Vibration Assembly and Speaker

Abstract

One or more embodiments herein relate to a speaker including a drive assembly that vibrates based on an electrical signal, and a vibration assembly that vibrates in response to vibration from the drive assembly, the vibration assembly including an elastic element and a reinforcing member, the elastic element including a central region, an edge region located on an outer periphery of the central region, and a fixed region located on the outer periphery of the edge region, and configured to vibrate along a direction perpendicular to the central region, the reinforcing member connected to the central region and including a reinforcing portion and a plurality of openwork portions, and the vibration of the reinforcing member and the elastic element generates at least two resonant peaks within the audible range of the human ear.

Description

[Technical Field]

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

[0002] [Incorporated by reference] This application claims priority to International Application No. PCT / CN2022 / 081838, filed March 18, 2022, the contents of which are incorporated herein by reference. [Background technology]

[0003] A speaker typically consists of three main parts: a driver, a vibrating part, and a supporting part. The vibrating part is also the load part of the speaker and is mainly the diaphragm assembly. Given the driving force of the driver, a rational design of the vibrating part can achieve good mechanical impedance matching between the load end and the driving end of the speaker, thereby achieving high sound pressure levels and wide bandwidth output effects. Summary of the Invention

[0004] A speaker according to one aspect of the embodiments of the present specification includes a drive assembly that vibrates based on an electrical signal, and a vibration assembly that vibrates in response to vibration from the drive assembly, wherein the vibration assembly includes an elastic element and a reinforcing member, the elastic element includes a central region, an edge region located on the outer periphery of the central region, and a fixed region located on the outer periphery of the edge region, and is configured to vibrate along a direction perpendicular to the central region, the reinforcing member is connected to the central region and includes a reinforcing portion and a plurality of openwork portions, and the vibration of the reinforcing member and the elastic element produces at least two resonant peaks within the audible range of the human ear.

[0005] In some embodiments, the reinforcing member includes one or more annular structures and one or more elongated structures, each of the one or more elongated structures being connected to at least one of the one or more annular structures to form the reinforcing portion and the openwork portion, and at least one of the one or more elongated structures extending toward the center of the central region.

[0006] In some embodiments, a maximum area of ​​the projection of the one or more annular structures along the vibration direction of the elastic element is smaller than an area of ​​the central region.

[0007] In some embodiments, the number of the one or more elongated structures ranges from 1-100.

[0008] In some embodiments, the shape of the projection of the one or more elongated structures along the vibration direction of the elastic element comprises at least one of a rectangle, a trapezoid, a curved shape, an hourglass shape, and a petal shape.

[0009] In some embodiments, the number of the one or more cyclic structures is in the range of 1-10.

[0010] In some embodiments, the one or more annular structures include a first annular structure and a second annular structure, wherein a radial dimension of the first annular structure is smaller than a radial dimension of the second annular structure, and the first annular structure is disposed inside the second annular structure.

[0011] In some embodiments, the one or more elongated structures include at least one first elongated structure and at least one second elongated structure, wherein the at least one first elongated structure is located inside the first annular structure and connected to the first annular structure, and the at least one second elongated structure is located between the first annular structure and the second annular structure and connected to the first annular structure and the second annular structure, respectively.

[0012] In some embodiments, the at least one first elongate structure and the at least one second elongate structure have different connection locations on the first annular structure.

[0013] In some embodiments, at least one of the one or more elongated structures has a plurality of different thicknesses along a vibration direction of the elastic element.

[0014] In some embodiments, the shape of the one or more ring structures comprises at least one of a circular ring, an elliptical ring, a polygonal ring, and a curved ring.

[0015] In some embodiments, the elastic element further comprises a connection region located between the edge region and the fixing region.

[0016] In some embodiments, when the vibrating assembly vibrates, there are only two resonance peaks within the audible range of the human ear, and the 3 dB bandwidth of at least one resonance peak is 1000 Hz or greater.

[0017] In some embodiments, the resonant peaks include a first resonant peak in a frequency range of 200 Hz to 3000 Hz, a second resonant peak in a frequency range of 3000 Hz to 7000 Hz, and a third resonant peak in a frequency range of 5000 Hz to 12000 Hz.

[0018] In some embodiments, when the vibrating assembly vibrates, there are only three resonant peaks within the audible range of the human ear.

[0019] In some embodiments, one or more openwork regions are configured between the one or more annular structures and the one or more elongated structures, and the ratio of the area of ​​at least one of the one or more openwork regions to the thickness of the elastic element is in the range of 100 mm to 1000 mm, so that the resonant peaks include a fourth resonant peak in the frequency range of 10,000 Hz to 18,000 Hz.

[0020] In some embodiments, when the vibrating assembly vibrates, there are only four resonant peaks within the audible range of the human ear.

[0021] In some embodiments, when the vibrating assembly vibrates, the difference between the third resonance peak and the second resonance peak is less than 3000 Hz.

[0022] In some embodiments, the difference between the third resonant frequency and the second resonant frequency is less than 2000 Hz.

[0023] In some embodiments, one or more openwork areas are configured between the one or more annular structures and the one or more elongated structures, and the ratio of the area of ​​the one or more openwork areas to the thickness of the elastic element is in a range of less than 100 mm, so that the vibration of the reinforcing member and the elastic element generates a fourth resonant peak outside the audible range of the human ear.

[0024] In some embodiments, the drive assembly includes a drive unit and a vibration transmission unit, and one end of the vibration transmission unit along the vibration direction of the central region is connected to the drive unit and the other end is connected to the central region.

[0025] In some embodiments, the reinforcing member includes a central connection portion, and the vibration transmission unit is directly connected to the central connection portion and connected to the central region via the central connection portion, or the vibration transmission unit is directly connected to the central region and indirectly connected to the central connection portion via the central region.

[0026] In some embodiments, the center of the one end of the vibration transmission unit connected to the central region and the center of the central region overlap or nearly overlap when projected along the vibration direction of the elastic element.

[0027] In some embodiments, the speaker further comprises a housing defining a cavity, the drive assembly and the vibration assembly being located within the cavity.

[0028] In some embodiments, the loudspeaker further comprises a support element connected to the housing and the fastening area, respectively.

[0029] A vibration assembly according to another aspect of the present specification includes an elastic element including a central region, an edge region located on the outer periphery of the central region, and a fixed region located on the outer periphery of the edge region, and configured to vibrate along a direction perpendicular to the central region, and a reinforcing member connected to the central region and including a reinforcing portion and a plurality of openwork portions, wherein the reinforcing member is configured to have a resonance peak of at least 10,000 Hz to 18,000 Hz when the vibration assembly vibrates.

[0030] In some embodiments, the ratio of the projected area of ​​at least one of the plurality of openwork portions along the vibration direction of the elastic element to the thickness of the elastic element is in the range of 1000 mm to 10000 mm.

[0031] In some embodiments, the ratio of the projected area of ​​at least one of the plurality of openwork portions along the vibration direction of the elastic element to the thickness of the elastic element is in the range of 4000 mm to 6000 mm.

[0032] In some embodiments, the plurality of openwork portions include a first openwork portion and a second openwork portion, the distance between the first openwork portion and the center of the central region is different from the distance between the second openwork portion and the center of the central region, and the ratio of the projected areas of the first openwork portion and the second openwork portion along the vibration direction of the elastic element is in the range of 0.1 to 10.

[0033] In some embodiments, the ratio of the projected areas of the first openwork portion and the second openwork portion along the vibration direction of the elastic element is in the range of 0.25 to 4.

[0034] In some embodiments, the ratio of the projected area of ​​the reinforcing portion along the vibration direction of the elastic element to the projected area of ​​the maximum contour of the reinforcing member along the vibration direction of the elastic element is in the range of 0.1 to 0.8.

[0035] In some embodiments, the ratio of the projected area of ​​the reinforcing portion along the vibration direction of the elastic element to the projected area of ​​the maximum contour of the reinforcing member along the vibration direction of the elastic element is in the range of 0.1 to 0.5.

[0036] In some embodiments, the reinforcing member includes one or more annular structures and one or more elongated structures, each of the one or more elongated structures being connected to at least one of the one or more annular structures to form the reinforcing portion and the openwork portion, and at least one of the one or more elongated structures extending toward the center of the central region.

[0037] In some embodiments, the one or more annular structures include at least a first annular structure, and the one or more elongated structures include at least one first elongated structure and at least one second elongated structure, wherein the at least one first elongated structure and an inner side of the first annular structure are connected to a first location, and the at least one second elongated structure and an outer side of the first annular structure are connected to a second location.

[0038] In some embodiments, the first location, the second location and the center of the first annular structure are not collinear.

[0039] In some embodiments, the vibration assembly further comprises a plurality of local mass structures mounted in the openwork portion.

[0040] In some embodiments, at least one of the plurality of local mass structures is connected to the reinforcement portion via one or more elastic connecting members.

[0041] In some embodiments, at least one of the plurality of local mass structures is connected to the elastic element.

[0042] A speaker according to another aspect of an embodiment of the present specification includes a drive assembly that vibrates based on an electric signal, and a vibration assembly that vibrates in response to vibration from the drive assembly, wherein the vibration assembly includes an elastic element and a reinforcing member, the elastic element including a central region, an edge region located on the outer periphery of the central region, and a fixed region located on the outer periphery of the edge region, and is configured to vibrate along a direction perpendicular to the central region, the reinforcing member being connected to the central region and including a reinforcing portion and a plurality of openwork portions, and the reinforcing member being configured to have a resonance peak of at least 10,000 Hz to 18,000 Hz when the vibration assembly vibrates.

[0043] In some embodiments, the speaker further comprises a housing defining a cavity, the drive assembly and the vibration assembly being located within the cavity.

[0044] In some embodiments, the loudspeaker further comprises a support element connected to the housing and the fastening area, respectively.

[0045] Another aspect of the embodiments of the present specification provides a vibration assembly comprising an elastic element including a central region, an edge region located on the outer periphery of the central region, and a fixed region located on the outer periphery of the edge region, configured to vibrate along a direction perpendicular to the central region, and a reinforcing member having a projected area of ​​its maximum contour along the vibration direction that is smaller than the projected area of ​​the central region along the vibration direction, wherein the central region includes a suspension region located on the outer periphery of the reinforcing member, and the edge region and the suspension region are configured to have a resonance peak of at least 3000 Hz to 7000 Hz when the vibration assembly vibrates.

[0046] In some embodiments, the ratio of the sum of the projected area of ​​the suspension region along the vibration direction of the elastic element and the projected area of ​​the edge region along the vibration direction of the elastic element to the thickness of the elastic element is in the range of 5000 mm to 12000 mm.

[0047] In some embodiments, the ratio of the sum of the projected area of ​​the suspension region along the vibration direction of the elastic element and the projected area of ​​the edge region along the vibration direction of the elastic element to the thickness of the elastic element is in the range of 6000 mm to 10000 mm.

[0048] In some embodiments, the ratio of the sum of the projected area of ​​the suspension region along the vibration direction of the elastic element and the projected area of ​​the edge region along the vibration direction of the elastic element to the arch height of the edge of the edge region is in the range of 50 mm to 600 mm.

[0049] In some embodiments, the ratio of the sum of the projected area of ​​the suspension region along the vibration direction of the elastic element and the projected area of ​​the edge region along the vibration direction of the elastic element to the arch height of the edge of the edge region is in the range of 200 mm to 400 mm.

[0050] In some embodiments, the ratio of the projected area of ​​the suspension region along the vibration direction of the elastic element to the projected area of ​​the central region along the vibration direction of the elastic element is in the range of 0.05 to 0.7.

[0051] In some embodiments, the ratio of the projected area of ​​the suspension region along the vibration direction of the elastic element to the projected area of ​​the central region along the vibration direction of the elastic element is in the range of 0.15 to 0.35.

[0052] In some embodiments, the vibrating assembly, when vibrating, has a second resonant peak in the frequency range of 3000 Hz to 7000 Hz and a third resonant peak in the frequency range of 5000 Hz to 12000 Hz.

[0053] In some embodiments, the frequency difference between the third resonant peak and the second resonant peak is less than 3000 Hz.

[0054] A speaker according to another aspect of an embodiment of the present specification includes a drive assembly that vibrates based on an electric signal, and a vibration assembly that vibrates in response to vibration from the drive assembly, wherein the vibration assembly includes an elastic element and a reinforcing member, the elastic element including a central region, an edge region located on the outer periphery of the central region, and a fixed region located on the outer periphery of the edge region, and is configured to vibrate along a direction perpendicular to the central region, the projected area of ​​the maximum contour of the reinforcing member along the vibration direction is smaller than the projected area of ​​the central region along the vibration direction, the central region includes a suspension region located on the outer periphery of the reinforcing member, and the edge region and the suspension region are configured to have a resonance peak of at least 3000 Hz to 7000 Hz when the vibration assembly vibrates.

[0055] In some embodiments, the speaker further comprises a housing defining a cavity, the drive assembly and the vibration assembly being located within the cavity.

[0056] In some embodiments, the loudspeaker further comprises a support element connected to the housing and the fastening area, respectively.

[0057] Another aspect of the present invention provides a vibration assembly comprising an elastic element configured to vibrate along a direction perpendicular to the central region, the elastic element including a central region, an edge region located on the outer periphery of the central region, and a fixed region located on the outer periphery of the edge region, and the elastic element being configured to vibrate along a direction perpendicular to the central region, and a reinforcing member connected to the central region and including one or more annular structures and one or more elongated structures, each connected to at least one of the one or more annular structures, at least one of the one or more elongated structures extending toward the center of the central region, the reinforcing member being configured to have a resonant peak of at least 5000 Hz to 12000 Hz when the vibration assembly vibrates.

[0058] In some embodiments, the angle between two sides of the shape of the projection of at least one of the one or more elongated structures onto a projection plane perpendicular to the vibration direction is in the range of -150° to 150°.

[0059] In some embodiments, the area ratio between the inside and outside of a half outline of the shape of the reinforcement member projected onto a projection plane perpendicular to the vibration direction of the elastic element is in the range of 0.3-3.

[0060] In some embodiments, at least one of the one or more elongated structures has a plurality of steps with different thicknesses along the vibration direction of the elastic element.

[0061] In some embodiments, the ratio of the thickness of any two of the steps is in the range of 0.1-10.

[0062] In some embodiments, the ratio of the thickness of any two of the steps is in the range of 0.25-4.

[0063] In some embodiments, the one or more annular structures include at least a first annular structure and a second annular structure, wherein a radial dimension of the first annular structure is smaller than a radial dimension of the second annular structure, and the first annular structure is disposed inside the second annular structure.

[0064] In some embodiments, the ratio of the number of elongated structures connected to the inside of the first annular structure to the number of elongated structures connected to the inside of the second annular structure is in the range of 0.1-10.

[0065] In some embodiments, the ratio of the number of elongated structures connected to the inside of the first annular structure to the number of elongated structures connected to the inside of the second annular structure is in the range of 0.2 to 5.

[0066] In some embodiments, the shape of the projection of the one or more elongated structures onto a projection plane perpendicular to the vibration direction of the elastic element comprises at least one of a rectangle, a trapezoid, a curved shape, an hourglass shape, and a petal shape.

[0067] In some embodiments, the stiffening member includes a central connection that receives a vibration drive signal and transmits the vibration drive signal to the elastic element.

[0068] In some embodiments, the resonant peaks include a third resonant peak, and a 3 dB bandwidth of the third resonant peak is in the range of 1000 Hz or greater.

[0069] A speaker according to another aspect of an embodiment of the present specification includes a drive assembly that vibrates based on an electric signal, and a vibration assembly that vibrates in response to vibration from the drive assembly, wherein the vibration assembly includes an elastic element and a reinforcing member, wherein the elastic element includes a central region, an edge region located on the outer periphery of the central region, and a fixed region located on the outer periphery of the edge region, and is configured to vibrate along a direction perpendicular to the central region, the reinforcing member is connected to the central region and includes one or more annular structures and one or more elongated structures, each connected to at least one of the one or more annular structures, at least one of the one or more elongated structures extending toward the center of the central region, and the reinforcing member is configured to have a resonant peak of at least 5000 Hz to 12000 Hz when the vibration assembly vibrates.

[0070] In some embodiments, the angle between two sides of the shape of the projection of at least one of the one or more elongated structures onto a projection plane perpendicular to the vibration direction is in the range of -90° to 150°.

[0071] In some embodiments, the angle between two sides of the shape of the projection of at least one of the one or more elongated structures onto a projection plane perpendicular to the vibration direction is in the range of 0 to 60°.

[0072] In some embodiments, the angle between two sides of the shape of the projection of at least one of the one or more elongated structures onto a projection plane perpendicular to the vibration direction is in the range of -150° to 90°.

[0073] In some embodiments, the angle between two sides of the shape of the projection of at least one of the one or more elongated structures onto a projection plane perpendicular to the vibration direction is in the range of -60° to 0°.

[0074] In some embodiments, the area ratio between the inside and outside of a half contour of the shape of the reinforcement member projected onto a projection plane perpendicular to the vibration direction of the elastic element is in the range of 0.3-2.

[0075] In some embodiments, the area ratio between the inside and outside of a half outline of the shape of the reinforcement member projected onto a projection plane perpendicular to the vibration direction of the elastic element is in the range of 0.5 to 1.2.

[0076] In some embodiments, the area ratio between the inside and outside of a half contour of the shape of the reinforcement member projected onto a projection plane perpendicular to the vibration direction of the elastic element is in the range of 1-3.

[0077] In some embodiments, the area ratio between the inside and outside of a half contour of the shape of the reinforcement member projected onto a projection plane perpendicular to the vibration direction of the elastic element is in the range of 1.2 to 2.8.

[0078] In some embodiments, at least one of the one or more elongated structures has a plurality of steps of varying thickness along the vibration direction of the elastic element, the steps including a first step located at the radially outermost position of the elongated structure and a second step located at the radially innermost position of the elongated structure.

[0079] In some embodiments, the ratio of the thickness of the first step to the thickness of the second step is in the range of 0.1-1.

[0080] In some embodiments, the ratio of the thickness of the first step to the thickness of the second step is in the range of 0.2 to 0.8.

[0081] In some embodiments, the ratio of the thickness of the first step to the thickness of the second step is in the range of 1-10.

[0082] In some embodiments, the ratio of the thickness of the first step to the thickness of the second step is in the range of 1.2-6.

[0083] In some embodiments, the drive assembly includes a drive unit and a vibration transmission unit, and one end of the vibration transmission unit along the vibration direction of the central region is connected to the drive unit and the other end is connected to the central region.

