pentagon, a hexagon (as shown in fig. 21C-21D), a heptagon, an octagon, a nonagon, a decagon, etc. In some embodiments, the elastic element 110 may also be polygonal, for example: triangles, quadrilaterals (as shown in fig. 21D and 21E), pentagons, hexagons, heptagons, octagons, nonagons, decagons, etc., and other irregular patterns, the stiffener 120 may be correspondingly designed in similar or dissimilar structures, so that the shape of the suspended region 1121 is controlled by the shape of the stiffener 120, the central region 112, and the folds of the fold-over region 114, thereby enabling tuning of the performance of the vibration assembly 100.

Referring to fig. 22, fig. 22 is a schematic structural view of a vibration assembly of a variable-width ring structure according to some embodiments of the present disclosure. In some embodiments, by designing partial structures with different widths at different positions of any one of the annular structures 122, the mass of the stiffener 120 can be effectively adjusted and regulated, and the total equivalent mass Mt can be regulated and controlled to be changed, so that the resonant frequency of the mass Mt-spring Kt-damping Rt system is changed, and the first-order resonant frequency of the vibration assembly 100 is further changed. Meanwhile, by designing partial structures of unequal widths at different locations (e.g., adjacent locations) of any one of the annular structures 122, the stiffness and centroid distribution of the stiffener 120 can be adjusted, thereby adjusting the resonant frequency of the overturned motion of the Mt 1-spring Kt 1-damping Rt1 system such that the third resonant position of the vibration assembly 100 is changed. The unequal width of the annular structure 122 also allows the stiffness distribution of the strip-shaped structure 124 to be different at different positions extending from the center to the periphery, thereby realizing a third resonance peak of the vibration assembly 100 with adjustable 3dB bandwidth. The annular structures 122 with unequal widths can also be designed to adjust the number and the area of the suspended areas of the central area 112, so that the fourth resonance peak position and the sensitivity of the vibration assembly 100 are changed. For example, at least one of the one or more annular structures 122 has a different radial width on both sides of the connection location with any of the one or more strip structures 124, as shown in fig. 22. As another example, at least one of the one or more annular structures 122 has a different circumferential width between the connection locations with any two of the one or more bar structures 124.

In some embodiments, the partial structures with unequal widths are designed at any position (e.g., adjacent positions) of any one of the annular structures 122, so that the fourth resonance peak of the vibration assembly 100 is located in the range of 15kHz-18kHz, and each hollowed-out area S _i Thickness H of the elastic element 110 corresponding to each hollow region _i The ratio is the area thickness ratio mu, the range is 150mm-700mm, and the hollow area S of any two elastic elements 110 _ki And S is equal to _ji The ratio gamma is in the range of 0.25-4 and the ratio beta of the reinforcing portion of the reinforcing member 120 to the transverse area of the reinforcing member 120 is in the range of 0.2-0.7. In some embodiments, the local structures with unequal widths are designed at any position of any one of the annular structures 122, so that the fourth resonance peak of the vibration component 100 is located in the range of 15kHz-18kHz, and the area S of each hollowed-out area is _i The ratio of the thickness Hi of the diaphragm to the thickness mu of each hollowed-out area is 100mm-1000mm; hollow area S of any two elastic elements 110 _ki And S is equal to _ji The ratio gamma is in the range of 0.1-10; the ratio β of the reinforcing portion of the reinforcing member 120 to the transverse area of the reinforcing member 120 is 0.1 to 0.8.

Referring to fig. 23, fig. 23 is a schematic structural view of a vibration assembly having an irregular ring structure according to some embodiments of the present disclosure. In some embodiments, by designing the partial structures of different locations of the different annular structures 122, such as circles, rectangles, squares, triangles, hexagons, octagons, other polygons, ovals, and other irregular annular structures 122, the size, location, and shape of the partial areas of the annular structures 122 can be more flexibly controlled, the mass of the stiffener 120 can be effectively adjusted, the total equivalent mass Mt can be adjusted, and the resonant frequency forming the mass Mt-spring Kt-damping Rt system can be changed, so that the first resonant frequency of the vibration assembly 100 can be changed. By adjusting the rigidity of the reinforcement 120 and the mass center distribution of the reinforcement 120, the Mt 1-spring Kt 1-damping Rt1 system can be adjusted, and the resonance frequency of the overturning motion can be adjusted, so that the position of the third resonance peak of the vibration assembly 100 is changed; the rigidity distribution of the strip-shaped structure 124 at different positions extending from the center to the periphery is different, so that a third resonance peak of the vibration assembly 100 with adjustable 3dB bandwidth is realized. Meanwhile, the number and the area of the suspended areas of the central area 112 can be effectively adjusted, so that the fourth resonance peak position and the sensitivity of the vibration assembly 100 are changed. In addition, by designing the irregular structure, stress concentration can be effectively avoided, so that the deformation of the reinforcing member 120 is smaller.

In some embodiments, referring to fig. 23, the stiffener 120 comprises a double annular structure including a first annular structure 1221 on the inside and a second annular structure 1222 on the outside. In some embodiments, the shape of the first annular structure 1221 and the second annular structure 1222 may be different. In some embodiments, the first annular structure 1221 may be a curvilinear ring and the second annular structure 1222 may be a circular ring. In some embodiments, the fourth resonance peak of the vibration assembly 100 may be located in the range of 10kHz-18kHz, with the respective hollowed-out areas S by designing the irregular annular structure 122 _i And the thickness H of the vibrating diaphragm of each hollowed-out area _i The ratio is the area thickness ratio mu and the range is 150mm-700mm, and the area S of any two vibrating diaphragm hollowed-out areas _ki And S is equal to _ji The ratio gamma is in the range of 0.25-4 and the ratio beta of the reinforcing portion of the reinforcing member 120 to the transverse area of the reinforcing member 120 is in the range of 0.2-0.7. In some embodiments, the fourth resonance peak of the vibration assembly 100 is located in the range of 15kHz-18kHz, with each hollowed-out area S by designing the irregular annular structure 122 _i And the thickness H of the vibrating diaphragm of each hollowed-out area _i The ratio is the area thickness ratio mu and the range is 100mm-1000mm; hollow area S of any two elastic elements 110 _ki And S is equal to _ji The ratio gamma is in the range of 0.1-10; the ratio β of the reinforcing portion of the reinforcing member 120 to the transverse area of the reinforcing member 120 is 0.1 to 0.8.

Referring to fig. 24A-24B, fig. 24A is a schematic structural view of a vibration assembly having a bar-shaped structure with a step structure according to some embodiments of the present disclosure. Fig. 24B is a schematic structural view of a vibration assembly according to a bar-shaped structure having a step structure shown in other embodiments of the present specification. In some embodiments, referring to fig. 24A, by designing the reinforcement 120 with the bar-shaped structure 124 having a step structure, under the condition that the hollowed-out area (affecting the fourth resonance peak of the vibration assembly 100) and the suspended area 1121 (affecting the second resonance peak of the vibration assembly 100) of the control center area 112 are unchanged, the rigidity, the mass and the mass center distribution of the reinforcement 120 are changed, so that the effective adjustment of the first resonance peak position, the third resonance peak position and the bandwidth of the vibration assembly 100 can be realized without changing the second resonance peak and the fourth resonance peak of the vibration assembly 100, and different frequency response curves can be adjusted according to practical application requirements.

In some embodiments, by designing the thickness of different regions of the stiffener 120 from the thickness direction (i.e., along the vibration direction of the vibration assembly 100), it is achieved that the stiffener 120 mass can be unchanged or changed while the stiffener 120 stiffness itself is changed, depending on the actual desired mass distribution, such that the stiffener 120, the elastic element 110, provides the stiffness Kt to the system ₁ Change to further make the mass Mt ₁ Spring Kt ₁ Damping Rt ₁ A system in which the resonant frequency of the flipping motion is changed, thereby changing the third resonant position of the vibration assembly 100; further, the 3dB bandwidth of the third resonance peak of the vibration assembly 100 may be controlled.

In some embodiments, the bar-shaped structure 124 may have a plurality of steps having different thicknesses along the vibration direction of the elastic member 110, i.e., the bar-shaped structure 124 has a stepped shape. In some embodiments, at least one of the plurality of bar structures has a stepped shape. In some embodiments, all of the plurality of bar structures have a stepped shape. The structure of the reinforcing member 120 having the bar-shaped structure 124 of a stepped shape, and the sectional structure of the D-D section thereof are shown in fig. 24B. Defining the thickness h of the endmost step of the reinforcement 120 structure (i.e., the first step located radially outermost of the bar-shaped structure 124) to be ₁ The thickness of the secondary edge step is h ₂ … … the central step (i.e. the second step located radially innermost of the bar-shaped structure 124) has a thickness h _n Defining the physical quantity epsilon as the thickness h of any two steps _j And h _k Ratio of (k > j):

defining the physical quantity phi as the thickness h of the endmost step of the reinforcement 120 structure (i.e., the first step located radially outermost of the bar-shaped structure 124) is ₁ A thickness h with the center step (and the second step located radially innermost of the bar-shaped structure 124) _n Ratio of (3):

in some embodiments, any two step thicknesses h _j And h _k The value of the ratio E is in the range of 0.1-10. In some embodiments, any two step thicknesses h _j And h _k The value of the ratio E is in the range of 0.1-8. In some embodiments, any two step thicknesses h _j And h _k The value of the ratio E is in the range of 0.2-8. In some embodiments, any two step thicknesses h _j And h _k The value of the ratio E is in the range of 0.1-7. In some embodiments, any two step thicknesses h _j And h _k The value of the ratio E is in the range of 0.1-6. In some embodiments, any two step thicknesses h _j And h _k The value of the ratio E is in the range of 0.2-6. In some embodiments, any two step thicknesses h _j And h _k The value of the ratio E is in the range of 0.2-5. In some embodiments, any two step thicknesses h _j And h _k The value of the ratio E is in the range of 0.25-4.

In some embodiments, by designing the thickness of different regions of the stiffener 120, the mass distribution of the stiffener 120 may be adjusted to change the stiffness of the stiffener 120 itself without changing or varying the mass of the stiffener 120, such that the stiffener 120, the elastic element 110, provides the stiffness Kt to the system ₁ Changes are made to adjust the position of the third resonance peak of the vibration assembly 100 and to control the 3dB bandwidth of the third resonance peak of the vibration assembly 100.

Fig. 24C is a plot of the frequency response of a vibration assembly according to other embodiments of the present disclosure, wherein the vibration assembly is configured such that the second resonant peak 220 and the third resonant peak 230 of the vibration assembly are combined, such that the plot of the frequency response of the vibration assembly exhibits only two resonant peaks. As shown in fig. 24C, the frequency response curves of the vibration components corresponding to e=1, e=0.68, and e=0.5 are shown. As shown in fig. 24C, the positions of the middle-high frequency resonance peaks (e.g., the resonance peak after the second resonance peak 220 and the third resonance peak 230 are combined) of the frequency response curves corresponding to e=1, e=0.68, and e=0.5 are different, the 3dB bandwidths at the resonance peaks are also different, and as the value of e becomes smaller, the resonance frequency of the middle-high frequency resonance peak (e.g., the resonance peak after the second resonance peak 220 and the third resonance peak 230) of the vibration component is gradually increased, and the 3dB bandwidth is gradually increased. Therefore, the frequency position of the middle-high frequency resonance peak and the 3dB bandwidth of the vibration component can be adjusted by adjusting the value of E. In some embodiments, any two step thicknesses h _j And h _k The ratio epsilon of the vibration component is in the range of 0.25-4, so that the middle-high frequency resonance peak of the vibration component is in the range of 3000Hz-12000Hz, and the resonance peak has a larger 3dB bandwidth.

Corresponding to certain vibration assemblies 100 that require a low Q and wide bandwidth, a larger mass concentration near the center of the stiffener 120 may be designed. In some embodiments, the stiffener 120 is configured to have an edge-most step thickness h ₁ Thickness of the central step is h _n The value of the ratio phi of the (E) is in the range of 0.1-1. In some embodiments, the stiffener 120 is configured to have an edge-most step thickness h ₁ Thickness of the central step is h _n The value of the ratio phi of the (E) is in the range of 0.2-0.8. In some embodiments, the stiffener 120 is configured to have an edge-most step thickness h ₁ Thickness of the central step is h _n The value of the ratio phi of the (E) is in the range of 0.2-0.6. In some embodiments, the stiffener 120 is configured to have an edge-most step thickness h ₁ Thickness of the central step is h _n The value of the ratio phi of the (E) is in the range of 0.2-0.4.

Corresponding to the frequency response of certain vibration assemblies 100 requiring a high Q narrow bandwidth, a greater mass concentration in the stiffener 120 may be designedIs provided. In some embodiments, the stiffener 120 is configured to have an edge-most step thickness h ₁ Thickness of the central step is h _n The value of the ratio phi of the (E) is 1-10. In some embodiments, the stiffener 120 is configured to have an edge-most step thickness h ₁ Thickness of the central step is h _n The value of the ratio phi of the (E) is 1.2-6. In some embodiments, the stiffener 120 is configured to have an edge-most step thickness h ₁ Thickness of the central step is h _n The value of the ratio phi of the (E) is 2-6. In some embodiments, the stiffener 120 is configured to have an edge-most step thickness h ₁ Thickness of the central step is h _n The value of the ratio phi of the (E) is 3-6. In some embodiments, the stiffener 120 is configured to have an edge-most step thickness h ₁ Thickness of the central step is h _n The value of the ratio phi of the (E) is in the range of 4-6. In some embodiments, the stiffener 120 is configured to have an edge-most step thickness h ₁ Thickness of the central step is h _n The value of the ratio phi of the (E) is 5-6.