[0084] In some embodiments, the reinforcing member includes a central connection portion, and the vibration transmission unit is directly connected to the central connection portion and connected to the central region via the central connection portion, or the vibration transmission unit is directly connected to the central region and indirectly connected to the central connection portion via the central region.

[0085] In some embodiments, the center of the one end of the vibration transmission unit connected to the central region and the center of the central region overlap or nearly overlap when projected along the vibration direction of the elastic element.

[0086] In some embodiments, the speaker further comprises a housing defining a cavity, the drive assembly and the vibration assembly being located within the cavity.

[0087] In some embodiments, the loudspeaker further comprises a support element connected to the housing and the fastening area, respectively.

[0088] The present application will be further illustrated by exemplary embodiments, which are illustrated in detail in the drawings, which are not limiting and in which like numbers represent like structures. [Brief explanation of the drawings]

[0089] [Figure 1] 1 is a schematic diagram of a vibrating assembly and its equivalent vibration model, according to some embodiments herein. [Figure 2] 1 is a schematic diagram of a deformation at a first resonance peak of a vibration assembly according to some embodiments herein; [Figure 3] 10 is a schematic diagram of a deformation at a second resonance peak of a vibrating assembly according to some embodiments herein. FIG. [Figure 4] 10 is a schematic diagram of a deformation at a third resonance peak of a vibrating assembly according to some embodiments herein. FIG. [Figure 5] FIG. 10 is a schematic diagram of deformation at a fourth resonance peak of a vibration assembly according to some embodiments herein. [Figure 6] 10A-10C are schematic diagrams of frequency response curves of vibrating assemblies with different differences between the third and fourth resonant frequencies, according to some embodiments herein. [Figure 7A] FIG. 1 is a schematic diagram of a frequency response curve of a vibration assembly according to some embodiments herein. [Figure 7B] FIG. 10 is a schematic diagram of a frequency response curve of a vibration assembly according to some other embodiments of the present disclosure. [Figure 7C]FIG. 10 is a schematic diagram of a frequency response curve of a vibration assembly according to some other embodiments of the present disclosure. [Figure 7D] FIG. 10 is a schematic diagram of a frequency response curve of a vibration assembly according to some other embodiments of the present disclosure. [Figure 8A] FIG. 1 is a schematic diagram of a vibration assembly according to some embodiments of the present disclosure. [Figure 8B] FIG. 10 is a schematic diagram of a frequency response curve of a vibration assembly according to some other embodiments of the present disclosure. [Figure 9A] 1 is a partial schematic diagram of a vibration assembly according to some embodiments of the present disclosure. [Figure 9B] FIG. 10 is a schematic diagram of a frequency response curve of a vibration assembly according to some other embodiments of the present disclosure. [Figure 9C] FIG. 10 is a schematic diagram of a frequency response curve of a vibration assembly according to some other embodiments of the present disclosure. [Figure 10A] FIG. 10 is a schematic diagram of deformation at a fourth resonance peak of a vibration assembly according to some other embodiments of the present disclosure. [Figure 10B] FIG. 10 is a schematic diagram of a frequency response curve of a vibration assembly according to some other embodiments of the present disclosure. [Figure 10C] FIG. 10 is a schematic diagram of a frequency response curve of a vibration assembly according to some other embodiments of the present disclosure. [Figure 11] FIG. 10 is a schematic diagram of deformation at a fourth resonance peak of a vibration assembly according to some other embodiments of the present disclosure. [Figure 12A] FIG. 12 is a schematic diagram of a frequency response curve of the vibrating assembly shown in FIG. [Figure 12B] FIG. 10 is a schematic diagram of a frequency response curve of a vibration assembly according to some other embodiments of the present disclosure. [Figure 13A] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 13B] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 14A]FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 14B] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 14C] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 14D] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 15A] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 15B] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 16A] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 16B] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 16C] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 16D] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 16E] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 16F] FIG. 10 is a schematic diagram of a frequency response curve of a vibration assembly according to some other embodiments of the present disclosure. [Figure 17A] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 17B] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 17C] FIG. 10 is a schematic diagram of a frequency response curve of a vibration assembly according to some other embodiments of the present disclosure. [Figure 18A] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 18B]FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 18C] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 19] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 20A] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 20B] FIG. 10 is a schematic diagram of a frequency response curve of a vibration assembly according to some other embodiments of the present disclosure. [Figure 21A] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 21B] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 21C] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 21D] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 21E] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 22] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 23] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 24A] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 24B] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 24C] FIG. 10 is a schematic diagram of a frequency response curve of a vibration assembly according to some other embodiments of the present disclosure. [Figure 25A] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 25B]FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 25C] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 26A] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 26B] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 26C] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 26D] FIG. 10 is a schematic diagram of a vibration assembly according to some other embodiments of the present disclosure. [Figure 26E] 1 is a cross-sectional schematic diagram of a reinforcing member according to some embodiments of the present disclosure. [Figure 27] FIG. 1 is an exemplary structural diagram of a speaker according to some embodiments of the present disclosure. DETAILED DESCRIPTION OF THE INVENTION

[0090] In order to more clearly describe the technical means of the embodiments of the present application, the following will briefly describe the drawings necessary for describing the embodiments. Obviously, the drawings described below are only some examples or embodiments of the present application, and those skilled in the art can apply the present application to other similar scenarios based on these drawings without any creative effort. Unless otherwise clear from the language environment or otherwise described, the same numbers in the drawings indicate the same structures or operations.

[0091] It should be understood that the terms "system," "device," "unit," and / or "module" used herein are ways of distinguishing between various levels of assemblies, elements, parts, portions, or assemblies, however, other terms may be used in place of the above terms if they achieve the same purpose.

[0092] As used in this application and the claims, unless the context clearly dictates otherwise, terms such as "a," "one," "one kind," and / or "the" do not specifically refer to the singular but may also include the plural. In general, the terms "comprise" and "containing" are intended to indicate only the inclusion of explicitly identified steps and elements, and these steps and elements are not an exclusive listing; a method or apparatus may also include other steps or elements.

[0093] Flowcharts are used herein to describe operations performed by systems according to embodiments of the present invention. It should be understood that the preceding and following operations are not necessarily performed in exact order. Instead, steps may be performed in reverse order or simultaneously. Other operations may also be added to these processes, or one or more operations may be removed from these processes.

[0094] The embodiments of the present specification provide a vibration assembly applicable to various acoustic output devices. Examples of acoustic output devices include, but are not limited to, speakers and hearing aids. The vibration assembly according to the embodiments of the present specification mainly includes an elastic element and a reinforcing member. The elastic element or the reinforcing member may be connected to a speaker driver, and the edge of the elastic element is fixed (e.g., connected to the speaker housing). In a speaker, the speaker driver serves as an electrical-mechanical energy conversion unit, converting electrical energy into mechanical energy to provide a driving force to the speaker. The vibration assembly receives force or displacement transmitted from the driver and generates a corresponding vibration output, thereby pushing and moving air and generating sound pressure. The elastic element is connected to an air inertial load by a spring and damping, and can be considered to realize the radiation of sound pressure by pushing and moving air.

[0095] The elastic element mainly includes a central region, an edge region located around the periphery of the central region, and a fixed region located around the periphery of the edge region. In some embodiments, to ensure that a speaker has a flat sound pressure level output within a wide range (e.g., 20 Hz to 20 kHz), a certain pattern is designed on the edge region of the elastic element to disrupt the vibration pattern in the corresponding frequency band of the edge region of the elastic element, avoiding sound cancellation caused by local split vibration of the elastic element, and increasing the local stiffness of the elastic element through the pattern design. Furthermore, by designing a thick layer structure on the central region of the elastic element, the stiffness of the central region of the elastic element is increased, avoiding sound cancellation caused by the split vibration pattern in the range of 20 Hz to 20 kHz in the central region of the elastic element of the speaker. However, directly designing a thick layer on the central region of the elastic element increases the mass of the entire vibration assembly, increases the load on the speaker, causes impedance mismatch between the drive end and the load end, and reduces the sound pressure level output from the speaker. On the other hand, in the vibration assembly according to the embodiment of the present specification, the reinforcing member and the elastic element are structurally designed so that the reinforcing member includes one or more annular structures and one or more elongated structures, and each of the one or more elongated structures is connected to at least one of the one or more annular structures. This allows the vibration assembly to exhibit required higher-order modes at mid-to-high frequencies (above 3 kHz), resulting in multiple resonance peaks in the frequency response curve of the vibration assembly, and the vibration assembly can have high sensitivity within a wide frequency range. The structural design of the reinforcing member reduces the mass of the vibration assembly and improves the sensitivity of the entire vibration assembly. Furthermore, by rationally arranging the reinforcing member and arranging multiple openwork regions in the central region of the elastic element, the local stiffness of the central region of the elastic element can be controlled, and the divided vibration form of each openwork region in the central region can be used to control the resonance peak output from the vibration assembly, resulting in a flat sound pressure level curve. For specific details of the vibration assembly, the elastic element, and the reinforcing member, please refer to the related descriptions below.

[0096] As shown in FIG. 1, FIG. 1 is a schematic diagram of a vibration assembly and a corresponding vibration model, according to some embodiments herein.

[0097] In some embodiments, vibrating assembly 100 primarily includes elastic element 110, which includes a central region 112, edge regions 114 located around the periphery of central region 112, and anchoring regions 116 located around the periphery of edge region 114. Elastic element 110 is configured to vibrate along a direction perpendicular to central region 112, thereby transmitting forces and displacements received by vibrating assembly 100 to push and move air. Reinforcement member 120 is connected to central region 112 and includes one or more annular structures 122 and one or more elongated structures 124, each connected to at least one of the one or more annular structures 122, and at least one of the one or more elongated structures 124 extending toward the center of central region 112. By rationally arranging the reinforcing member 120 and arranging multiple openwork areas in the central region 112 of the elastic element 110, the local stiffness of the central region 112 of the elastic element 110 can be controlled to be adjusted, and the divided vibration form of each openwork area in the central region 112 can be used to control the resonance peak output from the vibration assembly, so that the vibration assembly 100 has a flat sound pressure level curve. Furthermore, by engaging the annular structure 122 and the elongated structure 124 with each other, the reinforcing member 120 has an appropriate proportion of reinforcement and openwork (i.e., openwork) portions, which reduces the mass of the reinforcing member 120 and improves the sensitivity of the entire vibration assembly 100. By designing the shape, size, and number of the annular structure 122 and the elongated structure 124, the positions of multiple resonance peaks of the vibration assembly 100 can be adjusted to control the vibration output of the vibration assembly 100.

[0098] The elastic element 110 may be an element that can elastically deform under an external load. In some embodiments, the elastic element 110 may be a heat-resistant material so as to maintain performance during the manufacturing process when the vibrating assembly 100 is applied to a speaker. In some embodiments, the Young's modulus and shear modulus of the elastic element 110 do not change or change only slightly (e.g., within 5%) when the elastic element 110 is in an environment of 200°C to 300°C. The Young's modulus characterizes the elastic element 110's ability to deform when stretched or compressed, and the shear modulus characterizes the elastic element 110's ability to deform when sheared. In some embodiments, the elastic element 110 may be a material with excellent elasticity (i.e., easily elastically deformed) so that the vibrating assembly 100 has excellent vibration response. In some embodiments, the material of the elastic element 110 may be one or more of an organic polymer material, a rubber-based material, etc.In some embodiments, the organic polymeric material is selected from the group consisting of polycarbonate (PC), polyamides (PA), acrylonitrile butadiene styrene (ABS), polystyrene (PS), high impact polystyrene (HIPS), polypropylene (PP), polyethylene terephthalate (PET), polyvinyl chloride (PVC), polyurethanes (PU), polyethylene (PE), phenolic resins (Phenol), and the like. The organic polymer material may be any one or a combination of the following: polyethylene naphthalate (PEN), polyethylene naphthalate two formal acid glycol ester (PF), melamine-formaldehyde resin (MF), polyarylate (PAR), polyetherimide (PEI), polyimide (PI), polyethylene naphthalate two formal acid glycol ester (PEN), polyetheretherketone (PEEK), carbon fiber, graphene, silica gel, etc. In some embodiments, the organic polymer material may be any one or a combination of the following: a rubber-based material, including, but not limited to, a gel-based material, a silicone gel-based material, an acrylic-based material, a polyurethane-based material, a rubber-based material, an epoxy-based material, a hot melt-based material, a photocurable material, etc., and preferably a silicone adhesive adhesive or a silicone sealing adhesive.

[0099] In some embodiments, the Shore hardness of the elastic element 110 may be between 1 and 50 HA. In some embodiments, the Shore hardness of the elastic element 110 may be between 1 and 15 HA. In some embodiments, the Shore hardness of the elastic element 110 may be between 14.9 and 15.1 HA.

[0100] In some embodiments, the Young's modulus of the elastic element 110 is in the range of 5E8 Pa to 1E10 Pa. In some embodiments, the Young's modulus of the elastic element 110 is in the range of 1E9 Pa to 5E9 Pa. In some embodiments, the Young's modulus of the elastic element 110 is in the range of 1E9 Pa to 4E9 Pa. In some embodiments, the Young's modulus of the elastic element 110 is in the range of 2E9 Pa to 5E9 Pa.

[0101] In some embodiments, the density of the elastic element 110 is 1E3 kg / m 3 ~4E3kg / m 3 In some embodiments, the density of the elastic element 110 is in the range of 1E3 kg / m 3 ~2E3kg / m 3 In some embodiments, the density of the elastic element 110 is in the range of 1E3 kg / m 3 ~3E3kg / m 3 In some embodiments, the density of the elastic element 110 is in the range of 1E3 kg / m 3 ~1.5E3kg / m 3 In some embodiments, the density of the elastic element 110 is in the range of 1.5E3 kg / m 3 ~2E3kg / m 3 is in the range.

[0102] 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 a driving unit of the speaker. In other embodiments, the reinforcing member 120 installed in the central region 112 of the elastic element 110 may be directly connected to a driving unit of the speaker. The central region 112 of the elastic element 110 and the reinforcing member 120 can transmit the force and displacement of the driving unit to push and move air, thereby outputting sound pressure.

[0103] The central region 112 refers to a region of the elastic element 110 that extends from the center (e.g., the center of gravity) toward the periphery by a certain area, and the reinforcing member 120 is connected to the central region 112. The elastic element 110 is configured to vibrate along a direction perpendicular to the central region 112. As the main vibration region of the elastic element 110, the central region 112 can transmit force and displacement and output a vibration response.

[0104] The edge region 114 is located outside the central region 112. In some embodiments, the edge region 114 may be designed with a unique pattern to disrupt the vibration mode of the elastic element 110 in the corresponding frequency band of the edge region 114, avoid sound cancellation caused by localized partial vibration of the elastic element 110, and increase the local stiffness of the elastic element 110 through the pattern design.

[0105] In some embodiments, the edge region 114 may include an edge structure. In some embodiments, by adjusting parameters such as the edge width and arch height of the edge structure, the stiffness of the edge region 114 corresponding to the edge structure varies, and the frequency band of the corresponding high-frequency local division vibration mode also varies. The edge width may be the radial width of the projection of the edge region 114 along the vibration direction of the elastic element 110. The arch height refers to the height of the edge region 114 protruding from the central region 112 or the fixed region 116 along the vibration direction of the elastic element 110.

[0106] In some embodiments, the maximum area of ​​the projection of one or more annular structures 122 of stiffening member 120 along the vibration direction of elastic element 110 is smaller than the area of ​​central region 112. That is, between the outermost portion of the projection of stiffening member 120 and edge region 114, there is an area that is not supported by stiffening member 120, and the portion of central region 112 between edge region 114 and stiffening member 120 is referred to herein as suspension region 1121. In some embodiments, by adjusting the maximum contour of stiffening member 120, the area of ​​suspension region 1121 can be adjusted to adjust the modal vibration type of the vibrating assembly.

[0107] The fixing region 116 is disposed on the outer periphery of the edge region 114. The elastic element 110 can be connected and fixed via the fixing region 116. For example, the elastic element 110 may be connected and fixed to a speaker housing or the like via the fixing region 116. In some embodiments, the fixing region 116 can be considered to be attached and fixed to the speaker housing and not involved in the vibration of the elastic element 110. In some embodiments, the fixing region 116 of the elastic element 110 may be connected to the speaker housing via a support element. In some embodiments, the support element may include a soft material that is easily deformed so that the support element also deforms when the vibrating assembly 100 vibrates, thereby providing a larger displacement for the vibration of the vibrating assembly 100. In other embodiments, the support element may include a hard material that is less likely to deform.

[0108] In some embodiments, the elastic element 110 may further include a connection region 115 located between the edge region 114 and the anchoring region 116. In some embodiments, the connection region 115 can adjust the modal vibration type of the vibrating assembly 100 by providing additional stiffness and damping to the vibration of the elastic element 110.

[0109] To enable the elastic element 110 to provide appropriate stiffness, the thickness and elastic modulus of the elastic element 110 can be set within a reasonable range. In some embodiments, the thickness of the elastic element 110 may be in the range of 3 μm to 100 μm. In some embodiments, the thickness of the elastic element 110 may be in the range of 3 μm to 50 μm. In some embodiments, the thickness of the elastic element 110 may be in the range of 3 μm to 30 μm.

[0110] The reinforcing member 120 may be an element for increasing the stiffness of the elastic element 110. In some embodiments, the reinforcing member 120 is connected to the central region 112, and the reinforcing member 120 and / or the central region 112 are connected to a speaker driver to transmit force and / or displacement, causing the vibrating assembly 100 to push and move air and output sound pressure. The reinforcing member 120 may include one or more annular structures 122 and one or more elongated structures 124, each connected to at least one of the one or more annular structures 122 to form cross-supports for the central region 112 of the elastic element 110. At least one of the one or more elongated structures 124 extends toward the center of the central region 112. In some embodiments, the one or more elongated structures 124 may pass through the center of the central region 112 to support the center of the central region 112. In some embodiments, the reinforcing member 120 may further include a central connection 123, and one or more elongated structures 124 may cover the center of the central region 112 by the central connection 123 without passing through the center of the central region 112, and the one or more elongated structures 124 are connected to the central connection 123.

[0111] The annular structure 122 may be a structure extending around a specific center. In some embodiments, the center surrounded by the annular structure 122 may be the center of the central region 112. In other embodiments, the center surrounded by the annular structure 122 may be at another position offset from the center of the central region 112. In some embodiments, the annular structure 122 may be a structure with a closed contour. In some embodiments, the shape of the annular structure 122 projected along the vibration direction of the elastic element 110 may include, but is not limited to, one or more combinations of a circular ring, a polygonal ring, a curved ring, or an elliptical ring. In other embodiments, the annular structure 122 may be a structure with an open contour. For example, the annular structure 122 may be a circular ring, a polygonal ring, a curved ring, or an elliptical ring with a cutout. In some embodiments, the number of the annular structures 122 may be one. In some embodiments, the number of the annular structures 122 may be multiple, and the multiple annular structures may have the same center of gravity. In some embodiments, the number of annular structures 122 may range from 1 to 10. In some embodiments, the number of annular structures 122 may range from 1 to 5. In some embodiments, the number of annular structures 122 may range from 1 to 3. If the number of annular structures 122 is too large, the mass of the stiffening member 120 may be too large, which may further reduce the sensitivity of the entire vibrating assembly 100. In some embodiments, the number of annular structures 122 can be designed to adjust the mass and stiffness of the stiffening member 120. In some embodiments, the size of the outermost annular structure 122 of the stiffening member 120 can be considered the maximum size of the stiffening member. In some embodiments, setting the size of the outermost annular structure 122 can adjust the size (or area) of the suspension region 1121 between the edge region 114 and the stiffening member 120, thereby changing the mode vibration type of the vibrating assembly 100.

[0112] In some embodiments, the one or more annular structures 122 may include a first annular structure and a second annular structure, where the radial dimension of the first annular structure is smaller than the radial dimension of the second annular structure. In some embodiments, the first annular structure is disposed inside the second annular structure. In some embodiments, the centers of gravity of the first annular structure and the second annular structure may overlap. In other embodiments, the centers of gravity of the first annular structure and the second annular structure may not overlap. In some embodiments, the first annular structure and the second annular structure may be connected via one or more elongated 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 be non-adjacent annular structures, and one or more annular structures may be disposed between the first annular structure and the second annular structure.

[0113] The elongated structure 124 may have a specific extension pattern. In some embodiments, the elongated structure 124 may extend along a straight line. In some embodiments, the elongated structure 124 may extend along a curved line. In some embodiments, extending along a curved line may include, but is not limited to, extending in an arc, extending in a spiral, extending along a spline curve, extending in a circular arc, and extending in an S-shape. In some embodiments, the elongated structure 124 is connected to the annular structure 122 to divide the reinforcing member 120 into multiple openwork sections. In some embodiments, the area corresponding to the openwork section of the central region 112 may be referred to as an openwork region. In some embodiments, the number of elongated structures 124 may be one. For example, one elongated structure 124 may be disposed along any diameter of the annular structure 122 (e.g., any of the annular structures). In some embodiments, the elongated structures 124 may be connected to both the center of the central region (i.e., the center of gravity of the annular structure 122) and the annular structure 122. In some embodiments, the number of elongated structures 124 may be multiple. In some embodiments, the multiple elongated structures 124 may be located along multiple diameters of the annular structure 122. In some embodiments, at least some of the multiple elongated structures 124 may extend toward a central location of the central region 112, which may be the center of gravity of the elastic element 110. In some embodiments, the multiple elongated structures 124 may include separate portions extending in other directions. In some embodiments, at least some of the multiple elongated structures 124 may be connected to a central location of the central region, forming a central connection 123 at the central location. In some embodiments, the central connection 123 may be a separate structure, and at least some of the multiple elongated structures 124 may be connected to the central connection 123. In some embodiments, the shape of the central connection portion 123 may include, but is not limited to, a circle, a square, a polygon, an ellipse, etc. In some embodiments, the shape of the central connection portion 123 may be arbitrarily set.In some embodiments, when there are multiple annular structures 122, adjacent annular structures 122 may be connected via one or more elongated structures 124. In some embodiments, the elongated structures 124 connected between adjacent annular structures 122 may or may not extend toward the center position of the central region 112.

[0114] In some embodiments, the number of elongated structures 124 may range from 1 to 100. In some embodiments, the number of elongated structures 124 may range from 1 to 50. In some embodiments, the number of elongated structures 124 may range from 1 to 30. By setting the number of elongated structures 124, the mass of the entire vibrating assembly 100, the stiffness of the reinforcing member 120, and the area of ​​the openwork region of the elastic element 110 can be adjusted to change the modal vibration type of the vibrating assembly.

[0115] In some embodiments, the shape of the projection of the elongated structure 124 along the vibration direction of the elastic element 110 comprises at least one of a rectangular, a trapezoidal, a curved, an hourglass, and a petal. By designing the elongated structure 124 with different shapes, the mass distribution (e.g., the location of the center of mass) of the stiffening member 120, the stiffness of the stiffening member 120, and the area of ​​the openwork region can be adjusted to change the modal vibration type of the vibrating assembly.

[0116] The structures of the annular structures 122 and the elongated structures 124 in the embodiments of this specification are merely optional structures selected to facilitate rational installation of the reinforcing member 120, and should not be understood as limiting the shape of the reinforcing member 120 and each of its portions. In fact, the reinforcing member 120 in the embodiments of this specification can be configured with the annular structures 122 and the elongated structures 124 to form a reinforcing portion and an openwork portion (i.e., an openwork portion corresponding to the openwork region of the central region 112) located between the annular structures 122 and the elongated structures 124. The region where one or more annular structures 122 are located and the region where one or more elongated structures 124 are located together form the reinforcing portion. The region not covered by the one or more annular structures 122 and the one or more elongated structures 124 within the projection range of the maximum contour of the reinforcing member 120 along the vibration direction of the elastic element 110 forms the openwork portion. By adjusting the parameters of the reinforcing portion and the openwork portion (e.g., area, thickness of the reinforcing portion, etc.), it is possible to adjust the vibration characteristics (e.g., the number and frequency range of resonance peaks) of the vibration assembly 100. In other words, for a reinforcing member of any shape having a reinforcing portion and an openwork portion, the parameter setting method for the reinforcing portion and the openwork portion provided in this specification can be used to set, thereby achieving the purpose of adjusting the vibration performance of the vibration assembly (e.g., the number and position of resonance peaks, the shape of the frequency response curve, etc.), and all of these means should be included in the scope of the present application.

[0117] In some embodiments, as shown in FIG. 1, the connection region 115 between the fixed region 116 and the edge region 114 of the elastic element 110 is installed in a suspended manner, and the equivalent mass of the region is Mm1, and the elastic element 110 can provide elasticity and damping, so that the region is equivalent to being fixedly connected to the housing via a spring Km and a damping Rm, and the connection region 115 is connected to the air load at the front end of the elastic element 110 via a spring Ka1 and a damping Ra1, and transmits force and displacement to push and move the air.

[0118] In some embodiments, the edge region 114 of the elastic element 110 has a local equivalent mass Mm2, which is connected to the connection region 115 of the elastic element 110 via a spring Ka1' and a damping Ra1', and the edge region 114 is connected to the air load at the front end of the elastic element 110 via a spring Ka2 and a damping Ra2, transmitting force and displacement to push and move the air.

[0119] In some embodiments, a reinforcing member 120 is installed in the central region 112 of the elastic element 110, and is connected to 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 partial suspension region 1121 exists between the area of ​​the central region 112 of the elastic element 110 supported by the reinforcing member 120 and the edge region 114. The region has a local equivalent mass Mm3, and is connected to the edge region 114 via a spring Ka2' and a damper Ra2'. The region where the reinforcing member 120 is located is connected to the air load at the front end of the elastic element 110 via a spring Ka3 and a damper Ra3, transmitting force and displacement to push and move the air.

[0120] In some embodiments, depending on the design of the stiffening member 120, the central region 112 of the elastic element 110 corresponding to the stiffening member 120 may have one or more openwork regions, each of which may correspond to a mass-spring-damping system, with an equivalent mass Mm i , equivalent stiffness Ka i , Ka i ', equivalent damping Ra i , Ra i The openwork area has a spring Ka i ', decay Ra i The openwork area is further connected to the adjacent openwork area via a spring Ka i ', decay Ra i ', and the suspension area 1121 is connected to the suspension area 1121 between the area supported by the reinforcing member 120 of the central area 112 and the edge area 114, and the suspension area 1121 is connected to the spring Ka i , attenuation Ra i110 to transmit force and displacement to push and move the air.

[0121] In some embodiments, the stiffening member 120 itself has an equivalent mass Mm n The reinforcing member 120 has a spring Ka n ', decay Ra n ', and the reinforcing member 120 is connected to the central region 112 via the spring Ka n , attenuation Ra n When the reinforcing member 120 itself resonates, it drives the central region 112 and the resilient element 110 to generate a large moving speed and displacement, thereby generating a high sound pressure level.

[0122] According to the dynamic characteristics of the mass-spring-damping system, each mass-spring-damping system has its own resonance peak frequency f0, and can generate large moving speed and displacement at f0. By designing different parameters of the vibration assembly 100 (for example, the structural parameters of the elastic element 110 and / or the stiffening member 120), the mass-spring-damping systems formed by the structures at different positions of the vibration assembly 100 can resonate in a required frequency band, and the frequency response curve of the vibration assembly 100 will have multiple resonance peaks, thereby greatly widening the effective frequency band of the vibration assembly 100. And by designing the stiffening member 120, the vibration assembly 100 can have a lighter mass and output a higher sound pressure level.

[0123] FIG. 2 is a diagram of deformation of a vibration assembly according to some embodiments of the present specification at a first resonance peak, FIG. 3 is a diagram of deformation of a vibration assembly according to some embodiments of the present specification at a second resonance peak, FIG. 4 is a diagram of deformation of a vibration assembly according to some embodiments of the present specification at a third resonance peak, and FIG. 5 is a diagram of deformation of a vibration assembly according to some embodiments of the present specification at a fourth resonance peak.

[0124] As can be seen from the schematic diagram of the equivalent vibration model of the vibration assembly 100 shown in Figure 1, each part of the vibration assembly 100 resonates at a different frequency band, and by outputting a large velocity value in the corresponding frequency band, a large sound pressure value is output in the corresponding frequency band of the frequency response curve of the vibration assembly 100, and a corresponding resonance peak appears. Furthermore, due to the multiple resonance peaks, the frequency response of the vibration assembly 100 has high sensitivity within the audible range (e.g., 20 Hz to 20 kHz).

[0125] As shown in FIGS. 1 and 2, in some embodiments, the mass of the stiffening member 120, the mass of the elastic element 110, the equivalent air mass, and the equivalent driving end mass are combined to form a total equivalent mass Mt, and the equivalent damping of each part forms a total equivalent damping Rt. The elastic element 110 (especially the edge region 114 and the region of the elastic element 110 suspended between the edge region 114 and the stiffening member 120) has a large compliance and provides a stiffness Kt to the system, forming a mass Mt-spring Kt-damping Rt system. The system has a resonant frequency, and when the excitation frequency of the driving end is close to the velocity resonant frequency of the system, the system resonates (as shown in FIG. 2), and a large velocity value v occurs in a frequency band near the velocity resonant frequency of the Mt-Kt-Rt system. a and the sound pressure amplitude and sound velocity output from the vibration assembly 100 are positively correlated (p a ∝v a), a resonance peak appears in the frequency response curve, and this resonance peak is defined herein as the first resonance peak of the vibration assembly 100. In some embodiments, as shown in FIG. 2, FIG. 2 shows the vibration situation in the AA cross section of the vibration assembly 100, where the white structure in FIG. 2 represents the shape and position of the reinforcing member 120 before deformation, and the black structure represents the shape and position of the reinforcing member 120 at the time of the first resonance peak. Note that FIG. 2 only shows the structure situation in the AA cross section from the center of the reinforcing member 120 of the vibration assembly 100 to one side edge of the elastic element 110, i.e., only half of the AA cross section, and the other half of the AA cross section, which is not shown, is symmetrical to the situation shown in FIG. 2. As can be seen from the vibration situation in the AA cross section of the vibration assembly 100, at the position of the first resonance peak, the main deformation position of the vibration assembly 100 is the part of the elastic element 110 connected to the fixed region 116. In some embodiments, the frequency of the first resonant peak of the vibrating assembly 100 (also referred to as the first resonant frequency) may be related to the ratio of the mass of the vibrating assembly 100 to the elastic modulus of the elastic element 110. In some embodiments, the frequency range of the first resonant peak is 180 Hz to 3000 Hz. In some embodiments, the frequency range of the first resonant peak is 200 Hz to 3000 Hz. In some embodiments, the frequency range of the first resonant peak is 200 Hz to 2500 Hz. In some embodiments, the frequency range of the first resonant peak is 200 Hz to 2000 Hz. In some embodiments, the frequency range of the first resonant peak is 200 Hz to 1000 Hz. In some embodiments, the structure of the reinforcing member 120 can be configured to place the first resonant peak of the vibrating assembly 100 within the above frequency range.

[0126] As shown in Figures 1 and 3, the connection region 115 between the fixed region 116 and the edge region 114 of the elastic element 110 is in a suspended state, and the equivalent mass of the region is Mm1, and the region is fixedly connected to the housing via a spring Km and a damping Rm, and the connection region 115 is connected to the air load at the front end of the elastic element 110 via a spring Ka1 and a damping Ra1, and transmits force and displacement to push and move the air.

[0127] The edge region 114 has a local equivalent mass Mm2, which is connected to the connection region 115 via a spring Ka1' and a damping Ra1', and the edge region 114 is connected to the air load at the front end of the elastic element 110 via a spring Ka2 and a damping Ra2, transmitting force and displacement to push and move the air.

[0128] A suspended region 1121 is provided between the region of the central region 112 where the reinforcing member 120 is installed and the edge region 114. The suspended region 1121 has a local equivalent mass Mm3, and is connected to the edge region 114 via a spring Ka2' and a damper Ra2', and the region where the reinforcing member 120 is located is connected to the air load at the front end of the elastic element 110 via a spring Ka3 and a damper Ra3, transmitting force and displacement to push and move the air.

[0129] The above three parts form an equivalent mass Ms, equivalent stiffness Ks, and equivalent damping Rs, forming a mass Ms-spring Ks-damping Rs system. Furthermore, the system has a resonance frequency. When the excitation frequency of the driving end is close to the speed resonance frequency of the Ms-Ks-Rs system, the system resonates and generates a large speed value v in a frequency band near the speed resonance frequency of the Ms-Ks-Rs system. a and the sound pressure amplitude and sound velocity output from the vibration assembly 100 are positively correlated (p a ∝v a), a resonance peak appears in the frequency response curve, and this resonance peak is defined herein as the second resonance peak of the vibration assembly 100. The resonance peak is mainly caused by the vibration modes of the connection region 115, the edge region 114, and the suspension region between the region of the central region 112 where the reinforcing member 120 is installed and the edge region 114. As shown in FIG. 3 , FIG. 3 shows the deformation positions of the vibration assembly 100 before the second resonance peak (the upper structural view in FIG. 3 ) and after the second resonance peak (the lower structural view in FIG. 3 ). In some embodiments, as can be seen from the vibration situation in the AA cross section of the vibration assembly 100 as shown in FIG. 3 , the main deformation positions of the vibration assembly 100 before and after the frequency of the second resonance peak are the edge region 114 and the suspension region 1121. 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 the vibrating assembly 100 may be 1000 Hz to 10000 Hz. In some embodiments, the frequency range of the second resonant peak of the vibrating assembly 100 may be 3000 Hz to 7000 Hz. In some embodiments, the frequency range of the second resonant peak of the vibrating assembly 100 may be 3000 Hz to 6000 Hz. In some embodiments, the frequency range of the second resonant peak of the vibrating assembly 100 may be 4000 Hz to 6000 Hz. In some embodiments, the structure of the reinforcing member 120 can be configured to place the second resonant peak of the vibrating assembly 100 within the above frequency range.

[0130] As shown in FIGS. 1 and 4, the reinforcing member 120 itself has an equivalent mass Mm n The reinforcing member 120 has a spring Ka n ', decay Ra n ', and the reinforcing member 120 is connected to the central region 112 via the spring Ka n , attenuation Ra nWhen the reinforcing member 120 itself resonates, it drives the central region 112 and the resilient element 110 to generate a large moving speed and displacement, thereby generating a high sound pressure level.

[0131] The stiffening member 120, the connection region 115, the edge region 114, the hanging region 1121 between the region where the stiffening member 120 is installed in the central region 112 and the edge region 114, the equivalent air mass, and the equivalent mass at the driving end combine to form a total equivalent mass Mt1, and the equivalent damping of each part forms a total equivalent damping Rt1. The stiffening member 120 and the elastic element 110 (especially the region covered by the stiffening member 120 in the central region 112) have high stiffness and provide stiffness Kt1 to the system, forming a mass Mt1-spring Kt1-damping Rt1 system, which is configured such that an annular region in the diameter direction of the central region 112 is an equivalent fixed support point, and the stiffness Kt1 is provided within the annular region and the annular region. The connecting region 115, the edge region 114, and the suspension region 1121 between the region where the reinforcing member 120 of the central region 112 is installed and the edge region 114 are driven to vibrate by the reinforcing member 120, realizing a resonance mode (shown in FIG. 4) with a vibration form of reverse motion. This resonance is also at the resonance frequency point of the equivalent mass Mt1-spring Kt1-damper Rt1 system. When the excitation frequency of the driving end is close to the velocity resonance frequency of the system, the Mt1-Kt1-Rt1 system resonates, and a large velocity value v is generated in the frequency band near the velocity resonance frequency of the Mt1-Kt1-Rt1 system. a and the sound pressure amplitude and sound velocity output from the vibration assembly 100 are positively correlated (p a ∝v a), a resonance peak appears in the frequency response curve, and this resonance peak is defined herein as the third resonance peak of the vibration assembly 100. In some embodiments, as shown in FIG. 4, which shows the deformation positions of the vibration assembly 100 before the third resonance peak (the upper structural view in FIG. 4) and after the third resonance peak (the lower structural view in FIG. 4), respectively, as can be seen from the vibration situation in the AA cross section of the vibration assembly 100, the main deformation position of the vibration assembly 100 before and after the frequency of the third resonance peak (also referred to as the third resonance frequency) is the reverse deformation portion of the stiffening member 120. In some embodiments, the third resonance peak of the vibration assembly 100 may be related to the stiffness of the stiffening member 120. In some embodiments, the frequency range of the third resonance peak may be 5000 Hz to 12000 Hz. In some embodiments, the frequency range of the third resonance peak may be 6000 Hz to 12000 Hz. In some embodiments, the frequency range of the third resonant peak may be 6000 Hz to 10000 Hz. In some embodiments, the structure of the reinforcing member 120 can be configured to place the third resonant peak of the vibrating assembly 100 within the above frequency range.