Referring to fig. 25A-25C, fig. 25A-25C are schematic structural views of vibration assemblies with different shaped stiffeners according to some embodiments of the present disclosure. Wherein the stiffener 120 in fig. 25A is rectangular in shape, the annular structure 122 is a single ring rectangular structure, and the bar-shaped structure 124 is a trapezoid structure; the stiffener 120 in fig. 21B is rectangular in shape, the annular structure 122 is a double-ring rectangular structure, and the bar-shaped structure 124 is a trapezoid structure; the stiffener 120 in fig. 21C has a hexagonal shape, the annular structure 122 has a single ring hexagonal structure, and the bar-shaped structure 124 has a trapezoidal structure. In some embodiments, the shape of the stiffener 120 of the vibration assembly 100 may match the shape of the resilient element 110. The elastic member 110 may have various structures, such as a circle, a square, a polygon, etc. The shape of the corresponding stiffener 120 may also be designed in different shapes including, but not limited to, circular, square (e.g., rectangle, square), triangular, hexagonal, octagonal, other polygonal, oval, and other irregular configurations.

The reinforcing members 120 of different shapes and the elastic members 110 of different shapes can be flexibly designed to change the mass and rigidity of the reinforcing members 120, the mass and rigidity of the vibration assembly 100, etc., thereby changing the resonant frequency of the vibration assembly 100.

In some embodiments, the shape of the stiffener 120 and the shape of the elastic element 110 may each comprise a variety of different shapes, where different widths, different shapes may be designed for the laterally extending strip-shaped structures 124 of the central region 112; the annular structure 122 can also be designed, and annular structures 122 with different shapes, numbers and sizes can be designed, and the annular structure 122 can be designed into a whole annular shape or can be designed into a partial annular structure 122; the different annular structures 122 divide the strip-shaped structures 124 into different regions, and the strip-shaped structures 124 may be continuous, staggered, and equal in number or unequal in different regions from the center to the periphery. In some embodiments, the annular structure 122 may also be designed as a circle, square (e.g., rectangle, square), triangle, hexagon, octagon, other polygons, oval, and other irregular structures.

In some embodiments, the vibration assembly 100 including differently shaped stiffeners 120 may be designed such that the fourth resonance peak of the vibration assembly 100 is in the range of 10kHz-18 kHz; the ratio of the area Si of each hollowed-out area to the thickness Hi of the elastic element 110 of each hollowed-out area is 150mm-700mm; suspended area S of any two elastic elements 110 _ki And S is equal to _ji The ratio gamma is in the range of 0.25-4; the ratio beta of the area of the hollowed-out area to the transverse area of the reinforcement 120 is 0.2-0.7. In some embodiments, the vibration assembly 100 including differently shaped stiffeners 120 may be designed such that the fourth resonance peak of the vibration assembly 100 is in the range of 10kHz-18 kHz; the ratio of the area Si of each hollowed-out area to the thickness Hi of the elastic element 110 of each hollowed-out area is 100mm-1000mm; suspended area S of any two elastic elements 110 _ki And S is equal to _ji The ratio gamma is in the range of 0.1-10; the ratio beta of the area of the hollowed-out area to the transverse area of the reinforcement 120 is 0.1-0.8.

26A-26D, FIGS. 26A-26D illustrate structures of vibration assembly 100 including a partial mass structure according to some embodiments of the present disclosureSchematic diagram. Wherein fig. 26A shows a double elastically connected partial mass structure 126, fig. 26B shows a four elastically connected partial mass structure 126, fig. 26C shows an S-shaped four elastically connected partial mass structure 126, and fig. 26D shows an S-shaped four elastically connected irregular partial mass structure 126. In some embodiments, the local mass structure 126 may be designed in the suspended area of the central area 112, so as to flexibly adjust the equivalent mass Mm of each hollow area _i Equivalent stiffness Ka _i And Ka _i ' equivalent damping Ra _i And (3) with Ra (Ra) _i ' so that the fourth resonance peak of the vibration assembly 100 is effectively tuned. By designing the local mass structure 126, the mass and stiffness of the stiffener 120 can also be adjusted over a wide range, thereby adjusting the first and third resonant peaks of the vibration assembly 100.

In some embodiments, the partial mass structures 126 may be circumferentially connected to the adjacent strip-shaped structures 124 by dual elastic structures (as shown in fig. 26A) or may be circumferentially connected to the adjacent ring-shaped structures 122 by dual elastic structures. In other embodiments, each partial mass structure 126 may also be unconnected to either the bar structure 124 or the loop structure 122, and connected only to the elastic element 110. In some embodiments, the partial mass structure 126 may also be connected to the elastic element 110 in part and to the annular structure 122 and/or the strip-shaped structure 124 in another part.

In some embodiments, the partial mass structure 126 may also be connected to both the adjacent strip structure 124 and the ring structure 122 by four elastic structures (as shown in fig. 26B).

In some embodiments, the planar shape of the elastic structure may be regular (as shown in fig. 26A and 26B) or irregular (as shown in fig. 26C).

In some embodiments, the local mass structure 126 may be regular (as shown in fig. 26A-26C) or any irregular (as shown in fig. 26D).

In some embodiments, the elastic attachment structure size, location, number, shape may be made by designing the size, location, number, shape of the partial mass structure 126The fourth resonance peak of the vibration assembly 100 is located in the range of 10kHz-18 kHz; area S of each hollowed-out area _i Thickness H of the elastic element 110 corresponding to each hollowed-out region _i The ratio is the area thickness ratio mu and the range is 150mm-700mm; suspended area S of any two elastic elements 110 _ki And S is equal to _ji The ratio gamma is in the range of 0.25-4; the ratio beta of the area of the hollowed-out area to the transverse area of the reinforcement 120 is 0.2-0.7. In some embodiments, the fourth resonant peak of vibration assembly 100 can be located in the range of 10kHz-18kHz by designing the size, location, number, shape of local mass structures 126, the size, location, number, shape of elastic connection structures; area S of each hollowed-out area _i Thickness H of the elastic element 110 corresponding to each hollowed-out region _i The ratio is the area thickness ratio mu and the range is 100mm-1000mm; suspended area S of any two elastic elements 110 _ki And S is equal to _ji The ratio gamma is in the range of 0.1-10; the ratio beta of the area of the hollowed-out area to the transverse area of the reinforcement 120 is 0.1-0.8.

Fig. 26E is a schematic cross-sectional structure of a stiffener according to some embodiments of the present description. As shown in fig. 26E, the reinforcement 120 may include a center connection portion 123, a reinforcement portion 125, and a hollowed-out portion 127. In some embodiments, the hollowed-out portion 127 may be obtained by carving out a portion of the material on the reinforcing member 120, and the portion of the reinforcing member 120 that is not carved out constitutes the reinforcing portion 125. In some embodiments, hollowed-out portion 127 may be configured as a circle. In some embodiments, hollowed-out portion 127 may also be configured in other shapes. In some embodiments, the central connection 123 and the reinforcing portion 125 have different thicknesses along the vibration direction of the elastic element 110. In some embodiments, the thickness of the central connection portion 123 in the vibration direction of the elastic element 110 may be greater than the thickness of the reinforcement portion 125 in the vibration direction of the elastic element 110.