[0132] As shown in FIGS. 1 and 5, the reinforcing member 120 has one or more openwork regions corresponding to the central region 112, each openwork region being a mass-spring-damping system with an equivalent mass Mm i , equivalent stiffness Ka i , Ka i ', equivalent damping Ra i , Ra i The openwork area has a spring Ka i ', decay Ra i ' and connected to the adjacent openwork area via spring Ka i ', decay Ra i ', and the openwork area is connected to the suspension area 1121 between the area supported by the reinforcing member 120 of the central area 112 and the edge area 114, and the openwork area is connected to the spring Ka i , attenuation Ra i110 to transmit force and displacement to push and move the air.

[0133] Because the openwork regions are spaced apart by the elongated structures 124 of the reinforcing member 120, each openwork region can form a different resonant frequency and independently push and move the air regions connected thereto to generate corresponding sound pressure. Furthermore, by designing the position, size, and number of the elongated structures 124 of the reinforcing member 120, each openwork region can have a different resonant frequency, thereby causing one or more high-frequency resonant peaks (i.e., fourth resonant peaks) to appear in the frequency response curve of the vibrating assembly 100. In some embodiments, the one or more high-frequency resonant peaks (i.e., fourth resonant peaks) may range from 10,000 Hz to 18,000 Hz.

[0134] Furthermore, to increase the sound pressure level output by the vibration assembly 100 at high frequencies (10,000 Hz to 20,000 Hz), the resonant frequencies of the openwork regions are designed to be equal or close to each other by designing the position, dimensions, and number of the elongated structures 124. In some embodiments, by setting the difference in the resonant frequencies of the openwork regions within 4,000 Hz, a high-frequency resonant peak with a high output sound pressure level appears on the frequency response curve of the vibration assembly 100. This resonant peak is defined herein as the fourth resonant peak (shown in FIG. 5 ) of the vibration assembly 100. In some embodiments, as can be seen from the vibration situation in the B-B cross section of the vibration assembly 100 as shown in FIG. 5 , the main deformation location of the vibration assembly 100 near the frequency of the fourth resonant peak (also referred to as the fourth resonant frequency) is the portion of deformation occurring in the openwork region of the central region 112. In some embodiments, the frequency range of the fourth resonant peak may be 8,000 Hz to 20,000 Hz. In some embodiments, the frequency range of the fourth resonant peak may be 10,000 Hz to 18,000 Hz. In some embodiments, the frequency range of the fourth resonant peak may be 12,000 Hz to 18,000 Hz. In some embodiments, the frequency range of the fourth resonant peak may be 15,000 Hz to 18,000 Hz. In some embodiments, the resonant frequency of each openwork region can be adjusted by designing the area of ​​one or more openwork regions and the thickness of elastic element 110, so that the fourth resonant peak of vibrating assembly 100 is within the above frequency range. In some embodiments, to ensure that the range of the fourth resonant peak of vibrating assembly 100 is within the above frequency range, the ratio of the area of ​​each openwork region to the thickness of elastic element 110 is in the range of 100 mm to 1,000 mm. In some embodiments, the ratio of the area of ​​each openwork region to the thickness of the elastic element 110 is in the range of 120 mm to 900 mm to ensure that the range of the fourth resonance peak of the vibrating assembly 100 is within the above frequency range. In some embodiments, the ratio of the area of ​​each openwork region to the thickness of the elastic element 110 is in the range of 150 mm to 800 mm to ensure that the range of the fourth resonance peak of the vibrating assembly 100 is within the above frequency range.In some embodiments, in order to place the fourth resonant peak of the vibrating assembly 100 within the above frequency range, the ratio of the area of ​​each openwork region to the thickness of the elastic element 110 is in the range of 150 mm to 700 mm.

[0135] As shown in FIG. 6, FIG. 6 shows frequency response curves of vibration assemblies 100 having different differences between the third and fourth resonant frequencies according to some embodiments of the present disclosure. The horizontal axis represents frequency (Hz), and the vertical axis represents sensitivity (SPL). By designing the structures of the reinforcing member 120 and the elastic element 110, the vibration assembly 100 can have multiple resonant peaks in the audible range. Furthermore, by combining multiple resonant peaks, the vibration assembly 100 can have high sensitivity throughout the entire audible range. By designing the elongated structure 124 and the annular structure 122 of the reinforcing member 120, the fourth resonant peak 240 of the vibration assembly 100 can be located in a different frequency range. By designing the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230, the frequency response curve can be flat and the output sound pressure level can be high in the frequency band between the fourth resonant peak 240 and the third resonant peak 230, thereby avoiding the appearance of valleys in the frequency response curve. 6, if the frequency difference Δf between the fourth resonance peak 240 and the third resonance peak 230 is too large (Δf2 shown in FIG. 6), a valley appears in the frequency band between the fourth resonance peak 240 and the third resonance peak 230, causing a decrease in the output sound pressure level. On the other hand, if the frequency difference Δf between the fourth resonance peak 240 and the third resonance peak 230 is too small (Δf1 shown in FIG. 6), the frequency of the fourth resonance peak 240 decreases, causing a decrease in the sound pressure level in the high frequency band (e.g., 12 kHz to 20 kHz), and narrowing the frequency band of the vibrating assembly 100. By adjusting the structure of the reinforcing member 120 and the elastic element 110, the third resonance peak 230 can be shifted to the left and / or the fourth resonance peak 240 can be shifted to the 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 is in the range of 80 Hz to 15,000 Hz. In some embodiments, the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230 is in the range of 100 Hz to 13,000 Hz.In some embodiments, the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230 is in the range of 200 Hz to 12,000 Hz. In some embodiments, the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230 is in the range of 300 Hz to 11,000 Hz. In some embodiments, the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230 is in the range of 400 Hz to 10,000 Hz. In some embodiments, the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230 is in the range of 500 Hz to 9,000 Hz. In some embodiments, the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230 is in the range of 200 Hz to 11,000 Hz. In some embodiments, the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230 is in the range of 200 Hz to 10,000 Hz. In some embodiments, the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230 is in the range of 2,000 Hz to 15,000 Hz. In some embodiments, the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230 is in the range of 3,000 Hz to 14,000 Hz. In some embodiments, the frequency difference Δf between the fourth resonant peak 240 and the third resonant peak 230 is in the range of 4,000 Hz to 13,000 Hz.

[0136] As shown in FIG. 7A, due to the design of the reinforcing member 120 and the elastic element 110, the vibration assembly 100 exhibits the required higher-order modes within the audible range of the human ear (20 Hz to 20,000 Hz), and the above-mentioned first resonance peak 210, second resonance peak 220, third resonance peak 230 and fourth resonance peak 240 appear on the frequency response curve of the vibration assembly 100, that is, the number of resonance peaks on the frequency response curve of the vibration assembly 100 within the frequency range of 20 Hz to 20,000 Hz is four, thereby making the vibration assembly 100 have high sensitivity over a wide frequency band range.

[0137] In some embodiments, by designing the structures of the reinforcing member 120 and the elastic element 110, the vibration assembly 100 can have only three resonance peaks within the audible range (20 Hz to 20,000 Hz). For example, if the frequency difference between the second and third resonance peaks of the vibration assembly 100 is less than 2,000 Hz, the second and third resonance peaks will appear as a single resonance peak in the frequency response sound pressure level curve of the vibration assembly 100. Also, for example, if the reinforcing member 120 has one or more suspension regions corresponding to the central region 112, and the resonance frequencies of each openwork region are higher than the audible range or the resonance frequencies of each openwork region are different, and different suspension regions have different vibration phases in different frequency bands in the high frequency range (10,000 Hz to 18,000 Hz), thereby achieving a sound overlap cancellation effect, a high frequency roll-off effect can be achieved, and the fourth resonance peak will not appear in the sound pressure level frequency response curve of the vibration assembly 100.

[0138] 7B, which is a schematic diagram illustrating an overlap of the second and third resonant peaks, according to some embodiments herein. In some embodiments, the frequency difference between the second and third resonant peaks 220 and 230 of the vibrating assembly 100 can be engineered by designing the structure and dimensions of the stiffening member 120, including the overall dimensions of the stiffening member 120, the number and dimensions of the elongated structures 124, the locations of the elongated structures 124, the area of ​​the suspended region 1121 between the region where the stiffening member 120 is installed in the central region 112 and the edge region 114, the pattern design of the edge region 114 (e.g., edge width, arch height, arch shape), and the area of ​​the connection region 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 2000 Hz to 3000 Hz, the frequency response sound pressure level curve (e.g., frequency response curve 710) of the vibration assembly 100 does not have a valley between the second resonant peak 220 and the third resonant peak 230, and the second resonant peak 220 and the third resonant peak 230 (corresponding to the dashed lines in the figure) can still be identified on the frequency response curve. 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 to less than 2000 Hz, the second resonant peak 220 and the third resonant peak 230 appear as a single resonant peak (corresponding to the solid line in the figure) in the frequency response sound pressure level curve (e.g., frequency response curve 720) of the vibration assembly 100, thereby enabling high sensitivity in the mid-to-high frequency band (3000 Hz to 10000 Hz).

[0139] By designing the annular structure 122 and the elongated structures 124 of the reinforcing member 120, the reinforcing member 120 has one or more openwork regions corresponding to the central region 112, each of which is a mass-spring-damping system, and by designing the location, size, and number of the elongated structures 124 of the reinforcing member 120, the resonant frequencies of the openwork regions are equal or close to each other. In some embodiments, the resonant frequency difference between the openwork regions is in the range of 4000 Hz, which results in one or more high frequency resonant peaks (i.e., fourth resonant peaks) with high output sound pressure levels appearing in the frequency response curve of the vibrating assembly 100.

[0140] In some embodiments, as shown in FIG. 7C , by designing the position, dimensions, and number of each elongated structure 124 of the reinforcing member 120, the resonant frequency of each openwork area can be made higher than the audible range, or the resonant frequency of each openwork area can be made different, and different openwork areas can have different vibration phases in different frequency bands in the high frequency range (10,000 Hz to 18,000 Hz), thereby achieving the sound overlap cancellation effect. In this way, the effect of high frequency roll-off can be obtained, and the fourth resonant peak will not appear in the sound pressure level frequency response curve of the vibration assembly 100.

[0141] 7D, which is a schematic diagram of a frequency response curve when the vibration assembly 100 has two resonance peaks, according to some embodiments herein. In some embodiments, by designing the structure of the stiffening member 120, when the frequency difference between the second resonance peak 220 and the third resonance peak 230 of the vibration assembly 100 is less than 2000 Hz, the second resonance peak 220 and the third resonance peak 230 appear as one resonance peak in the frequency response sound pressure level curve of the vibration assembly 100. On the other hand, if the position, size, and number of each elongated structure 124 of the reinforcing member 120 are designed so that the resonant frequency of each openwork area is higher than the audible range, or the resonant frequencies of each openwork area are different and different openwork areas have different vibration phases in different frequency bands in the high frequency range (10,000 Hz to 18,000 Hz), thereby achieving the effect of sound overlap cancellation, a high frequency roll-off effect can be obtained and a fourth resonant peak will not appear in the sound pressure level frequency response curve of the vibration assembly 100. In this case, the vibration assembly 100 has an output characteristic of having a certain bandwidth and high sensitivity in the mid-to-high frequency band (3,000 Hz to 10,000 Hz).

[0142] In some embodiments, the area and thickness of the suspension region 1121 and the edge region 114 of the elastic element 110 can be designed to ensure that the second resonant peak of the vibrating assembly 100 is in a required frequency range. In some embodiments, the second resonant peak of the vibrating assembly 100 may be in a range of 1000 Hz to 10000 Hz. In some embodiments, the second resonant peak of the vibrating assembly 100 may be in a range of 3000 Hz to 7000 Hz. In some embodiments, when designing the frequency difference between the second resonant peak and the third resonant peak of the vibrating assembly 100, the frequency difference between the second resonant peak and the third resonant peak of the vibrating assembly 100 is set to be less than 3000 Hz.

[0143] 8A, which is a schematic diagram of a vibration assembly including a reinforcing member having a single ring structure, according to some embodiments of the present disclosure. In some embodiments, the horizontal projection area of ​​the suspension region 1121 (i.e., the projection area of ​​the suspension region 1121 along the vibration direction of the elastic element 110) is defined as S v and the horizontal plane projected area of ​​the edge region 114 (i.e., the projected area of ​​the edge region 114 along the vibration direction of the elastic element 110) is defined as S e The horizontal projection area S of the hanging area 1121 is defined as v and the horizontal plane projected area S of the edge region 114 e The sum of s The physical quantity α (unit: mm) is defined as S s and the thickness H of the elastic element 110 (also called the diaphragm) i It is defined as the ratio of

[0144]

number

[0145] In some embodiments, to set the frequency range of the second resonant peak of the vibrating assembly 100 between 3000 Hz and 7000 Hz, S s and the thickness of the diaphragm H i The ratio α to α may be in the range of 5000 mm to 12000 mm. In some embodiments, α may be in the range of 6000 mm to 10000 mm to shift the frequency range of the second resonant peak of the vibrating assembly 100 to 3000 Hz to 7000 Hz. In some embodiments, α may be in the range of 6000 mm to 9000 mm to further adjust and shift the frequency range of the second resonant peak of the vibrating assembly 100 to higher frequencies. In some embodiments, α may be in the range of 6000 mm to 8000 mm to further adjust and shift the frequency range of the second resonant peak of the vibrating assembly 100 to higher frequencies. In some embodiments, α may be in the range of 6000 mm to 7000 mm to further adjust and shift the frequency range of the second resonant peak of the vibrating assembly 100 to higher frequencies.

[0146] In some embodiments, the relationship between the area of ​​the suspension region 1121 and the edge region 114 and the thickness of the elastic element 110 affects the local equivalent mass Mm3, the local equivalent mass Mm2, the local region stiffness Ka2' and the local region stiffness Ka1', and further affects the equivalent mass Ms, equivalent stiffness Ks, and equivalent damping Rs formed by the three parts of the connection region 115, the edge region 114, and the suspension region 1121, thereby controlling the range of the second resonance peak of the vibrating assembly 100. In some embodiments, the control of the second resonance peak of the vibrating assembly 100 can be achieved by further designing the arch height of the edge of the edge region 114.

[0147] 8B is a schematic diagram of a frequency response curve of a vibration assembly according to some embodiments of the present disclosure. In some embodiments, as shown in FIG. 8B, frequency response curve 810 represents the frequency response curve of the vibration assembly when α = 8190 mm, frequency response curve 820 represents the frequency response curve of the vibration assembly when α = 7146 mm, and frequency response curve 830 represents the frequency response curve of the vibration assembly when α = 12360 mm. As can be seen from frequency response curve 820, when α = 7146 mm, the frequency of second resonance peak 220 of vibration assembly 100 is approximately 7000 Hz. As can be seen from frequency response curve 810, when α = 8190 mm, the frequency of second resonance peak 220 of vibration assembly 100 is approximately 5000 Hz, and the amplitude of second resonance peak 220 of frequency response curve 810 is close to the amplitude of second resonance peak 220 of frequency response curve 820. That is, as α increases, the resonant frequency of the second resonant peak 220 decreases, but the amplitude remains almost unchanged. As can be seen from the frequency response curve 820, when α=12360 mm, no obvious second resonant peak appears in the vibration assembly 100, and the amplitude of the vibration assembly 100 in the range of 3000 Hz to 7000 Hz is lower than that of the frequency response curves 810 and 820. That is, when α=12360 mm, the output sound pressure level of the vibration assembly 100 is low. Therefore, when α is in the range of 6000 mm to 10000 mm, the frequency range of the second resonant peak of the vibration assembly 100 can be suitably controlled to be 3000 Hz to 7000 Hz, so that the vibration assembly 100 has a high output sound pressure level in the range of 3000 Hz to 7000 Hz.

[0148] 9A, which is a partial schematic diagram of a vibration assembly according to some embodiments of the present specification. In this specification, the arch height of the edge of the edge region 114 is defined as Δh, and the physical quantity δ (unit: mm) is defined as S s and the arch height Δh of the edge of the diaphragm.

[0149]

number

[0150] In some embodiments, δ may be in the range of 50 mm to 600 mm. In some embodiments, δ may be in the range of 100 mm to 500 mm. In some embodiments, δ may be in the range of 200 mm to 400 mm to shift the frequency range of the second resonant peak of the vibrating assembly 100 to 3000 Hz to 7000 Hz. In some embodiments, δ may be in the range of 300 mm to 400 mm to shift the frequency range of the second resonant peak of the vibrating assembly 100 to a lower frequency within the range of 3000 Hz to 7000 Hz. In some embodiments, δ may be in the range of 350 mm to 400 mm to shift the frequency range of the second resonant peak of the vibrating assembly 100 to a lower frequency within the range of 3000 Hz to 7000 Hz. In some embodiments, δ may be in the range of 200 mm to 300 mm to shift the frequency range of the second resonant peak of the vibrating assembly 100 to a higher frequency within the range of 3000 Hz to 7000 Hz. In some embodiments, δ may be in the range of 200 mm to 250 mm to shift the frequency range of the second resonant peak of the vibrating assembly 100 to an even higher frequency within the range of 3000 Hz to 7000 Hz.

[0151] In some embodiments, by designing the arch height of the edge, it is possible to change the three-dimensional dimensions of the edge region 114, thereby changing the stiffness Ka1' of the edge region 114 and further control the second resonance peak of the speaker, without changing the horizontal projection areas of the edge region 114 and the hanging region 1121. In some embodiments, it is possible to further adjust and design the dimensions of the reinforcing portion to adjust the output sound pressure level of the speaker.

[0152] 9B is a schematic diagram of a frequency response curve of a vibration assembly according to some other embodiments of the present disclosure. In some embodiments, as shown in FIG. 9B, frequency response curve 910 represents the frequency response curve of the vibration assembly when δ=262 mm, and frequency response curve 920 represents the frequency response curve of the vibration assembly when δ=197 mm. As can be seen from frequency response curve 910, when δ=262 mm, the frequency of the second resonance peak 220 of the vibration assembly 100 is approximately 5000 Hz. As can be seen from frequency response curve 920, when δ=197 mm, the frequency of the second resonance peak 220 of the vibration assembly 100 is approximately 7000 Hz. Therefore, as δ increases, the resonant frequency of the second resonance peak 220 decreases. When δ is in the range of 200 mm to 400 mm, the frequency range of the second resonance peak of the vibration assembly 100 can be preferably controlled to be 3000 Hz to 7000 Hz.

[0153] In this specification, the horizontal projection area of ​​the central region 112 is defined as S c and the horizontal projection area of ​​the maximum contour of the reinforcing member 120 is defined as S rm and the horizontal projection area of ​​the hanging area 1121 is defined as S v and S rm =S c -S v .