The embodiment of the specification also provides a loudspeaker, which is provided with the vibration component provided by the embodiment of the specification, and the structure and parameters of the vibration component (such as an elastic element and a reinforcing piece) are reasonably arranged, so that the loudspeaker has a plurality of resonance peaks in an audible range of human ears (such as 20kHz-20 kHz), thereby improving the frequency band and the sensitivity of the loudspeaker and improving the sound pressure level of the loudspeaker output.

Fig. 27 is an exemplary block diagram of a speaker shown in accordance with some embodiments of the present description. In some embodiments, referring to fig. 27, a speaker 2700 can include a housing 2730, a drive assembly 2720, and a vibration assembly 2710 described above. Wherein the driving assembly 2720 is capable of generating vibrations based on the electrical signal, and the vibration assembly 2710 is capable of receiving the vibrations of the driving assembly 2720 to generate vibrations. The housing 2730 forms a cavity within which the drive assembly 2720 and the vibration assembly 2710 are disposed. Here, the structure of the vibration assembly 2710 may be the same as any of the vibration assemblies in the embodiments of the present specification.

In some embodiments, the vibration assembly 2710 mainly includes a resilient element 2711 and a stiffener 2712. The elastic element 2711 mainly includes a central region 2711A, a ring-folded region 2711B disposed at the periphery of the central region 2711A, and a fixing region 2711C disposed at the periphery of the ring-folded region 2711B. The elastic element 2711 is configured to vibrate in a direction perpendicular to the central region 2711A. The stiffener 2712 is connected to the central region 2711A. The stiffening member 2712 includes a stiffening portion and a plurality of hollowed-out portions, and vibration of the stiffening member 2712 and the elastic element 2711 produces at least two resonance peaks in the audible range of the human ear (20 Hz-20 kHz).

The drive assembly 2720 may be an acoustic device with energy conversion functionality. In some embodiments, the drive assembly 2720 may be electrically connected to other components of the speaker 2700 (e.g., a signal processor) to receive electrical signals and convert the electrical signals to mechanical vibration signals, which may be transferred to the vibration assembly 2710 to cause the vibration assembly 2710 to vibrate, thereby pushing air within the cavity to vibrate, producing sound.

In some embodiments, the drive assembly 2720 may include a drive unit 2722 and a vibration transfer unit 2724. Among other things, the driving unit 2722 may be electrically connected with other components (e.g., a signal processor) of the speaker 2700 to receive an electrical signal and convert the electrical signal into a mechanical vibration signal. The vibration transmission unit 2724 is connected between the driving unit 2722 and the vibration assembly 2710, and is used for transmitting a vibration signal generated by the driving unit 2722 to the vibration assembly 2710.

In some embodiments, the drive unit 2722 may include, but is not limited to, a moving coil acoustic driver, a moving iron acoustic driver, an electrostatic acoustic driver, or a piezoelectric acoustic driver. In some embodiments, a moving coil acoustic driver may include a magnetic member that generates a magnetic field and a coil disposed in the magnetic field that, when energized, may generate vibrations in the magnetic field to convert electrical energy to mechanical energy. In some embodiments, the moving iron acoustic driver may include a coil generating an alternating magnetic field and a ferromagnetic member disposed in the alternating magnetic field, the ferromagnetic member generating vibrations under the influence of the alternating magnetic field to convert electrical energy into mechanical energy. In some embodiments, the electrostatic acoustic driver may drive the diaphragm to vibrate through an electrostatic field disposed inside the driver, thereby converting electrical energy into mechanical energy. In some embodiments, the piezoelectric acoustic driver may convert electrical energy into mechanical energy by the electrostrictive effect of the piezoelectric material disposed therein.

In some embodiments, the driving unit 2722 and the vibration transmitting unit 2724 may be located at the same side of the vibration direction of the vibration assembly. In some embodiments, one end of the vibration transmission unit 2724 in the vibration direction of the central region 2711A is connected to the driving unit 2722, and the other end of the vibration transmission unit 2724 remote from the driving unit 2722 may be connected to the central region 2711A of the vibration assembly 2710. In other embodiments, the stiffener 2712 may include a center connector 27121, with the center connector 27121 covering the center of the center region 2711A. In some embodiments, the other end of the vibration transfer unit 2724 remote from the driving unit 2722 may be directly connected to the central connection portion 27121, i.e., the vibration transfer unit 2724 is connected to the central region 2711A through the central connection portion 27121. In some embodiments, the other end of the vibration transfer unit 2724 remote from the driving unit 2722 may be indirectly connected to the central connection portion 27121, i.e., the vibration transfer unit 2724 is directly connected to the central region 2711A and is connected to the central connection portion 27121 through the central region 2711A. In some embodiments, the size of the vibration transfer unit 2724 may be the same or substantially the same as the size of the center connection 27121 (e.g., within 10% of the difference in size).

In some embodiments, the center of the end of the vibration transmission unit 2724 connected to the central region 2711A coincides or substantially coincides with the projection of the center of the central region 2711A in the vibration direction of the elastic element 2711, and by such an arrangement, on the one hand, uniformity and stability of vibration of the elastic element 2711 can be improved, and on the other hand, the third resonance peak of the output of the speaker 2700 can be controlled to be within the frequency range (for example, 5000Hz to 12000 Hz) described in the embodiments of the present specification. In the present embodiment, substantially overlapping means that the distance between the center of the end of the vibration transmission unit 2724 connected to the center region 2711A and the center of the center region 2711A is not more than 5% of the diameter of the center region 2711A. In other embodiments, when the vibration transmitting unit 2724 is connected to the central region 2711A through the central connecting portion of the reinforcement 2712, since the size of the vibration transmitting unit 2724 is matched with (e.g., the same as) the size of the central connecting portion, the center of the end of the vibration transmitting unit 2724 connected to the central connecting portion coincides with or substantially coincides with the center of the central connecting portion 27121, and at this time, the center of the central connecting portion may also coincide with or substantially coincides with the projection of the center of the central region 2711A in the vibration direction of the elastic element 2711. For details of the central connection portion of the reinforcement members 2712, reference may be made to the description of the central connection portion 123 of the reinforcement member 120.

In some embodiments, the vibration assembly 2710 is capable of receiving force and displacement transferred by the vibration transfer unit 2724 to push air into motion, producing sound. In some embodiments, the structure of the vibration assembly 2710 may be identical to the vibration assembly 100.

In some embodiments, the ring-folded region 2711B may be designed with a pattern of a characteristic shape, so as to break the vibration mode of the ring-folded region 2711B of the elastic element 2711 at a corresponding frequency segment, avoid the occurrence of acoustic cancellation caused by the local split vibration of the elastic element 2711, and enable the vibration component 2710 to have a flatter sound pressure level curve. While the local stiffness of the elastic element 2711 is increased by the design of the pattern.