[0154] In this specification, the physical quantity

number

[0155]

number

[0156] In some embodiments,

number

number

number

number

number

number

number

[0157] In some embodiments, when the vibration assembly is deformed near a frequency corresponding to the second resonance peak, local resonance occurs in the suspension region 1121 and the edge region 114. At this time, by designing the dimensions of the reinforcing member 120 (i.e., the maximum contour dimensions of the reinforcing member 120), the reinforcing member 120 can achieve a constant bending deformation in that frequency band, thereby realizing an overlapping increase in sound pressure in different regions of the diaphragm and realizing the output of the maximum sound pressure level at the second resonance peak of the vibration assembly or speaker.

[0158] 9C is a schematic diagram of a frequency response curve of a vibration assembly according to some embodiments of the present disclosure. In some embodiments, as shown in FIG. 9C, the frequency response curve 940 in the figure is

number

number

number

number

number

number

[0159] In some embodiments, the elongated structures 124 can have different widths, shapes, and numbers to adjust the resonant frequency of the speaker by changing the openwork area (the suspended area corresponding to the central area 112) of the reinforcing member 120. For specific details, please refer to Figures 13A to 18C and their related descriptions below.

[0160] In some embodiments, by designing the area of ​​the openwork region (e.g., designing the number and positions of the elongated structures 124 of the reinforcing member 120, the number and positions of the annular structures 122, etc.), the resonant frequency of the vibrating assembly 100 can be adjusted to improve the performance of the vibrating assembly 100. In some embodiments, the fourth resonant peak of the vibrating assembly 100 may be in the range of 8000 Hz to 20000 Hz. In some embodiments, the fourth resonant peak of the vibrating assembly 100 may be in the range of 10000 Hz to 18000 Hz.

[0161] As shown in Figures 6 and 10A, Figure 10A is a diagram of deformation around the frequency of the fourth resonance peak of the CC cross section of a vibration assembly including a reinforcement member with a single ring structure, according to some embodiments of the present disclosure. As can be seen from Figure 6, the frequency difference Δf between the fourth resonance peak 240 and the third resonance peak 230 has a significant effect on the flatness of the frequency response curve of the vibration assembly 100 in the high frequency band. In some embodiments, as can be seen from the vibration situation at the CC cross section of the vibration assembly 100 as shown in Figure 10A, around the frequency of the fourth resonance peak, the main deformation location of the vibration assembly 100 is the portion of deformation occurring in the openwork region of the central region 112. In some embodiments, a mass-spring-damping system is formed, and an equivalent mass Mm i , equivalent stiffness Ka iBy controlling each openwork area corresponding to the central region 112 of the reinforcing member 120 to correspond to S, it is possible to achieve control of the fourth resonance peak 240 of the vibrating assembly 100. For example, the number and dimensions of the elongated structures 124 and the annular structure 122 can be designed to design the area of ​​each openwork area of ​​the central region 112, and the area of ​​each openwork area can be set to S. i 10A shows a modified view of the fourth resonance peak of the vibration assembly 100 including a single annular reinforcing member 120, the conclusion still applies to a vibration assembly having multiple annular reinforcing members 120 (e.g., the vibration assembly 100 shown in FIG. 5).

[0162] In order to place the fourth resonance peak within an appropriate frequency range (10,000 Hz to 18,000 Hz), the physical quantity is defined herein as the area of ​​any openwork region (i.e., the projected area of ​​the openwork portion along the vibration direction of the elastic element 110) S i and the thickness H of the diaphragm (e.g., elastic element 110) of each openwork area. i The area-to-thickness ratio μ (unit: mm) is defined as the ratio of

[0163]

number

[0164] In some embodiments, when the Young's modulus and density of the diaphragm (e.g., elastic element 110) are in a given range, μ can be designed to adjust the frequency position of the fourth resonant peak of the vibrating assembly. In some embodiments, the given range of the Young's modulus of the diaphragm is 5×10^8 Pa to 1×10^10 Pa. In some embodiments, the given range of the Young's modulus of the diaphragm is 1×10^9 Pa to 5×10^9 Pa. In some embodiments, the given range of the density of the diaphragm is 1×10^3 kg / m 3 ~4×10^3kg / m 3 In some embodiments, the given range of diaphragm densities is 1×10^3 kg / m 3 ~2×10^3kg / m3 is.

[0165] In some embodiments, the area-to-thickness ratio μ is in the range of 1000 mm to 10000 mm. In some embodiments, the area-to-thickness ratio μ is in the range of 1500 mm to 9000 mm. In some embodiments, the area-to-thickness ratio μ is in the range of 2000 mm to 8000 mm. In some embodiments, the area-to-thickness ratio μ is in the range of 2500 mm to 7500 mm. In some embodiments, the area-to-thickness ratio μ is in the range of 3000 mm to 7000 mm. In some embodiments, the area-to-thickness ratio μ is in the range of 3500 mm to 6500 mm. In some embodiments, the area-to-thickness ratio μ is in the range of 4000 mm to 6000 mm.

[0166] In some embodiments, the area of ​​each openwork area and the thickness of the diaphragm are designed to provide an equivalent mass Mm i , equivalent stiffness Ka i and further realizes control of the fourth resonance peak of the speaker.

[0167] 10B is a schematic diagram of frequency response curves of a vibrating assembly according to some embodiments herein. In some embodiments, as shown in FIG. 10B, frequency response curve 1010 represents the frequency response curve of the vibrating assembly when μ=5230 mm, 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, and frequency response curve 1040 represents the frequency response curve of the vibrating assembly when μ=5440 mm. 10B, the frequency of the fourth resonant peak of frequency response curve 1010 corresponding to μ = 5230 mm is approximately 15,000 Hz, the frequency of the fourth resonant peak of frequency response curve 1020 corresponding to μ = 4870 mm is approximately 12,000 Hz, the frequency of the fourth resonant peak of frequency response curve 1030 corresponding to μ = 5330 mm is approximately 16,000 Hz, and the frequency of the fourth resonant peak of frequency response curve 1040 corresponding to μ = 5440 mm is approximately 17,000 Hz. Therefore, when μ is in the range of 4,000 mm to 6,000 mm, the frequency range of the fourth resonant peak of vibrating assembly 100 can be suitably controlled to be 10,000 Hz to 18,000 Hz.

[0168] 11, in some embodiments, the reinforcing member 120 has multiple annular structures (e.g., a double annular structure), i.e., the reinforcing member 120 includes multiple annular structures (e.g., a first annular structure, a second annular structure, etc.) adjacently disposed along the radial direction, each having a different diameter, with the annular structure with a smaller diameter being disposed inside the annular structure with a larger diameter. Herein, the area of ​​each openwork region of the elastic element 110 inside the first annular structure is defined as S. 1i When the first annular structure and the second annular structure are adjacent annular structures, the area of ​​each openwork region of the elastic element 110 between the first annular structure and the second annular structure is defined as S 2iIn some other embodiments, the reinforcing member 120 may have more annular structures 122, and the area of ​​each openwork region of the elastic element 110 between the (n-1)th annular structure and the nth annular structure is defined as S ni The openwork area located between the annular structures of different diameters may include a first openwork area and a second openwork area, and the distance between the center of gravity of the first openwork area and the center of the central area is different from the distance between the center of gravity of the second openwork area and the center of the central area. In this specification, the physical quantity that is the openwork area area ratio γ (unit: 1) of the elastic element 110 is defined as the area S of the first openwork area. ki and the area of ​​the second openwork region S ji It is defined as the ratio of

[0169]

number

[0170] where k>j. By designing γ, the frequency position of the fourth resonance peak and the output sound pressure level of the vibrating assembly can be adjusted.

[0171] As shown in Figures 11 and 12A, Figure 12A is a frequency response curve of the vibration assembly corresponding to Figure 11. In Structures 1 to 4, the area S of each openwork area between the first annular area and the second annular area is 2i (i.e., the first openwork area) and the area S of each openwork area within the first annular area 1iThe area ratios γ of the first openwork region (i.e., the second openwork region) are 5.9, 4.7, 3.9, and 3.2, respectively. As can be seen from FIG. 11 , at the fourth resonance peak position of the vibration assembly 100, in Structures 1 to 4, as γ decreases, the radius ΔR1 of the first openwork region located within the inner annular structure 122 gradually increases, and the radius ΔR2 of the second openwork region located between the inner annular structure 122 and the outer annular structure 122 gradually decreases. In some embodiments, as further shown in FIG. 12A , the frequency response curves of the vibration assemblies of Structures 1 to 4 show that the sound pressure amplitude output at the fourth resonance peak position gradually increases. Therefore, the area ratio of each openwork region in the central region 112 affects the resonant frequency of each openwork region, ultimately resulting in a sound pressure superposition effect in the high-frequency band. That is, by setting γ, the high-frequency sensitivity of the vibration assembly 100 can be adjusted.

[0172] In some embodiments, the area ratio of each openwork area in the central area 112 is as small as possible, for example, the area S of the first openwork area ki and the area of ​​the second openwork region S ji The ratio γ of the area S of the first openwork region is in the range of 0.1 to 10. ki and the area of ​​the second openwork region S ji The ratio γ of the area S of the first openwork region to the area S of the first openwork region is in the range of 0.16 to 6. ki and the area of ​​the second openwork region S ji The ratio γ of the area S of the first openwork region is in the range of 0.2 to 5. ki and the area of ​​the second openwork region S ji The ratio γ of the area S of the first openwork region to the area S of the first openwork region is in the range of 0.25 to 4. ki and the area of ​​the second openwork region S ji The ratio γ of the area S of the first openwork region is in the range of 0.25 to 1. ki and the area of ​​the second openwork region S jiIn some embodiments, the ratio γ of the area S of the first openwork region to the area S of the first openwork region is in the range of 0.25 to 0.6. ki and the area of ​​the second openwork region S ji The ratio γ of the area S of the first openwork region to the area S of the first openwork region is in the range of 0.1 to 4. ki and the area of ​​the second openwork region S ji The ratio γ of the area S of the first openwork region to the area S of the first openwork region is in the range of 0.1 to 3. ki and the area of ​​the second openwork region S ji The ratio γ of the area S of the first openwork region to the area S of the first openwork region is in the range of 0.1 to 2. ki and the area of ​​the second openwork region S ji The ratio γ is in the range of 0.1 to 1.

[0173] In some embodiments, the area ratio of each openwork region of the elastic element 110 affects the resonant frequency difference of each openwork region, but since the resonant frequencies of each openwork region are equal or close, the sound pressure of each openwork region is superimposed, thereby increasing the output sound pressure level at the fourth resonant peak position of the speaker.

[0174] FIG. 10C is a schematic diagram of a frequency response curve of a vibration assembly according to some other embodiments of the present disclosure. In some embodiments, as shown in FIG. 10C, frequency response curve 1050 represents the frequency response curve of the vibration assembly when γ=0.6, and frequency response curve 1060 represents the frequency response curve of the vibration assembly when γ=0.2. As shown in FIG. 10C, the output sound pressure level (amplitude) at the fourth resonance peak of frequency response curve 1050 is high, and the output sound pressure level (amplitude) at the fourth resonance peak of frequency response curve 1060 is low. Therefore, when γ is in the range of 0.25 to 4, vibration assembly 100 can have a high output sound pressure level in a high frequency range (e.g., 10,000 Hz to 18,000 Hz).

[0175] In some embodiments, by designing the projected area of ​​the reinforcing member 120 along the vibration direction and the projected area of ​​the maximum contour of the reinforcing member 120 onto the central region 112 along the vibration direction, it is possible to adjust the mass, center of mass, stiffness of the reinforcing member 120, and the mass and stiffness of the openwork region of the central region 112, thereby enabling adjustment of the first resonance peak, third resonance peak, and fourth resonance peak of the vibration assembly 100.

[0176] In this specification, as shown in FIG. 11, the lateral area ratio β (unit: 1) of the reinforcing portion of the reinforcing member 120 to the reinforcing member 120 is defined as the ratio of the projected area S of the reinforcing portion in the shape of the reinforcing member 120 projected along the vibration direction. r and the projected area S of the maximum contour of the reinforcing member 120 onto the central region 112 t It is defined as the ratio of

[0177]

number

[0178] In some embodiments, the lateral area ratio β of the reinforcing portion of the reinforcing member 120 to the reinforcing member 120 is 0.1 to 0.8. In some embodiments, the lateral area ratio β of the reinforcing portion of the reinforcing member 120 to the reinforcing member 120 is 0.2 to 0.7. In some embodiments, the lateral area ratio β of the reinforcing portion of the reinforcing member 120 to the reinforcing member 120 is 0.1 to 0.7. In some embodiments, the lateral area ratio β of the reinforcing portion of the reinforcing member 120 to the reinforcing member 120 is 0.2 to 0.6. In some embodiments, the lateral area ratio β of the reinforcing portion of the reinforcing member 120 to the reinforcing member 120 is 0.3 to 0.6. In some embodiments, the lateral area ratio β of the reinforcing portion of the reinforcing member 120 to the reinforcing member 120 is 0.4 to 0.5. In some embodiments, the lateral area ratio β of the reinforcing portion of the reinforcing member 120 to the reinforcing member 120 is 0.3 to 0.5. In some embodiments, the lateral area ratio β of the reinforcing portion of the reinforcing member 120 to the reinforcing member 120 is 0.2 to 0.5. In some embodiments, the lateral area ratio β of the reinforcing portion of the reinforcing member 120 to the reinforcing member 120 is 0.1 to 0.5.

[0179] In some embodiments, by designing the projected area of ​​the reinforcing member 120 along the vibration direction and the projected area of ​​the maximum contour of the reinforcing member 120 along the vibration direction, it is possible to control the mass, center of mass, and stiffness of the reinforcing member 120 and adjust the mass and stiffness of the openwork area of ​​the central region 112, thereby controlling the total equivalent mass Mt formed by combining the mass of the reinforcing member 120, the mass of the elastic element 110, the equivalent air mass, and the driving end equivalent mass, and further adjusting the first resonance peak, third resonance peak, and fourth resonance peak of the speaker.

[0180] 12B is a schematic diagram of a frequency response curve of a vibration assembly according to some embodiments of the present disclosure. In some embodiments, as shown in FIG. 12B, frequency response curve 1210 represents the frequency response curve of the vibration assembly when β=0.16, frequency response curve 1220 represents the frequency response curve of the vibration assembly when β=0.17, and frequency response curve 1230 represents the frequency response curve of the vibration assembly when β=0.26. As shown in FIG. 12B, frequency response curve 1210, frequency response curve 1220, and frequency response curve 1230 have a first resonant peak 210, a second resonant peak 220, a third resonant peak 230, and a fourth resonant peak 240. When the value of β is changed, the frequencies of first resonant peak 210, third resonant peak 230, and fourth resonant peak 240 all change significantly, but the frequency of second resonant peak 220 changes only slightly. When β=0.16, the fourth resonance peak 240 does not appear in the frequency response curve 1210. When β is increased to 0.17, the first resonance peak 210 and the second resonance peak 220 of the vibrating assembly change little, the third resonance peak 230 moves to a higher frequency, the output sound pressure level at high frequencies increases, and the fourth resonance peak 240 appears clearly. When β is increased to 0.26, the first resonance peak 210 moves to a lower frequency, the third resonance peak 230 moves to a higher frequency, and the fourth resonance peak 240 moves to a higher frequency, and the output sound pressure level of the entire vibrating assembly decreases. Therefore, when β is changed, the first resonant peak, the third resonant peak, and the fourth resonant peak of the vibration assembly 100 can be adjusted, and β can be set in the range of 0.1 to 0.5 to keep the first resonant peak, the third resonant peak, and the fourth resonant peak of the vibration assembly 100 within an appropriate range (e.g., the range shown in the examples of this specification) and to provide the vibration assembly with a high output sound pressure level.

[0181] 13A and 13B, which are schematic diagrams of vibration assemblies having different numbers of elongated structures, according to some embodiments herein. In some embodiments, adjusting the number of elongated structures 124 can adjust the overall mass of the vibration assembly 100 to change the total equivalent mass Mt formed by combining the mass of the stiffening member 120, the mass of the elastic element 110, the equivalent air mass, and the equivalent driving end mass, thereby changing the resonant frequency of the mass Mt-spring Kt-damping Rt system, which in turn changes the primary resonant frequency of the vibration assembly 100, changing the sensitivity of the vibration assembly 100 in the low frequency band before the first resonant frequency and the mid frequency band after the first resonant frequency. In some embodiments, the number of elongated structures 124 can be designed to increase the total equivalent mass Mt, thereby shifting the first resonant frequency of the vibrating assembly 100 forward, thereby improving sensitivity in low frequency bands before the first resonant frequency of the vibrating assembly 100, e.g., frequency bands before 3000 Hz, frequency bands before 2000 Hz, frequency bands before 1000 Hz, frequency bands before 500 Hz, and frequency bands before 300 Hz. In some embodiments, the number of elongated structures 124 can be designed to decrease the total equivalent mass Mt, thereby shifting the first resonant frequency of the vibrating assembly 100 forward, thereby improving sensitivity in mid-frequency bands after the first resonant frequency of the vibrating assembly 100, e.g., frequency bands after 3000 Hz. Also, for example, sensitivity may be improved in frequency bands after 2000 Hz. Also, for example, sensitivity may be improved in frequency bands after 1000 Hz. Also, for example, sensitivity may be improved in frequency bands after 500 Hz. Also, for example, the sensitivity of the frequency band after 300 Hz may be increased.

[0182] In some embodiments, adjusting the number of elongated structures 124 can further adjust the stiffness of the reinforcing member 120 to change the stiffness Kt1 provided to the system by the reinforcing member 120 and the elastic element 110; the reinforcing member 120, the connection region 115, the edge region 114, the suspension region between the area covered by the reinforcing member 120 in the central region 112 and the edge region 114, the equivalent air mass, and the equivalent drive end mass combine to form a total equivalent mass Mt1, and the equivalent damping of each part forms a total equivalent damping Rt1; the formed mass Mt1-spring Kt1-damping Rt1 system has an equivalent fixed support at a certain annular region in the diameter direction of the reinforcing member 120, and by changing the resonant frequency of the reversal motion by the ring, the third resonance position of the vibration assembly 100 is changed.

[0183] In some embodiments, the number of elongated structures 124 can be adjusted, and the area of ​​one or more hanging regions corresponding to the central region 112 of the reinforcing member 120 can be adjusted to reduce the equivalent mass Mm i , equivalent stiffness Ka i , Ka i ', equivalent damping Ra i , Ra i ' can be varied, thereby varying the location of the fourth resonant peak of the vibrating assembly. In some embodiments, adjusting the number of elongated structures 124 can further adjust the area-to-thickness ratio μ of the vibrating assembly and the lateral area ratio β of the stiffening portion of the stiffening member 120 to the stiffening member 120 to adjust the location of the fourth resonant peak of the vibrating assembly.

[0184] In some embodiments, the number of elongated structures 124 of the reinforcing member 120 is adjustable, and the positions of the first resonant peak, the third resonant peak, and the fourth resonant peak of the vibrating assembly 100 can be adjusted according to actual application needs, thereby realizing controllable adjustment of the frequency response of the vibrating assembly 100.

[0185] In some embodiments, the shape of the projection of the elongated structure 124 along the vibration direction of the elastic element 110 includes at least one of a rectangle, a trapezoid, a curved shape, an hourglass shape, and a petal shape. Therefore, by adjusting the shape of the elongated structure 124, the area of ​​the openwork region of the reinforcing member 120 (corresponding to the hanging region of the central region 112 within the projection range of the reinforcing member 120) can be changed to adjust the relationship between the area of ​​the openwork region and the thickness of the elastic element 110 (area-thickness ratio μ), thereby achieving the purpose of adjusting the fourth resonance peak. In addition, by changing the relationship between the areas of the openwork areas between different annular structures 122 of the reinforcing member 120 (openwork area area ratio γ), the objective of adjusting the fourth resonance peak can be achieved, and further, by changing the relationship between the lateral area of ​​the reinforcing portion of the reinforcing member 120 and the reinforcing member 120 (lateral area ratio β between the reinforcing portion of the reinforcing member 120 and the reinforcing member 120), the objective of adjusting the first resonance peak, the third resonance peak, and the fourth resonance peak can be achieved.

[0186] 14A-14D, which are schematic diagrams of vibrating assemblies having elongated structures with different widths according to some embodiments herein, the elongated structure 124 in FIG. 14A is an inverted trapezoid (i.e., the shorter side of the trapezoid is close to the center of the stiffening member 120), the elongated structure 124 in FIG. 14B is a trapezoid (i.e., the shorter side of the trapezoid is away from the center of the stiffening member 120), the elongated structure 124 in FIG. 14C is an outwardly arcing elongated structure, and the elongated structure 124 in FIG. 14D is an inwardly arcing elongated structure. In some embodiments, designing the elongated structures 124 with different lateral widths can effectively adjust the location of the center of mass of the stiffening member 120. In some embodiments, changing the stiffness of the reinforcing member 120 itself without changing the mass of the reinforcing member 120 changes the stiffness Kt1 provided to the system by the reinforcing member 120, the elastic element 110 (particularly the area covered by the reinforcing member 120 in the central region 112), and further changes the resonant frequency of the reversal motion of the mass Mt1-spring Kt1-damping Rt1 system, thereby changing the third resonant frequency of the vibrating assembly 100.

[0187] In some embodiments, by changing the design of the width of the elongated structure 124, the local stiffness can be varied at different locations extending from the center to the periphery of the elongated structure 124. When the driving end frequency is close to the resonant frequency of the mass Mt1-spring Kt1-damping Rt1 system, the connection region 115 between the fixed region 116 and the edge region 114, the edge region 114, and the suspended region between the region of the central region 112 covered by the reinforcing member 120 and the edge region 114 are driven to vibrate by the reinforcing member 120, resulting in a resonant peak adjustable with a 3 dB bandwidth.

[0188] 14A to 14D , in some embodiments, by designing the elongated structure 124 to have an inverted trapezoidal shape or an outer arc shape (an outwardly protruding arc is defined as an outer arc and an inwardly concave arc is defined as an inner arc, and the outer arc may be a circular arc, an ellipse, a high-order function arc, or any other outer arc), the third resonance peak of the vibrating assembly 100 can be obtained with a wide 3 dB bandwidth, which is applicable to scenarios requiring a low Q value and a wide bandwidth. In some embodiments, by designing the elongated structure 124 to have a trapezoidal shape, a rectangular shape, or an inner arc shape (an outwardly protruding arc is defined as an outer arc and an inwardly concave arc is defined as an inner arc, and the inner arc may be a circular arc, an ellipse, a high-order function arc, or any other inner arc), the third resonance peak of the vibrating assembly 100 can be obtained with high sensitivity and a small 3 dB bandwidth, which is applicable to scenarios requiring a high Q value and high local sensitivity.

[0189] By designing the elongated structures 124 with different lateral widths, the area of ​​one or more suspension regions corresponding to the central region 112 of the reinforcing member 120 can be further adjusted, thereby adjusting the area of ​​each equivalent mass Mm i , equivalent stiffness Ka i , Ka i ', equivalent damping Ra i , Ra i Furthermore, the fourth resonant peak position of the vibrating assembly 100 changes.

[0190] Therefore, by designing elongated structures 124 with different lateral widths, the frequency position of the third resonant peak of the vibrating assembly 100, the 3 dB bandwidth at the resonant peak, the sensitivity of the vibrating assembly 100 at the resonant peak, and the position of the fourth resonant peak of the vibrating assembly 100 can be adjusted.

[0191] 15A and 15B, which are schematic diagrams of vibrating assemblies having different shaped elongated structures according to some embodiments herein, the elongated structure 124 in FIG. 15A is a rotational shape, and the elongated structure 124 in FIG. 15B is an S-shape. In some embodiments, designing the elongated structure 124 with different lateral shapes adjusts the stiffness of the stiffening member 120 to change the stiffness Kt1 provided to the system by the stiffening member 120 and the elastic element 110 (particularly the area covered by the stiffening member 120 in the central region 112), and further changes the resonant frequency of the reversal motion of the mass Mt1-spring Kt1-damper Rt1 system, thereby changing the third resonance position of the vibrating assembly 100. In some embodiments, the area of ​​one or more suspension regions corresponding to the central region 112 of the stiffening member can be further adjusted to change the stiffness Kt1 of each equivalent mass Mt1. i , equivalent stiffness Ka i , Ka i ', equivalent damping Ra i , Ra i ' changes, thereby changing the fourth resonance peak position of the vibrating assembly 100. In some embodiments, designing the elongated structures 124 with different lateral shapes can further adjust the stress distribution within the stiffening member 120 and control the processing deformation of the stiffening member 120.

[0192] 16A-16E, which are schematic diagrams of reinforcing members having elongated structures of different shapes according to some embodiments of the present disclosure. In some embodiments, to precisely adjust the influence of the elongated structures of different shapes on the resonant peaks (e.g., the first, third, and fourth resonant peaks) of the vibrating assembly, for an elongated structure 124 whose width gradually decreases from the center to the edges, the included spoke angle θ is defined as the included angle between two sides of the shape of the projection of the elongated structure onto a projection plane perpendicular to the vibration direction. By setting θ, the resonant peak of the vibrating assembly can be adjusted. In some embodiments, for an elongated structure 124 whose sides are straight (as shown in FIGS. 16A-16C), the included angle θ is the included angle between two sides of the spokes. In some embodiments, for an elongated structure 124 with arcuate sides (as shown in FIG. 16E ), the included angle θ is the angle between the tangents to the two sides of the elongated structure 124. In some embodiments, to precisely adjust the effect of differently shaped elongated structures on the resonant peaks (e.g., the first resonant peak, the third resonant peak, and the fourth resonant peak) of the vibrating assembly, the included spoke angle θ is set to θ for a spoke structure with a gradually increasing width from the center to the edge, as shown in FIG. i and θ i In some embodiments, for an elongated structure 124 with straight sides, the included angle θ i is the included angle between the two sides of the spoke. In some embodiments, for elongated structures 124 whose sides are arcs, the included angle θ i is the included angle between the tangents to the two sides of the spoke.

[0193] In some embodiments, the included angle θ (or θ i), the stiffness Kt1 provided to the system by the stiffening member 120 and the elastic element 110 can be changed by changing the stiffness of the stiffening member 120 itself while keeping the mass of the stiffening member 120 unchanged or changed. This changes the resonant frequency of the reversal motion of the mass Mt1-spring Kt1-damping Rt1 system, thereby changing the third resonance position of the vibrating assembly 100 and controlling the 3 dB bandwidth of the third resonance peak of the vibrating assembly 100. In some embodiments, the included angle θ (or θ i ) can effectively increase the 3 dB bandwidth of the third resonance peak of the vibrating assembly 100.

[0194] In response to the frequency response of some vibrating assemblies 100 requiring a low Q factor and a wide bandwidth, the included angle θ (or θ i ) can be designed to be large. In some embodiments, the included angle θ of the elongated structure 124 can be in the range of 0 to 150°. In some embodiments, the included angle θ of the elongated structure 124 can be in the range of 0 to 120°. In some embodiments, the included angle θ of the elongated structure 124 can be in the range of 0 to 90°. In some embodiments, the included angle θ of the elongated structure 124 can be in the range of 0 to 80°. In some embodiments, the included angle θ of the elongated structure 124 can be in the range of 0 to 60°. In some embodiments, the included angle θ of the elongated structure 124 i may range from 0 to 90 degrees. In some embodiments, the included angle θ of the elongated structure 124 i may be in the range of 0 to 80°. In some embodiments, the included angle θ of the elongated structure 124 i may be in the range of 0 to 70°. In some embodiments, the included angle θ of the elongated structure 124 i may be in the range of 0 to 60°. In some embodiments, the included angle θ of the elongated structure 124 i may be in the range of 0 to 45°.

[0195] In response to the frequency response of some vibrating assemblies 100 requiring a high Q and narrow bandwidth, the included angle θ (or θ i ) can be designed to be small. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of 0 to 90°. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of 0 to 80°. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of 0 to 70°. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of 0 to 60°. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of 0 to 45°. In some embodiments, the included angle θ of the elongated structure 124 i may be in the range of 0 to 60°. In some embodiments, the included angle θ of the elongated structure 124 i may be in the range of 0 to 80°. In some embodiments, the included angle θ of the elongated structure 124 i may range from 0 to 90 degrees. In some embodiments, the included angle θ of the elongated structure 124 i may range from 0 to 120°. In some embodiments, the included angle θ of the elongated structure 124 i may be in the range of 0 to 150°.

[0196] In some embodiments, θ and θ i The relationship between is defined as follows:

[0197]

number

[0198] To accommodate the frequency response of some speakers requiring a low Q factor and a wide bandwidth, the included angle θ of the elongated structure 124 can be designed to be large. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of −90° to 150°. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of −45° to 90°. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of 0° to 60°.

[0199] To accommodate the frequency response of some speakers requiring a high Q factor and narrow bandwidth, the included angle θ of the elongated structure 124 can be designed to be small. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of −150° to 90°. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of −90° to 45°. In some embodiments, the included angle θ of the elongated structure 124 may be in the range of −60° to 0°.

[0200] In some embodiments, for an irregularly shaped elongated structure 124, the included angle of the elongated structure 124 cannot be designed. In this case, the area method can be used for design. By changing the stiffness of the stiffening member 120 itself while keeping the mass of the stiffening member 120 unchanged or changing it, the stiffness Kt1 provided to the system by the stiffening member 120 and the elastic element 110 can be changed. Furthermore, by changing the resonant frequency of the reversal motion of the mass Mt1-spring Kt1-damping Rt1 system, the third resonance position of the vibrating assembly 100 can be changed, and the 3 dB bandwidth of the third resonance peak of the vibrating assembly 100 can be controlled.

[0201] 16F is a schematic diagram of a frequency response curve of a vibration assembly according to some other embodiments of the present disclosure. The structure of the vibration assembly is designed to couple the second and third resonance peaks 220 and 230 of the vibration assembly, resulting in only two resonance peaks on the frequency response curve of the vibration assembly. FIG. 16F shows the frequency response curves of the vibration assembly when the included angle θ of the elongated structure 124 is 20°, 10°, and 1°, respectively. As shown in FIG. 16F, with an increase in the included angle θ, the 3 dB bandwidth of the mid- to high-frequency resonance peak of the vibration assembly (e.g., the resonance peak formed by combining the second and third resonance peaks 220 and 230) gradually increases. Therefore, the 3 dB bandwidth of the mid- to high-frequency resonance peak of the vibration assembly can be adjusted by adjusting the included angle θ of the elongated structure 124. In some embodiments, by setting the included angle θ of the elongated structure 124 in the range of −60° to 60°, the 3 dB bandwidth of at least one medium to high frequency resonance peak of the vibrating assembly can be made to be 1000 Hz or greater.

[0202] 17A and 17B, which are schematic diagrams of a reinforcing member having an irregular elongated structure according to some embodiments of the present disclosure. In some embodiments, to precisely design the irregular elongated structure to adjust the resonance peak of the vibrating assembly, as shown in FIG. 17A, a circle with a radius R is defined by the maximum contour of the reinforcing member 120, and half of the radius R of the circle defined by the maximum contour is defined as radius R / 2. The horizontal projection area of ​​the reinforcing member 120 within the radius R / 2 range is defined as S. in and the horizontal projection area (i.e., projection along the vibration direction of the vibrating assembly) of the reinforcing member 120 within the range between the circle of radius R / 2 and the circle of radius R is defined as S out and the physical quantity τ is defined as the horizontal projection area S of the reinforcing member 120. out and the horizontal projection area S of the reinforcing member 120 in Relative to

number

[0203] In some embodiments, the horizontal projected area S of the reinforcing member 120 out and the horizontal projection area S of the reinforcing member 120 in By adjusting the ratio τ between τ and τ, the mass distribution of the stiffening member 120 can be controlled, thereby controlling the bandwidth of the third resonance peak of the vibrating assembly 100. In the case of other types of regular stiffening member 120 structures, such as elliptical, rectangular, square, or other polygonal structures as shown in FIG. 17B, a figure similar to the stiffening member 120 is defined and enveloped by the maximum outline of the stiffening member 120, and the central region of the figure is defined as a reference point, and the distance from the reference point to each point on the outline envelope is defined as R (e.g., R i , …, R i+3 ) and all corresponding R / 2 (e.g., R i / 2, …, R i+3 The horizontal projection area of ​​the reinforcing member 120 in the area formed by the points S in The horizontal projection area of ​​the reinforcing member 120 within the range between the distance R / 2 and the distance R is S out In the case of the structure of another irregular reinforcing member 120, the maximum contour is enveloped by a regular shape of a structure that is more similar to the maximum contour, and S in , S out , and define the ratio τ.

[0204] To accommodate the frequency response of some vibrating assemblies 100 requiring a low Q factor and a wide bandwidth, the stiffening member 120 can be designed with a large concentrated mass in the central region. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 0.3 to 2. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 0.5 to 1.5. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 0.5 to 1.2. out and horizontal projection area S inThe ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 0.5 to 1.3. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 0.5 to 1.4. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 0.3 to 1.2. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 0.3 to 1.6. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 0.5 to 2. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 0.5 to 2.2. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 0.3 to 2.2. out and horizontal projection area S in The ratio τ to may be in the range of 0.3 to 2.

[0205] To accommodate the high Q, narrow bandwidth required frequency response of some vibrating assemblies 100, the stiffening member 120 can be designed with a large concentrated mass at the edge region. In some embodiments, the horizontal projected area S out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 1 to 3. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 1.2 to 2.8. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 1.4 to 2.6. out and horizontal projection area S inThe ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 1.6 to 2.4. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 1.8 to 2.2. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 1.2 to 2. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 1 to 2. out and horizontal projection area S in The ratio τ of the horizontal projection area S to the horizontal projection area S may be in the range of 2 to 2.8. out and horizontal projection area S in The ratio τ to may be in the range of 2 to 2.5.

[0206] In some embodiments, the horizontal projected area S out and horizontal projection area S in By adjusting the range of the ratio τ between τ and τ, the resonant frequency of the reversing motion during vibration of the vibrating assembly can be changed, thereby changing the position of the third resonant peak. FIG. 17C is a schematic diagram of a frequency response curve of a vibrating assembly according to some other embodiments of the present specification. As shown in FIG. 17C, the frequency response curves of the vibrating assembly when τ is 1.68 and 1.73 are shown, respectively. The 3 dB bandwidth at the third resonant peak 230 of the two frequency response curves is narrow. When τ increases from 1.68 to 1.73, the third resonant peak 230 moves to a lower frequency. Therefore, as τ increases, the frequency corresponding to the third resonant peak 230 decreases. Adjusting the τ of the vibrating assembly can effectively adjust the bandwidth and position of the third resonant peak.

[0207] In some embodiments, the fourth resonance peak can be adjusted by adjusting the number of annular structures 122 (for example, within a range of 1 to 10) and changing the area of ​​the openwork region of the reinforcing member 120 (the hanging region corresponding to the central region 112 within the projection range of the reinforcing member 120) to adjust the relationship between the area of ​​the openwork region and the thickness of the elastic element 110 (area-thickness ratio μ); the fourth resonance peak can be adjusted by changing the relationship between the areas of the openwork regions of different annular structures 122 of the reinforcing member 120 (openwork region area ratio γ); or the first resonance peak, the third resonance peak, and the fourth resonance peak can be adjusted by changing the relationship between the lateral areas of the reinforcing portion of the reinforcing member 120 and the reinforcing member 120 (lateral area ratio β between the reinforcing portion of the reinforcing member 120 and the reinforcing member 120).

[0208] In some embodiments, the annular structure 122 may include a first annular structure and a second annular structure having overlapping centers of gravity, wherein the radial dimension of the first annular structure is smaller than the radial dimension of the second annular structure. In some embodiments, the elongated structure 124 may further include at least one first elongated structure and at least one second elongated structure, wherein the at least one first elongated structure is disposed inside and connected to the first annular structure, and the at least one second elongated structure is disposed between and connected to the first and second annular structures, respectively, to form a plurality of distinct openwork regions in the reinforcing member 120.

[0209] 18A-18C, which are schematic diagrams of vibration assemblies having different numbers of annular structures according to some embodiments of the present disclosure, the annular structure 122 in FIG. 18A is a single annular structure, the annular structure 122 in FIG. 18B is a double annular structure, and the annular structure 122 in FIG. 18C is a three-annular structure. By designing the number of annular structures 122, it is possible to adjust the mass and stiffness of the reinforcing member 120 and the area of ​​the openwork region in the central region 112. In some embodiments, the number of annular structures 122 may be in the range of 1 to 10. In some embodiments, the number of annular structures 122 may be in the range of 1 to 5. In some embodiments, the number of annular structures 122 may be in the range of 1 to 3.

[0210] In some embodiments, by adjusting the number of annular structures 122, the mass of the stiffening member 120 can be adjusted to change the total equivalent mass Mt formed by combining the mass of the stiffening member 120, the mass of the elastic element 110, the equivalent air mass, and the equivalent drive end mass, thereby changing the resonant frequency of the mass Mt-spring Kt-damping Rt system, which in turn changes the primary resonant frequency of the vibrating assembly 100.