In some embodiments, the mode shape of the vibration assembly 2710 can be adjusted by adjusting the structure of the stiffener 2712.

In some embodiments, the stiffener 2712 comprises one or more annular structures and one or more bar structures, each of the one or more bar structures being connected to at least one of the one or more annular structures; wherein at least one of the one or more bar structures extends toward the center of the central region 2711A. The region where the one or more annular structures are located and the region where the one or more strip-like structures are located together constitute a reinforcing portion. The one or more annular structures and the uncovered area of the one or more bar-shaped structures form a hollowed-out portion within the projection range of the maximum profile of the reinforcement 2712 along the vibration direction of the elastic element 2711. For details of the annular structure and the bar-shaped structure of the reinforcement 2712, reference may be made to the description of the annular structure and the bar-shaped structure elsewhere in this specification.

In some embodiments, by reasonably arranging the reinforcing members 2712, arranging a plurality of hollowed-out areas in the central area 2711A enables the local rigidity of the central area 2711A of the elastic element 2711 to be controllably adjusted, so that the split vibration modes of each hollowed-out area of the central area 2711A of the elastic element 2711 of the vibration component 2710 are utilized to enable the resonance peak output by the vibration component 2710 to be controllably adjusted, and the vibration component 2710 has a flatter sound pressure level curve. In some embodiments, the annular structure and the bar structure cooperate such that the stiffener 2712 has a proper ratio of stiffener portion and hollowed portion (i.e., hollowed portion), reducing the mass of the stiffener 2712 and improving the overall sensitivity of the vibration assembly 2710. In some embodiments, by designing the shape, size, and number of annular structures and bar structures, the position and bandwidth of the multiple resonance peaks (e.g., third resonance peak, fourth resonance peak, etc.) of the vibration assembly 2710 can be adjusted to control the vibration output of the vibration assembly 2710.

In some embodiments, the mass of the stiffener 2712, the mass of the elastic element 2711, the equivalent air mass, and the equivalent mass of the drive end combine to form a total equivalent mass Mt, the partial equivalent damping forms a total equivalent damping Rt, the elastic element 2711 provides stiffness Kt to the system, forming a mass Mt-spring Kt-damping Rt system, and when the excitation frequency of the drive assembly 2720 approaches the resonance frequency of the system, a resonance peak appears in the frequency response curve of the vibration assembly 2710, i.e., the first resonance peak of the vibration assembly 2710. In some embodiments, the frequency range of the first resonant peak includes 180Hz-3000Hz. In some embodiments, the frequency range of the first resonant peak includes 200Hz-3000Hz. In some embodiments, the frequency range of the first resonant peak includes 200Hz-2500Hz. In some embodiments, the frequency range of the first resonant peak includes 200Hz-2000Hz. In some embodiments, the frequency range of the first resonant peak includes 200Hz-1000Hz.

In some embodiments, the gimbal region 2711B, the connecting region 2711D, and the suspended region 2711E between the region in which the stiffener 2712 is disposed in the center region 2711A and the gimbal region 2711B form an equivalent mass Ms, an equivalent stiffness Ks, and an equivalent damping Rs, forming a mass Ms-spring Ks-damping Rs system, and when the excitation frequency of the driving element 2720 approaches the resonance frequency of the system, one resonance peak appears in the frequency response curve of the vibration element 2710, i.e., the second resonance peak of the vibration element 2710. In some embodiments, the frequency range of the second resonant peak of vibration assembly 2710 may include 3000Hz-7000Hz. In some embodiments, the frequency range of the second resonant peak of vibration assembly 2710 may include 3000Hz-6000Hz. In some embodiments, the frequency range of the second resonant peak of vibration assembly 2710 may include 4000Hz-6000Hz. In some embodiments, the second resonance peak of the vibration component 2710 can be located in the above frequency range by setting the parameters of the elastic element 2711 (e.g., the parameters of the folded ring region 2711B and the suspended region 2711E).

In some embodiments, the reinforcement members 2712, the connection regions 2711D, the collar regions 2711B, the central region 2711A, the suspended region 2711E between the region where the reinforcement members 2712 are disposed and the collar regions 2711B, the equivalent air mass, the equivalent mass of the drive assembly 2720 combine to form a total equivalent mass Mt ₁ The equivalent damping of each part forms the total equivalent damping Rt ₁ The stiffener 2712, resilient element 2711 provide stiffness Kt to the system ₁ Forming a mass Mt ₁ Spring Kt ₁ Damping Rt ₁ System, when driving assembly 2720 near the system's velocity resonance frequency, one resonance peak appears in the vibration assembly 2710 frequency response curve, i.e., the third resonance peak of the vibration assembly 2710. In some embodiments, the frequency range of the third resonance peak may include 5000Hz-12000Hz. In some embodiments, the frequency range of the third resonance peak may include 6000Hz-12000Hz. In some embodiments, the frequency range of the third resonance peak may include 6000Hz-10000Hz.

In some embodiments, the stiffener 2712 has no less than one hollowed-out region corresponding to the central region 2711A, and each hollowed-out region with a different resonant frequency vibrates, such that there are no less than 1 high frequency resonance peaks on the frequency response curve of the vibration component 2710. In some embodiments, by designing the structure of the reinforcement member 2712, the resonance frequencies of the hollow areas can be equal or close (for example, the difference is smaller than 4000 Hz), so that a high-frequency resonance peak with a larger output sound pressure level is formed on the frequency response curve of the vibration component 2710, namely, the fourth resonance peak of the vibration component 2710. In some embodiments, the frequency range of the fourth resonance peak may include 8000Hz-20000Hz. In some embodiments, the frequency range of the fourth resonance peak may include 10000Hz-18000Hz. In some embodiments, the frequency range of the fourth resonance peak may include 12000Hz-18000Hz. In some embodiments, the frequency range of the fourth resonance peak may include 15000Hz-18000Hz. In other embodiments, the frequency range of the fourth resonance peak may also be greater than 20000Hz. In other embodiments, the resonance frequencies of the hollow areas are different, and the vibration phases of the hollow areas are different in different frequency ranges (e.g., 8000Hz-20000 Hz), so that the effect of sound superposition cancellation is formed, and the vibration component 2710 can not output the fourth resonance peak.

In some embodiments, by designing the structure of vibration assembly 2710, speaker 2700 can be made to exhibit 2, 3, or 4 resonant peaks in the audible range of the human ear (e.g., 20Hz-20 kHz).

In some embodiments, the frequency difference between the second and third resonance peaks of vibration assembly 2710 can be designed by designing the structure and dimensions of vibration assembly 2710, including the overall dimensions of reinforcement 2712, the number and dimensions of the bar structures, the placement of the bar structures, the area of suspended region 2711E, the structure of collar region 2711B (e.g., width of collar, height of collar, arch, pattern, etc.), and the area of connection region 2711D. In some embodiments, when the frequency difference between the second resonance peak and the third resonance peak of the vibration component 2710 is less than 2000Hz, the second resonance peak and the third resonance peak tend to be combined, i.e. the second resonance peak and the third resonance peak are embodied as one resonance peak, so that the middle-high frequency band (3000 Hz-10000 Hz) has higher sensitivity, and the bandwidth of the combined resonance peak can be greatly improved. In some embodiments, the frequency range of the fourth resonance peak may be greater than 20000Hz, i.e. without the fourth resonance peak in the audible range of the human ear. In some embodiments, when the second and third resonant peaks have a frequency difference of less than 2000Hz and do not have a fourth resonant peak in the audible range of the human ear, the vibration component 2710 vibrates with and only 2 resonant peaks in the audible range of the human ear, and wherein the 3dB bandwidth of at least one of the resonant peaks is not less than 1000Hz. Where the 3dB bandwidth refers to the width of the frequency band (e.g., the abscissa in fig. 7D) corresponding to the sound pressure level amplitude (e.g., the ordinate in fig. 7D) corresponding to the resonance peak reduced by 3 dB. In some embodiments, the 3dB bandwidth of at least one resonance peak in the audible range of the human ear is not less than 1500Hz when the vibration assembly 2710 vibrates. In some embodiments, the 3dB bandwidth of at least one resonance peak in the audible range of the human ear is not less than 1000Hz when the vibration assembly 2710 vibrates. In some embodiments, the 3dB bandwidth of at least one resonance peak in the audible range of the human ear is not less than 500Hz when the vibration assembly 2710 vibrates.

In some embodiments, by the design of the reinforcement members 2712 and the elastic members 2711, the vibration assembly 2710 can be made to exhibit a desired high order mode in the audible sound range (20 Hz-20000 Hz), with the above-described first, second, third and fourth resonance peaks appearing on the frequency response curve of the vibration assembly 2710, i.e., 4 resonance peaks in the frequency response curve of the vibration assembly 2710 in the frequency range of 20Hz-20000 Hz.

In some embodiments, by designing the structure of the stiffener 2712 and the resilient element 2711, the vibration assembly 2710 may also have and only have 3 resonant peaks in the audible range of the human ear (20 Hz-20000 Hz). For example, when the frequency difference between the second resonance peak and the third resonance peak of the vibration component 2710 is smaller than 2000Hz, the second resonance peak and the third resonance peak are embodied as one resonance peak on the vibration component 2710 frequency-ringing voltage level curve, and form 3 resonance peaks of the vibration component 2710 in the human ear audible range (20 Hz-20000 Hz) together with the first resonance peak and the fourth resonance peak. For another example, the reinforcement member 2712 has at least one suspended area corresponding to the central area 2711A, when the resonance frequency of each hollow area is higher than the audible sound range, or the resonance frequency of each hollow area is different, and the vibration phases of different suspended areas in different frequency ranges of the high frequency range (10000 Hz-18000 Hz) are different, so as to form the effect of sound superposition cancellation, the effect of high frequency roll-off can be obtained, the fourth resonance peak is not reflected in the sound pressure level frequency response curve of the vibration component 2710, and at this time, the first resonance peak, the second resonance peak and the third resonance peak form 3 resonance peaks of the vibration component 2710 in the audible human ear range (20 Hz-20000 Hz).

In some embodiments, not only the frequencies of the plurality of resonance peaks, but also the 3dB bandwidths of the plurality of resonance peaks (e.g., the third resonance peak) and the Q-value of the speaker can be adjusted by designing the structures of the reinforcement member 2712 or the elastic member 2711.

In some embodiments, the 3dB bandwidth of the third resonance peak output by the speaker 2700 and the Q value of the speaker 2700 can be adjusted by designing the angle θ between both sides of the projected shape of the bar-shaped structure in the vibration direction. In some embodiments, the angle θ of the bar-shaped structures may have a larger value when the speaker 2700 is required to exhibit a low Q and wide bandwidth frequency response characteristic. In some embodiments, the included angle θ of the bar-shaped structures may range from-90 ° to 150 °, such that the speaker 2700 has a lower Q value, and the 3dB bandwidth of the third resonance peak output by the speaker 2700 is not less than 1000Hz. In some embodiments, the included angle θ of the bar-shaped structures may range from-0 ° to 60 °, such that the speaker 2700 has a lower Q value, and the 3dB bandwidth of the third resonance peak output by the speaker 2700 is not less than 1000Hz.

In some embodiments, the included angle θ of the bar-shaped structures may be designed to be smaller when the speaker 2700 is required to exhibit high Q and narrow bandwidth frequency response characteristics. In some embodiments, the included angle θ of the bar-shaped structures may range from-150 ° to 90 °, such that the speaker 2700 has a higher Q value, and the 3dB bandwidth of the third resonance peak output by the speaker 2700 is no greater than 1000Hz. In some embodiments, the included angle θ of the bar-shaped structures may range from-60 ° to 0 °, such that the speaker 2700 has a higher Q value, and the 3dB bandwidth of the third resonance peak output by the speaker 2700 is not greater than 1000Hz.

In some embodiments, by designing the area ratio of the inner side and the outer side of the half-profile of the projected shape of the reinforcement member 2712 in the vibration direction of the elastic member 2711 to be τ, the 3dB bandwidth of the third resonance peak output by the speaker 2700 and the Q value of the speaker 2700 can be adjusted. When the speaker 2700 is required to exhibit a low Q and wide bandwidth frequency response characteristic, a larger mass can be designed to concentrate on the center region of the stiffener 2712. In some embodiments, the area ratio τ of the inner and outer sides of the projected shape of the stiffener 2712 along the vibration direction of the resilient element 2711 may range from 0.3 to 2 such that the speaker 2700 has a lower Q value and the 3dB bandwidth of the third resonance peak output by the speaker 2700 is not less than 1000Hz. In some embodiments, the area ratio τ of the inner and outer sides of the projected shape half-profile of the stiffening member 2712 along the vibration direction of the elastic element 2711 may range from 0.5 to 1.2 such that the speaker 2700 has a lower Q value and the 3dB bandwidth of the third resonance peak output by the speaker 2700 is not less than 1000Hz. When the speaker 2700 is required to exhibit a high Q-value and narrow bandwidth frequency response characteristic, a larger mass can be designed to concentrate on the edge region of the stiffener 2712. In some embodiments, the area ratio τ of the inner and outer sides of the projected shape of the stiffener 2712 along the vibration direction of the resilient element 2711 may range from 1 to 3 such that the speaker 2700 has a higher Q value and the 3dB bandwidth of the third resonance peak output by the speaker 2700 is not greater than 1000Hz. In some embodiments, the area ratio τ of the inner and outer sides of the projected shape half-profile of the stiffening member 2712 along the vibration direction of the resilient element 2711 may range from 1.2 to 2.8 such that the speaker 2700 has a higher Q and the 3dB bandwidth of the third resonance peak output by the speaker 2700 is no greater than 1000Hz.