[0211] In some embodiments, adjusting the number of annular structures 122 can further adjust the stiffness of the stiffening member 120 to change the stiffness Kt1 provided to the system by the stiffening member 120, the elastic element 110 (especially the area covered by the stiffening member 120 in the central region 112), and further change the resonant frequency of the reversal motion of the mass Mt1-spring Kt1-damping Rt1 system, thereby changing the third resonance position of the vibrating assembly 100. In some embodiments, adjusting the number of annular structures 122 can further vary the stiffness distribution at different positions extending from the center to the periphery of the elongated structure 124, and when the driving end frequency is close to the resonant frequency of the mass Mt1-spring Kt1-damping Rt1 system, the connection region 115, the edge region 114, and the local suspension region between the area covered by the stiffening member 120 in the central region 112 and the edge region 114 can be driven by the stiffening member 120 to vibrate, resulting in a tunable resonance peak with a 3 dB bandwidth.

[0212] In some embodiments, the number of annular structures 122 can be adjusted, and the area of ​​the openwork regions in the central region 112 can be adjusted to adjust the equivalent mass Mm i , equivalent stiffness Ka i , Ka i ', equivalent damping Ra i , Ra i ' can be varied, thereby changing the fourth resonant peak position of the vibrating assembly 100.

[0213] In some embodiments, by adjusting the number of annular structures 122, the dimensions of the outermost annular structure 122 can be further adjusted to adjust the area of ​​the local openwork area between the area of ​​the central region 112 covered by the reinforcing members 120 and the edge region 114, and the three parts, that is, the area, the connection region 115, and the edge region 114, can form an equivalent mass Ms, an equivalent stiffness Ks, and an equivalent damping Rs. The area of ​​the local suspension area between the area of ​​the central region 112 covered by the reinforcing members 120 and the edge region 114 can change the resonant frequency of the mass Ms-spring Ks-damping Rs system, thereby realizing the adjustment of the second resonant peak position of the vibrating assembly 100.

[0214] In some embodiments, by adjusting the number of annular structures 122, the fourth resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and each openwork area S i and the thickness H of the diaphragm in each openwork area i The area-thickness ratio μ is in the range of 150 mm to 700 mm, and the openwork area S of any two elastic elements 110 ki and S ji The ratio γ of the reinforcing portion of the reinforcing member 120 to the reinforcing portion of the reinforcing member 120 is in the range of 0.25 to 4, and the lateral area ratio β of the reinforcing portion of the reinforcing member 120 to the reinforcing portion of the reinforcing member 120 is in the range of 0.2 to 0.7. In some embodiments, by adjusting the number of the annular structures 122, the fourth resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and the area S of each openwork region is i and the thickness H of the diaphragm in each openwork area i The area-thickness ratio μ is in the range of 100 mm to 1000 mm, and the openwork area S of any two elastic elements 110 ki and S ji The ratio γ of the area of ​​the reinforcing portion of the reinforcing member 120 to the area of ​​the reinforcing member 120 in the horizontal direction is in the range of 0.1 to 10, and the ratio β of the area of ​​the reinforcing portion of the reinforcing member 120 to the area of ​​the reinforcing member 120 in the horizontal direction is in the range of 0.1 to 0.8.

[0215] 19 is a schematic diagram of a vibrating assembly in which the inner and outer ring elongated structures are discontinuous, according to some embodiments herein. In some embodiments, when the vibrating assembly 100 includes at least two annular structures, the annular structures 122 divide the elongated structure 124 into multiple regions along the extension direction from the center to the periphery, and the elongated structures 124 within each region may be continuous or discontinuous. In some embodiments, the one or more annular structures 122 of the vibrating assembly 100 may include at least a first annular structure 1221. For example, the annular structures 122 may include a first annular structure 1221 and a second annular structure 1222 whose centers of gravity overlap, and the radial dimension of the first annular structure 1221 is smaller than the radial dimension of the second annular structure 1222. In some embodiments, the elongated structure 124 may include at least one first elongated structure 1241 and at least one second elongated structure 1242, where any of the first elongated structures 1241 is disposed at a first location inside the first annular structure 1221 and connected to the first annular structure 1221, and any of the second elongated structures 1242 is connected at a second location outside the first annular structure 1221. The multiple first elongated structures 1241 are connected to the multiple first locations, and the multiple second elongated structures 1242 are connected to the multiple second locations, and in some embodiments, a line connecting at least one first location to the center of the first annular structure 1221 does not pass through any of the second locations. In some embodiments, a line connecting at least one second location to the center of the first annular structure 1221 does not pass through any of the first locations. In some embodiments, the plurality of first locations and the plurality of second locations are different, i.e., the first location, the second location, and the center of the first annular structure 1221 are not collinear, and the connection location of the first elongated structure 1241 to the first annular structure 1221 may be different from the connection location of the second elongated structure 1242 to the first annular structure 1221. In some embodiments, the number of first elongated structures 1241 and the number of second elongated structures 1242 may be the same or different.

[0216] By discontinuously arranging the elongated structures 124 in the inner and outer regions of the annular structure 122, it is possible to achieve different numbers of elongated structures 124 in the inner and outer regions of the annular structure 122, different lateral widths of the elongated structures 124 in the inner and outer regions, and different lateral shapes of the elongated structures 124 in the inner and outer regions, thereby making it possible to adjust the mass, stiffness, and center of mass distribution of the reinforcing member 120, and the number and area of ​​the openwork regions in the central region 112, over a wide range.

[0217] In some embodiments, adjusting the mass of the stiffening member 120 can adjust and change the total equivalent mass Mt, thereby changing the resonant frequency of the formed mass Mt-spring Kt-damping Rt system, which in turn changes the primary resonant frequency of the vibrating assembly 100. Adjusting the stiffness of the stiffening member 120 can adjust the resonant frequency of the reversing motion of the mass Mt1-spring Kt1-damping Rt1 system, thereby changing the third resonant position of the vibrating assembly 100, and by varying the stiffness distribution at different positions extending from the center to the periphery of the elongated structure 124, a third resonant peak of the vibrating assembly 100 that can be adjusted with a 3 dB bandwidth can be obtained. Adjusting the number and area of ​​the openwork regions in the central region 112 can change the fourth resonant peak position and sensitivity of the vibrating assembly 100.

[0218] In some embodiments, by discontinuously placing the elongated structures 124 in the inner and outer regions of the annular structure 122, the fourth resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and each openwork region area S i and the thickness H of the elastic element 110 of each openwork area portion. i The area-thickness ratio μ is in the range of 150 mm to 700 mm, and the openwork area S of any two elastic elements 110 ki and S jiThe ratio γ of the reinforcing portion of the reinforcing member 120 to the reinforcing portion of the reinforcing member 120 is in the range of 0.25 to 4, and the lateral area ratio β of the reinforcing portion of the reinforcing member 120 to the reinforcing portion of the reinforcing member 120 is in the range of 0.2 to 0.7. In some embodiments, by discontinuously arranging the elongated structures 124 in the inner and outer regions of the annular structure 122, the fourth resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and the area S of each openwork region is i and the thickness H of the diaphragm in each openwork area i The area-thickness ratio μ is in the range of 100 mm to 1000 mm, and the openwork area S of any two elastic elements 110 ki and S ji The ratio γ of the area of ​​the reinforcing portion of the reinforcing member 120 to the area of ​​the reinforcing member 120 in the horizontal direction is in the range of 0.1 to 10, and the ratio β of the area of ​​the reinforcing portion of the reinforcing member 120 to the area of ​​the reinforcing member 120 in the horizontal direction is in the range of 0.1 to 0.8.

[0219] 20A, which is a schematic diagram of a vibration assembly having multiple annular structures, according to some embodiments of the present disclosure. In some embodiments, the multiple annular structures 122 can be designed to have different spacing regions between the multiple annular structures 122, and the number of elongated structures 124 in different spacing regions can be designed to achieve a mass distribution design for the stiffening member 120. Note that the elongated structures 124 designed for the spacing regions of each annular structure 122 may be different in number, shape, or position.

[0220] In some embodiments, the annular structures 122 are defined from the center outward as the first annular structure 1221, the second annular structure 1222, the third annular structure 1223, ... the nth annular structure, and the elongated structures 124 in the gap region between the nth annular structure and the n-1th annular structure are defined as the nth elongated structures (e.g., the first elongated structure 1241, the second elongated structure 1242, the third elongated structure 1243), and the number of the nth elongated structures (i.e., the elongated structures connected to the inside of the nth annular structure) is defined as Q n where n is a natural number. The physical quantity q can be defined as the number Q of any i-th long structures. i and the number of j-th long structures Q j It is defined as the ratio of

[0221]

number

[0222] In some embodiments, the number Q of any i-th elongated structure i and the number of j-th long structures Q j The ratio q of the number of elongated structures Q to the number of elongated structures Q may be in the range of 0.05 to 20. i and the number of j-th long structures Q j The ratio q of the number of elongated structures Q to any i-th elongated structure may be in the range of 0.1 to 10. i and the number of j-th long structures Q j The ratio q of the number of elongated structures Q to any i-th elongated structure may be in the range of 0.1 to 8. i and the number of j-th long structures Q j The ratio q of the number of elongated structures Q to any i-th elongated structure may be in the range of 0.1 to 6. i and the number of j-th long structures Q j The ratio q of the number of elongated structures Q to any i-th elongated structure may be in the range of 0.2 to 5. i and the number of j-th long structures Q j The ratio q of the number of elongated structures Q to any i-th elongated structure may be in the range of 0.3 to 4. i and the number of j-th long structures Q j The ratio q of the number of elongated structures Q to any i-th elongated structure may be in the range of 0.5 to 6. i and the number of j-th long structures Q j The ratio q of the number of elongated structures Q to any i-th elongated structure may range from 1 to 4. i and the number of j-th long structures Q j The ratio q of the number of elongated structures Q to any i-th elongated structure may be in the range of 1 to 2. i and the number of j-th long structures Q j The ratio q may be in the range of 0.5 to 2.

[0223] In some embodiments, the mass distribution of the reinforcement member 120 is designed by designing multiple annular structures 122, designing the spacing areas of the multiple annular structures 122, and designing the number of elongated structures 124 in different spacing areas; further, by changing the stiffness of the reinforcement member 120 under the condition that the mass of the reinforcement member 120 is not changed or is changed, the equivalent stiffness Kt1 of the reinforcement member 120 and the diaphragm changes, and further, the resonant frequency of the inverted motion of the mass Mt1-spring Kt1-damping Rt1 system changes, thereby changing the third resonant peak position of the speaker.

[0224] 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 assembly when q = 0.67 and q = 0.1, respectively. 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 q, the amplitude of the third resonance peak can be controlled and changed, thereby adjusting the sensitivity of the vibration assembly. In some embodiments, when q is in the range of 0.2 to 5, the vibration assembly has high sensitivity.

[0225] In some embodiments, the shape of the annular structure 122 may include at least one of a circular annular shape, an elliptical annular shape, a polygonal annular shape, and a curved annular shape. By designing the annular structure 122 with different shapes and / or different dimensions, the mass and stiffness of the reinforcing member 120 can be adjusted, and the area of ​​the openwork region of the central region 112 can be adjusted.

[0226] In some embodiments, the size and shape of suspension region 1121 may be adjusted by the size and shape of the area of ​​central region 112 covered by reinforcing member 120 and the size and shape of reinforcing member 120. In some embodiments, the area and shape of edge region 114 can be adjusted to adjust the total horizontal projected area (i.e., projected along the vibration direction of the vibrating assembly) of suspension region 1121 and edge region 114. By controlling data such as the total horizontal projected area of ​​suspension region 1121 and edge region 114, the thickness of elastic element 110, and the arch height of the edge, the second resonance peak of vibrating assembly 100 can be accurately controlled to a desired frequency band. In some embodiments, the second resonance peak of vibrating assembly 100 may be in the range of 3000 Hz to 7000 Hz. In some embodiments, by controlling the area ratio between the suspension region 1121 and the edge region 114, the vibration displacement of the local region in the frequency band of the second resonant peak of the vibration assembly 100 can be adjusted, thereby maximizing the output sensitivity at the second resonant peak position of the vibration assembly 100.

[0227] In some embodiments, by setting the relationship between the dimensions of the edge region 114 and the suspension region 1121 of the vibrating assembly 100 and the thickness of the elastic element 110, it is possible to control the local equivalent mass Mm3, the local equivalent mass Mm2, the local area stiffness Ka2', and the local area stiffness Ka1', and further ensure that the second resonance peak of the vibrating assembly 100 is in a desired frequency range. s and the thickness of the diaphragm H i By setting the ratio α between 5000 mm and 12000 mm, the second resonance peak of the vibrating assembly 100 is in the range of 3000 Hz to 7000 Hz. s and the thickness of the diaphragm H i By setting the ratio α to be in the range of 6000 mm to 10000 mm, the second resonance peak of the vibrating assembly 100 is in the range of 3000 Hz to 7000 Hz.

[0228] In some embodiments, by designing the edge arch height based on the relationship between the dimensions of the edge region 114 and the hanging region 1121 and the dimension of the edge arch height of the edge region 114, it is possible to change the three-dimensional dimensions of the edge region 114 of the elastic element 110 without changing the horizontal projection area of ​​the edge region 114 and the hanging region 1121, thereby changing the stiffness Ka1′ of the edge region 114, and further controlling the second resonance peak of the vibrating assembly 100. s The ratio δ of the edge arch height Δh to the width S may be in the range of 50 mm to 600 mm. s The ratio δ of the edge arch height Δh to the width S may be in the range of 100 mm to 500 mm. s The ratio δ of the width of the groove to the arch height Δh of the edge may be in the range of 200 mm to 400 mm.

[0229] In some embodiments, the relationship between the dimensions of the suspension region 1121 and the area of ​​the central region 112 causes the stiffening member 120 to undergo a constant bending deformation in the frequency band, realizing enhancement and cancellation of the sound pressure superposition in different regions of the elastic element 110, thereby realizing maximum sound pressure level output. In some embodiments, the horizontal projection area S of the suspension region 1121 v and the horizontal projection area S of the center of the diaphragm of the vibration assembly 100 c Relative to

number

number

number

[0230] 21A-21E, which are schematic structural diagrams of vibrating assemblies having different structures according to some embodiments of the present disclosure. In some embodiments, the outer contour of the reinforcing member 120 may be a structure with outwardly extending spokes (as shown in FIG. 21A), a circular, elliptical, or curved ring structure (as shown in FIG. 21B), a polygon, other irregular ring structure, etc., and the polygon may include a triangle, a square, a pentagon, a hexagon (as shown in FIGS. 21C-21D), a heptagon, an octagon, a nonagon, a decagon, etc. In some embodiments, the elastic element 110 may be a polygon, such as a triangle, a square (as shown in Figures 21D and 21E), a pentagon, a hexagon, a heptagon, an octagon, a nonagon, a decagon, etc., and other irregular shapes, and accordingly, the reinforcing member 120 may be designed to have a similar or dissimilar structure, thereby controlling the shape of the suspension region 1121 by the shape of the edges of the reinforcing member 120, the central region 112, and the edge region 114, thereby realizing adjustment of the performance of the vibrating assembly 100.

[0231] As shown in FIG. 22, FIG. 22 is a schematic diagram of a vibration assembly with annular structures of unequal widths, according to some embodiments of the present disclosure. In some embodiments, designing local structures of unequal widths at different positions of any of the annular structures 122 effectively adjusts the mass of the stiffening member 120, thereby adjusting and varying the total equivalent mass Mt, thereby changing the resonant frequency of the formed mass Mt-spring Kt-damping Rt system, and further changing the primary resonant frequency of the vibration assembly 100. Designing local structures of unequal widths at different positions (e.g., adjacent positions) of any of the annular structures 122 can adjust the stiffness and center of mass distribution of the stiffening member 120, thereby adjusting the resonant frequency of the reversal motion of the mass Mt1-spring Kt1-damping Rt1 system and changing the third resonant position of the vibration assembly 100. Designing the annular structures 122 with unequal widths further results in different stiffness distributions at different positions extending from the center to the periphery of the elongated structure 124, resulting in a third resonant peak of the vibration assembly 100 that can be adjusted with a 3 dB bandwidth. Furthermore, by designing the annular structures 122 with unequal widths, the number and area of ​​the suspension regions in the central region 112 can be further adjusted to change the fourth resonance peak position and sensitivity of the vibrating assembly 100. For example, as shown in Fig. 22, the radial widths are different on both sides of the connection position between at least one of the one or more annular structures 122 and any two of the one or more elongated structures 124. Also, for example, the circumferential widths between the connection positions between at least one of the one or more annular structures 122 and any two of the one or more elongated structures 124 are different.

[0232] In some embodiments, by designing a local structure of unequal width at any position (e.g., adjacent positions) of any of the annular structures 122, the fourth resonance peak of the vibrating assembly 100 is in the range of 15 kHz to 18 kHz, and each openwork area S i and the thickness H of the elastic element 110 of each openwork area portion. i The area-thickness ratio μ is in the range of 150 mm to 700 mm, and the openwork area S of any two elastic elements 110 ki and S jiThe ratio γ of the reinforcing portion of the reinforcing member 120 to the reinforcing portion of the reinforcing member 120 is in the range of 0.25 to 4, and the lateral area ratio β of the reinforcing portion of the reinforcing member 120 to the reinforcing portion of the reinforcing member 120 is in the range of 0.2 to 0.7. In some embodiments, by designing a local structure with an unequal width at any position of any of the annular structures 122, the fourth resonance peak of the vibrating assembly 100 is in the range of 15 kHz to 18 kHz, and the area S of each openwork region i and the thickness H of the diaphragm in each openwork area i The area-thickness ratio μ is in the range of 100 mm to 1000 mm, and the openwork area S of any two elastic elements 110 ki and S ji The ratio γ of the area of ​​the reinforcing portion of the reinforcing member 120 to the area of ​​the reinforcing member 120 in the horizontal direction is in the range of 0.1 to 10, and the ratio β of the area of ​​the reinforcing portion of the reinforcing member 120 to the area of ​​the reinforcing member 120 in the horizontal direction is in the range of 0.1 to 0.8.