In some embodiments, at least one of the one or more bar structures has a plurality of steps having different thicknesses along the vibration direction of the elastic element 2711, the steps including a first step located radially outermost of the bar structure and a second step located radially innermost of the bar structure. In some embodiments, the 3dB bandwidth of the third resonance peak output by the speaker 2700 and the Q-value of the speaker 2700 can be adjusted by designing the thickness ratio Φ of the first step and the second step. When the speaker 2700 is required to exhibit a low Q-value wide bandwidth frequency response characteristic, a larger mass can be designed to concentrate on a position near the center of the reinforcement 2712. In some embodiments, the thickness ratio of the first step and the second step, φ, ranges from 0.1 to 1, such that the speaker 2700 has a lower Q value and the 3dB bandwidth of the third resonance peak output by the speaker 2700 is not less than 1000Hz. In some embodiments, the thickness ratio of the first step and the second step, φ, ranges from 0.2 to 0.8, such that speaker 2700 has a low Q value and the 3dB bandwidth of the third resonance peak output by speaker 2700 is not less than 1000Hz. When the speaker 2700 is required to exhibit a high Q-value and narrow bandwidth frequency response characteristic, a larger mass can be designed to concentrate on the edge region of the stiffener 2712. In some embodiments, the thickness ratio of the first step and the second step, φ, ranges from 1 to 10, such that the speaker 2700 has a higher Q value and the 3dB bandwidth of the third resonance peak output by the speaker 2700 is no greater than 1000Hz. In some embodiments, the thickness ratio of the first step and the second step, φ, ranges from 1.2 to 6, such that the speaker 2700 has a higher Q value and the 3dB bandwidth of the third resonance peak output by the speaker 2700 is no greater than 1000Hz.

In some embodiments, housing 2730 may be a regular or irregular three-dimensional structure that is hollow inside (i.e., provided with cavities), for example, housing 2730 may be a hollow frame structure including, but not limited to, regular shapes such as rectangular frames, circular frames, regular polygonal frames, and any irregular shape. In some embodiments, housing 2730 may be made of metal (e.g., stainless steel, copper, etc.), plastic (e.g., polyethylene (PE), polypropylene (PP), polyvinyl chloride (PVC), polystyrene (PS), acrylonitrile-butadiene-styrene copolymer (ABS), etc.), composite materials (e.g., metal matrix composite materials or non-metal matrix composite materials), etc. In some embodiments, the drive assembly 2720 may be located within an acoustic cavity formed by the housing 2730 or at least partially suspended within the acoustic cavity of the housing 2730.

In some embodiments, the circumferential side of the elastic element 2711 may be connected with the inner wall of the housing 2730, thereby dividing the cavity formed by the housing 2730 into a plurality of cavities. Specifically, the elastic element 2711 is bounded by the elastic element 2711 along its vibration direction, dividing the inner cavity of the housing 2730 into a front cavity 2731 and a rear cavity 2733, which are located on both sides of the elastic element 2711, respectively. In some embodiments, the front cavity 2731 is located on a side of the elastic element 2711 remote from the drive unit 2722.

In some embodiments, the rear cavity 2733 is located on a side of the elastic element 2711 near the drive unit 2722, i.e., the drive assembly 2720 may be disposed in the rear cavity 2733.

In some embodiments, one or more holes may be formed in the side walls of the housing 2730 corresponding to the front and rear chambers 2731, 2733. Illustratively, a first hole 2732 is provided in the housing 2730 on a side of the front cavity 2731 remote from the elastic element 2711, and the front cavity 2731 communicates with the outside of the speaker 2700 through the first hole 2732; the housing 2730 of the rear chamber 2733 remote from the elastic element 2711 is provided with a second hole portion 2734, and the rear chamber 2733 communicates with the outside of the speaker 2700 through the second hole portion 2734. The sound generated by the vibration assembly 2710 may radiate to the front cavity 2731 and/or the rear cavity 2733 and be transmitted to the exterior of the speaker 2700 through the first hole portion 2732 and/or the second hole portion 2734 on the housing 2730.

In some embodiments, a damping mesh or dust cloth (e.g., damping mesh 27341) may be disposed over one or more of the aperture portions (e.g., second aperture portion 2734). In some embodiments, the damping mesh may adjust (e.g., reduce) the amplitude of sound waves leaking from the aperture, thereby improving the performance of the speaker 2700.

In some embodiments, speaker 2700 can further include support element 2740, support element 2740 being coupled to housing 2730 and fixed region 2711C, respectively. In some embodiments, referring to fig. 27, the securing region 2711C of the elastic element 2711 of the vibration assembly 2710 is located at the periphery of the connecting region 2711D and surrounds the circumference side of the connecting region 2711D. The support member 2740 may be located at any surface of the fixing region 2711C along the vibration direction of the central region 2711A and connected to the connection region 2711D through the fixing region 2711C.

In some embodiments, a support element 2740 may be embedded in an inner wall of the housing 2730 and connected with the housing 2730 to support the elastic element 2711. When the support member 2740 is embedded in the inner wall of the housing 2730, a hole matching with the support member 2740 may be provided on the inner wall of the housing 2730, so that the support member 2740 may be placed in the hole, so as to implement the embedding of the support member 2740.

In some embodiments, referring to fig. 27, a supporting member 2740 may also be disposed in a cavity formed by the housing 2730, and the supporting member 2740 is connected with the housing 2730 along a lower surface (a surface close to the driving unit 2722) or a circumferential side of the vibration assembly 2710 in a vibration direction to support the elastic member 2711. In some embodiments, when the support element 2740 is disposed within the cavity formed by the housing 2730, the inner wall of the housing 2730 may be configured to have a protruding structure that mates with the support element 2740 such that the support element 2740 may be disposed on a surface of the protruding structure in the vibration direction to enable connection of the support element 2740 to the housing 2730. In this arrangement, by disposing the support member 2740 in the cavity formed by the housing 2730, the support member 2740 is prevented from being scratched and damaged during use of the speaker 2700, and thus the speaker 2700 (particularly the vibration assembly 2710) is prevented from being damaged.

In some embodiments, support element 2740 may be a rigid structure that is not easily deformed, providing support only to elastic element 2711 during vibration of vibration assembly 2710. In some embodiments, to further reduce the system stiffness of the vibration assembly 2710 as it vibrates, to improve the compliance of the speaker 2700, the support element 2740 can be configured as a flexible structure that is easily deformed, providing an additional amount of displacement of the vibration assembly 2710 as it vibrates.

In some embodiments, the support element 2740 may deform in response to a vibration signal of the elastic element 2711, providing the elastic element 2711 with an amount of displacement along its vibration direction, thereby increasing the total amount of displacement of the elastic element 2711 in its vibration direction, further increasing the low frequency sensitivity of the vibration assembly 2710. In some embodiments, the material of the support element 2740 may include one or more of a rigid material, a semiconductor material, an organic polymer material, a glue material, and the like. In some embodiments, the rigid material may include, but is not limited to, a metallic material, an alloy material, and the like. The semiconductor material may include, but is not limited to, one or more of silicon, silicon dioxide, silicon nitride, silicon carbide, and the like. The organic polymer material may include, but is not limited to, one or more of Polyimide (PI), parylene (Parylene), polydimethylsiloxane (PDMS), hydrogel, and the like. The gum-type material may include, but is not limited to, one or more of gels, silicones, acrylics, urethanes, rubbers, epoxies, hot melts, photo-curing, and the like. In some embodiments, to enhance the connection force between the support element 2740 and the elastic element 2711 and improve the reliability between the support element 2740 and the elastic element 2711, the material of the support element 2740 may be a silicone adhesive glue, a silicone sealing glue, or the like. In some embodiments, the cross-sectional shape of support element 2740 in a cross-section parallel to the direction of vibration of the reinforced area may be a regular and/or irregular geometric shape such as a rectangle, circle, oval, pentagon, and the like. Meanwhile, by providing the support member 2740 with a flexible structure, not only can the vibration characteristics of the vibration assembly 2710 be changed, but also the elastic member 2711 can be prevented from directly contacting the housing 2730, and stress concentration at the connecting end of the elastic member 2711 and the housing 2730 (the housing is generally a rigid body) can be reduced, so that the elastic member 2711 can be further protected.

While the basic concepts have been described above, it will be apparent to those skilled in the art that the foregoing detailed disclosure is by way of example only and is not intended to be limiting. Although not explicitly described herein, various modifications, improvements and adaptations of the application may occur to one skilled in the art. Such modifications, improvements, and modifications are intended to be suggested within the present disclosure, and therefore, such modifications, improvements, and adaptations are intended to be within the spirit and scope of the exemplary embodiments of the present disclosure.

Meanwhile, the present application uses specific words to describe embodiments of the present application. Reference to "one embodiment," "an embodiment," and/or "some embodiments" means that a particular feature, structure, or characteristic is associated with at least one embodiment of the application. Thus, it should be emphasized and should be appreciated that two or more references to "an embodiment" or "one embodiment" or "an alternative embodiment" in various positions in this specification are not necessarily referring to the same embodiment. Furthermore, certain features, structures, or characteristics of one or more embodiments of the application may be combined as suitable.

Furthermore, those skilled in the art will appreciate that the various aspects of the application are illustrated and described in the context of a number of patentable categories or circumstances, including any novel and useful procedures, machines, products, or materials, or any novel and useful modifications thereof. Accordingly, aspects of the application may be performed entirely by hardware, entirely by software (including firmware, resident software, micro-code, etc.) or by a combination of hardware and software. The above hardware or software may be referred to as a "data block," module, "" engine, "" unit, "" component, "or" system. Furthermore, aspects of the application may take the form of a computer product, comprising computer-readable program code, embodied in one or more computer-readable media.

Claims

1. A vibration assembly, comprising:

an elastic element including a central region, a folded ring region disposed at a periphery of the central region, and a fixed region disposed at a periphery of the folded ring region, the elastic element being configured to vibrate in a direction perpendicular to the central region;

the reinforcing piece is connected with the central area and comprises a reinforcing part and a plurality of hollowed-out parts;

wherein the stiffener is configured such that the vibration assembly has at least a resonance peak at 10000Hz-18000Hz when vibrated.

2. The vibration assembly of claim 1, wherein a ratio of a projected area of at least one of the plurality of hollowed-out portions along a vibration direction of the elastic element to a thickness of the elastic element ranges from 1000mm to 10000mm.

3. The vibration assembly of claim 2, wherein a ratio of a projected area of at least one of the plurality of hollowed-out portions along a vibration direction of the elastic element to a thickness of the elastic element ranges from 4000mm to 6000mm.

4. The vibration assembly of claim 1, wherein the plurality of hollowed-out portions include a first hollowed-out portion and a second hollowed-out portion, a distance between the first hollowed-out portion and a center of the center area and a distance between the second hollowed-out portion and a center of the center area are different, and a ratio of projection areas of the first hollowed-out portion and the second hollowed-out portion along a vibration direction of the elastic element ranges from 0.1 to 10.

5. The vibration assembly of claim 4, wherein a ratio of projection areas of the first hollowed-out portion and the second hollowed-out portion along the vibration direction of the elastic element ranges from 0.25 to 4.

6. The vibration assembly of claim 1, wherein a ratio of a projected area of the reinforcement portion along the vibration direction of the elastic member to a projected area of a maximum profile of the reinforcement member along the vibration direction of the elastic member ranges from 0.1 to 0.8.

7. The vibration assembly of claim 6, wherein a ratio of a projected area of the reinforcement portion along the vibration direction of the elastic member to a projected area of the maximum profile of the reinforcement member along the vibration direction of the elastic member ranges from 0.1 to 0.5.

8. A vibration assembly as claimed in any one of claims 1 to 7, wherein the stiffening member comprises one or more annular structures and one or more bar-shaped structures; each of the one or more strip-shaped structures is connected with at least one of the one or more annular structures to form the reinforcing part and the hollowed-out part; at least one of the one or more bar structures extends toward the center of the central region.

9. The vibration assembly of claim 8, wherein the one or more annular structures comprise at least a first annular structure; the one or more bar structures comprise at least one first bar structure and at least one second bar structure; the at least one first strip-shaped structure and the inner side of the first annular structure are connected to a first position, and the at least one second strip-shaped structure and the outer side of the first annular structure are connected to a second position.

10. The vibration assembly of claim 9, wherein the first location, the second location, and a center of the first annular structure are non-collinear.

11. The vibration assembly of claim 8, wherein the vibration assembly further comprises a plurality of partial mass structures disposed in the hollowed-out portion.

12. The vibration assembly of claim 11, wherein at least one of the plurality of partial mass structures is connected to the reinforcing portion by one or more elastic connectors.

13. The vibration assembly of claim 11, wherein at least one of the plurality of partial mass structures is connected to the elastic element.

14. A speaker, comprising:

A driving assembly generating vibration based on an electrical signal;

a vibration assembly receiving vibration of the driving assembly to generate vibration;

wherein the vibration assembly comprises an elastic element and a stiffener;

the elastic element comprises a central area, a folding ring area arranged at the periphery of the central area and a fixing area arranged at the periphery of the folding ring area, and the elastic element is configured to vibrate along the direction perpendicular to the central area;

the reinforcing piece is connected with the central area and comprises a reinforcing part and a plurality of hollowed-out parts; the stiffener is configured such that the vibration assembly has at least a resonance peak at 10000Hz-18000Hz when vibrated.

15. The speaker of claim 14, wherein the speaker further comprises a housing forming a cavity, the drive assembly and the vibration assembly being disposed within the cavity.

16. The speaker of claim 15, further comprising a support element connected to the housing and the fixed region, respectively.