[0233] 23, which is a schematic diagram of a vibration assembly having an irregular annular structure according to some embodiments of the present disclosure. In some embodiments, by designing local structures at different positions of different annular structures 122, such as circular, rectangular, square, triangular, hexagonal, octagonal, other polygonal, elliptical, and other irregular annular structures 122, the size, position, and shape of the local area of ​​the annular structure 122 can be more flexibly controlled, and the mass of the stiffening member 120 can be effectively adjusted, and the total equivalent mass Mt can be adjusted and changed, thereby changing the resonant frequency of the formed mass Mt-spring Kt-damping Rt system, and further changing the first resonant frequency of the vibration assembly 100. By adjusting the stiffness of the stiffening member 120 and the distribution of the center of mass of the stiffening member 120, the resonant frequency of the reversal motion of the mass Mt1-spring Kt1-damping Rt1 system can be adjusted, thereby changing the third resonant peak position of the vibrating assembly 100. The stiffness distribution at different positions extending from the center to the periphery of the elongated structure 124 is different, and the third resonant peak of the vibrating assembly 100 can be adjusted with a 3 dB bandwidth. And by effectively adjusting the number and area of ​​the suspension regions in the central region 112, the fourth resonant peak position and sensitivity of the vibrating assembly 100 can be changed. In addition, by designing an irregular structure, stress concentration can be effectively avoided, and the deformation of the stiffening member 120 can be made smaller.

[0234] In some embodiments, as shown in FIG. 23 , the reinforcing member 120 includes a double annular structure, which includes an inner first annular structure 1221 and an outer second annular structure 1222. In some embodiments, the first annular structure 1221 and the second annular structure 1222 may have different shapes. In some embodiments, the first annular structure 1221 may be a curved annular structure, and the second annular structure 1222 may be a circular annular structure. In some embodiments, by designing the irregular annular structure 122, the fourth resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and each openwork area S i and the thickness H of the diaphragm in each openwork area iThe area-thickness ratio μ is in the range of 150 mm to 700 mm, and the openwork area S of any two diaphragms ki and S ji The ratio γ of the reinforcing portion of the reinforcing member 120 to the reinforcing portion of the reinforcing member 120 is in the range of 0.25 to 4, and the lateral area ratio β of the reinforcing portion of the reinforcing member 120 to the reinforcing portion of the reinforcing member 120 is in the range of 0.2 to 0.7. In some embodiments, by designing the irregular annular structure 122, the fourth resonance peak of the vibrating assembly 100 is in the range of 15 kHz to 18 kHz, and each openwork area S i and the thickness H of the diaphragm in each openwork area i The area-thickness ratio μ is in the range of 100 mm to 1000 mm, and the openwork area S of any two elastic elements 110 ki and S ji The ratio γ of the area of ​​the reinforcing portion of the reinforcing member 120 to the area of ​​the reinforcing member 120 in the horizontal direction is in the range of 0.1 to 10, and the ratio β of the area of ​​the reinforcing portion of the reinforcing member 120 to the area of ​​the reinforcing member 120 in the horizontal direction is in the range of 0.1 to 0.8.

[0235] 24A-24B, FIG. 24A is a schematic diagram of a vibration assembly including a stepped elongated structure according to some embodiments of the present disclosure. FIG. 24B is a schematic diagram of a vibration assembly including a stepped elongated structure according to other embodiments of the present disclosure. In some embodiments, as shown in FIG. 24A, by designing a reinforcing member 120 including a stepped elongated structure 124, it is possible to ensure that the stiffness, mass, and center of mass distribution of the reinforcing member 120 are changed without controlling and changing the openwork area of ​​the central region 112 (affecting the fourth resonance peak of the vibration assembly 100) and the hanging area 1121 (affecting the second resonance peak of the vibration assembly 100). This can effectively adjust the first resonance peak position, the third resonance peak position, and the bandwidth of the vibration assembly 100 without changing the second resonance peak and the fourth resonance peak of the vibration assembly 100, thereby adjusting different frequency response curves according to actual application needs.

[0236] In some embodiments, by designing the thickness of different regions of the reinforcing member 120 in the thickness direction (i.e., along the vibration direction of the vibration assembly 100), it is possible to keep the mass of the reinforcing member 120 unchanged or changed according to the actually required mass distribution, while changing the stiffness of the reinforcing member 120 itself, so that the stiffness Kt1 provided to the system by the reinforcing member 120 and the elastic element 110 changes, and further changes the resonant frequency of the inverted motion of the mass Mt1-spring Kt1-damping Rt1 system, thereby changing the third resonance position of the vibration assembly 100, and further controlling the 3 dB bandwidth of the third resonance peak of the vibration assembly 100.

[0237] In some embodiments, the elongated structure 124 may have multiple steps with different thicknesses along the vibration direction of the elastic element 110, i.e., the elongated structure 124 has a step shape. In some embodiments, at least one of the multiple elongated structures has a step shape. In some embodiments, all of the multiple elongated structures have a step shape. FIG. 24B shows the structure of a reinforcing member 120 including step-shaped elongated structures 124 and its cross-sectional structure in a DD cross section. The thickness of the most peripheral step of the reinforcing member 120 structure (i.e., the first step that is the outermost in the radial direction of the elongated structure 124) is defined as h1, the thickness of the most inner step from the edge is defined as h2, and the thickness of the central step (i.e., the second step that is the innermost in the radial direction of the elongated structure 124) is defined as h1. n and the physical quantity ε is defined as the thickness of any two steps h j and h k It is defined as the ratio of (k>j).

[0238]

number

[0239] The physical quantity φ is defined as the thickness h1 of the outermost step of the structure of the reinforcing member 120 (i.e., the first step located at the outermost side in the radial direction of the elongated structure 124) and the thickness h of the central step (i.e., the second step located at the innermost side in the radial direction of the elongated structure 124). n It is defined as the ratio of

[0240]

number

[0241] In some embodiments, the thickness h of any two steps j and h k The ratio ε of the thickness h of any two steps is in the range of 0.1 to 10. j and h k The ratio ε of the thickness h of any two steps is in the range of 0.1 to 8. j and h k The ratio ε of the thickness h of any two steps is in the range of 0.2 to 8. j and h k The ratio ε of the thickness h of any two steps is in the range of 0.1 to 7. j and h k The ratio ε of the thickness h of any two steps is in the range of 0.1 to 6. j and h k The ratio ε of the thickness h of any two steps is in the range of 0.2 to 6. j and h k The ratio ε of the thickness h of any two steps is in the range of 0.2 to 5. j and h k The ratio ε to lies in the range of 0.25 to 4.

[0242] In some embodiments, the mass distribution of the reinforcing member 120 can be adjusted by designing the thickness of different regions of the reinforcing member 120, so that when the mass of the reinforcing member 120 is not changed or is changed, the stiffness of the reinforcing member 120 itself changes, and the stiffness Kt1 provided to the system from the reinforcing member 120 and the elastic element 110 changes, thereby adjusting the position of the third resonant peak of the vibration assembly 100 and controlling the 3 dB bandwidth of the third resonant peak of the vibration assembly 100.

[0243] FIG. 24C shows a frequency response curve of a vibration assembly according to some other embodiments of the present disclosure. The vibration assembly structure is designed to combine the second and third resonance peaks 220 and 230, resulting in only two resonance peaks on the frequency response curve. FIG. 24C shows the frequency response curves of the vibration assembly corresponding to ε = 1, ε = 0.68, and ε = 0.5, respectively. As shown in FIG. 24C, the positions of the mid- to high-frequency resonance peaks (e.g., the resonance peak formed by combining the second and third resonance peaks 220 and 230) on the frequency response curves corresponding to ε = 1, ε = 0.68, and ε = 0.5 are different, and the 3 dB bandwidths of the mid- to high-frequency resonance peaks (e.g., the resonance peak formed by combining the second and third resonance peaks 220 and 230) are also different. With a decrease in ε, the resonance frequency and 3 dB bandwidth of the mid- to high-frequency resonance peaks (e.g., the resonance peak formed by combining the second and third resonance peaks 220 and 230) of the vibration assembly gradually increase. Therefore, by adjusting ε, it is possible to adjust the frequency position and 3 dB bandwidth of the mid-to-high frequency resonance peak of the vibrating assembly. In some embodiments, the thickness h of any two steps can be adjusted. j and h k By setting the ratio ε to the frequency in the range of 0.25 to 4, the medium to high frequency resonance peak of the vibration assembly is in the range of 3000 Hz to 12000 Hz, and the resonance peak can have a wide 3 dB bandwidth.

[0244] To accommodate the frequency response of some vibrating assemblies 100 requiring a low Q and a wide bandwidth, the stiffening member 120 can be designed with a large mass concentrated near the center. In some embodiments, the stiffening member 120 structure has a step thickness h1 at the most edge and a step thickness h at the center. n The ratio φ of the thickness of the most peripheral step h1 to the thickness of the central step h2 of the reinforcing member 120 structure is in the range of 0.1 to 1. In some embodiments, n In some embodiments, the ratio φ between the thickness h1 of the most peripheral step and the thickness h of the central step of the reinforcing member 120 structure is in the range of 0.2 to 0.8. nIn some embodiments, the ratio φ between the thickness h1 of the most peripheral step and the thickness h of the central step of the reinforcing member 120 structure is in the range of 0.2 to 0.6. n The ratio φ to the value is in the range of 0.2 to 0.4.

[0245] To accommodate the high Q, narrow bandwidth requirements of some vibrating assemblies 100, the stiffening member 120 can be designed with a large mass concentrated at the edge region. In some embodiments, the stiffening member 120 structure has a step thickness h1 at the most edge and a step thickness h at the center. n The ratio φ of the thickness of the most peripheral step h1 to the thickness of the central step h2 of the reinforcing member 120 structure is in the range of 1 to 10. n The ratio φ of the thickness of the most peripheral step h1 to the thickness of the central step h2 of the reinforcing member 120 structure is in the range of 1.2 to 6. In some embodiments, n The ratio φ of the thickness of the most peripheral step h1 to the thickness of the central step h2 of the reinforcing member 120 structure is in the range of 2 to 6. In some embodiments, n The ratio φ of the thickness of the most peripheral step h1 to the thickness of the central step h2 of the reinforcing member 120 structure is in the range of 3 to 6. In some embodiments, n The ratio φ of the thickness of the most peripheral step h1 to the thickness of the central step h2 of the reinforcing member 120 structure is in the range of 4 to 6. In some embodiments, n The ratio φ is in the range of 5 to 6.

[0246] 25A-25C, which are schematic diagrams of vibration assemblies including reinforcing members of different shapes, according to some embodiments of the present disclosure. In FIG. 25A, the reinforcing member 120 has a rectangular shape, the annular structure 122 has a single annular rectangular structure, and the elongated structure 124 has a trapezoidal structure. In FIG. 25B, the reinforcing member 120 has a rectangular shape, the annular structure 122 has a double annular rectangular structure, and the elongated structure 124 has a trapezoidal structure. In FIG. 25C, the reinforcing member 120 has a hexagonal shape, the annular structure 122 has a single annular hexagonal structure, and the elongated structure 124 has a trapezoidal structure. In some embodiments, the shape of the reinforcing member 120 of the vibration assembly 100 may match the shape of the elastic element 110. The elastic element 110 may have various shapes, such as a circular shape, a square shape, a polygonal shape, or the like. The shape of the corresponding reinforcing member 120 may be designed in different shapes, including, but not limited to, circular, rectangular (e.g., rectangular, square), triangular, hexagonal, octagonal, other polygonal, elliptical, and other irregular structures.

[0247] The resonant frequency of the vibrating assembly 100 can be changed by flexibly designing differently shaped reinforcing members 120 and differently shaped elastic elements 110 to change the mass and stiffness of the reinforcing members 120 and the mass and stiffness of the vibrating assembly 100, etc.

[0248] In some embodiments, the shape of the reinforcing member 120 and the shape of the elastic element 110 may both include a plurality of different shapes, such as designing different lateral widths and shapes for the elongated structures 124 extending from the central region 112 to the periphery, designing annular structures 122, designing annular structures 122 with different shapes, numbers, and sizes, and designing annular structures 122 as generally annular or as localized annular structures 122. The different annular structures 122 divide the elongated structure 124 into different regions, and in the different regions, the elongated structures 124 in the different regions from the center to the periphery may be continuous, intertwined, and may be equal or unequal in number. In some embodiments, the annular structures 122 may be designed to be circular, rectangular (e.g., rectangular, square), triangular, hexagonal, octagonal, other polygonal, elliptical, and other irregularly shaped structures.

[0249] In some embodiments, by designing the vibrating assembly 100 to include stiffening members 120 with different shapes, the fourth resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and each openwork area S i and the thickness H of the elastic element 110 of each openwork area portion. i The area-thickness ratio μ, which is the ratio of the area-thickness ratio μ to the area S of the suspension region of any two elastic elements 110, is in the range of 150 mm to 700 mm. ki and S ji The ratio γ of the area of ​​the openwork region to the lateral area of ​​the reinforcing member 120 is in the range of 0.25 to 4, and the ratio β of the area of ​​the openwork region to the lateral area of ​​the reinforcing member 120 is in the range of 0.2 to 0.7. In some embodiments, by designing the vibrating assembly 100 including the reinforcing member 120 with different shapes, the fourth resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and the ratio of the area of ​​each openwork region S i and the thickness H of the elastic element 110 of each openwork area portion. i The area-thickness ratio μ, which is the ratio of the area-thickness ratio μ to the area S of the suspension region of any two elastic elements 110, is in the range of 100 mm to 1000 mm. ki and S jiThe ratio γ of the area of ​​the openwork region to the lateral area of ​​the reinforcing member 120 is in the range of 0.1 to 10, and the ratio β of the area of ​​the openwork region to the lateral area of ​​the reinforcing member 120 is in the range of 0.1 to 0.8.

[0250] 26A-26D, which are schematic diagrams of a vibration assembly 100 including a localized mass structure, according to some embodiments herein. FIG. 26A shows a double elastically connected localized mass structure 126, FIG. 26B shows a quadruple elastically connected localized mass structure 126, FIG. 26C shows a quadruple S-shaped elastically connected localized mass structure 126, and FIG. 26D shows an irregular quadruple S-shaped elastically connected localized mass structure 126. In some embodiments, the localized mass structures 126 are designed in the suspended region of the central region 112 to provide an equivalent mass Mm of each openwork region. i , equivalent stiffness Ka i , Ka i ', equivalent damping Ra i , Ra i By flexibly adjusting ', the fourth resonance peak of the vibrating assembly 100 can be effectively adjusted. And by designing the local mass structure 126, the mass and stiffness of the stiffening member 120 can be further adjusted in a wide range to adjust the first resonance peak and the third resonance peak of the vibrating assembly 100.

[0251] In some embodiments, a local mass structure 126 may be circumferentially connected to an adjacent elongate structure 124 by a dual elastic structure (as shown in FIG. 26A ), or may be circumferentially connected to an adjacent annular structure 122 by a dual elastic structure. In other embodiments, each local mass structure 126 may not be connected to either an elongate structure 124 or an annular structure 122, but may be connected only to the elastic element 110. In some embodiments, a portion of a local mass structure 126 may be connected to the elastic element 110, and another portion may be connected to the annular structure 122 and / or the elongate structure 124.

[0252] In some embodiments, the local mass structure 126 may be connected to both the adjacent elongated structure 124 and the annular structure 122 by a quadruple elastic structure (shown in Figure 26B).

[0253] In some embodiments, the planar shape of the resilient structure may be regular (as shown in Figures 26A and 26B) or irregular (as shown in Figure 26C).

[0254] In some embodiments, the local mass structures 126 may have a regular shape (as shown in Figures 26A-26C) or an arbitrary irregular shape (as shown in Figure 26D).

[0255] In some embodiments, by designing the dimensions, location, number, and shape of the local mass structures 126 and the dimensions, location, number, and shape of the elastically connected structures, the fourth resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and each openwork area S i and the thickness H of the elastic element 110 of each openwork area portion. i The area-thickness ratio μ, which is the ratio of the area-thickness ratio μ to the area S of the suspension region of any two elastic elements 110, is in the range of 150 mm to 700 mm. ki and S ji The ratio γ of the area of ​​the openwork region to the lateral area of ​​the stiffening member 120 is in the range of 0.25 to 4, and the ratio β of the area of ​​the openwork region to the lateral area of ​​the stiffening member 120 is in the range of 0.2 to 0.7. In some embodiments, by designing the dimensions, location, number, and shape of the local mass structure 126 and the dimensions, location, number, and shape of the elastically connected structures, the fourth resonance peak of the vibrating assembly 100 is in the range of 10 kHz to 18 kHz, and each openwork region area S i and the thickness H of the elastic element 110 of each openwork area portion. i The area-thickness ratio μ, which is the ratio of the area-thickness ratio μ to the area S of the suspension region of any two elastic elements 110, is in the range of 100 mm to 1000 mm. ki and S ji The ratio γ of the area of ​​the openwork region to the lateral area of ​​the reinforcing member 120 is in the range of 0.1 to 10, and the ratio β of the area of ​​the openwork region to the lateral area of ​​the reinforcing member 120 is in the range of 0.1 to 0.8.

[0256] FIG. 26E is a cross-sectional schematic diagram of a reinforcing member according to some embodiments of the present disclosure. As shown in FIG. 26E , the reinforcing member 120 may include a central connection portion 123, a reinforcing portion 125, and an openwork portion 127. In some embodiments, the openwork portion 127 is obtained by hollowing out a portion of the material of the reinforcing member 120, and the unhollowed portion of the reinforcing member 120 constitutes the reinforcing portion 125. In some embodiments, the openwork portion 127 may be configured to be circular. In some embodiments, the openwork portion 127 may be configured to have other shapes. In some embodiments, the central connection portion 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 along the vibration direction of the elastic element 110 may be greater than the thickness of the reinforcing portion 125 along the vibration direction of the elastic element 110.

[0257] The embodiments of the present specification further provide a speaker, which includes a vibration assembly according to the embodiments of the present specification. By rationally setting the structure and parameters of the vibration assembly (e.g., elastic element, reinforcing member), the speaker has multiple resonance peaks within the audible range of the human ear (e.g., 20 kHz to 20 kHz), thereby improving the frequency range and sensitivity of the speaker and increasing the sound pressure level output from the speaker.

[0258] 27 is an exemplary structural diagram of a speaker according to some embodiments of the present disclosure. In some embodiments, as shown in FIG. 27, speaker 2700 may include a housing 2730, a drive assembly 2720, and the vibration assembly 2710. Drive assembly 2720 can vibrate based on an electric signal, and vibration assembly 2710 can vibrate in response to vibration from drive assembly 2720. Housing 2730 forms a cavity, and drive assembly 2720 and vibration assembly 2710 are installed in the cavity. The structure of vibration assembly 2710 may be the same as the structure of any of the vibration assemblies in the embodiments of the present disclosure.

[0259] In some embodiments, the vibrating assembly 2710 mainly includes an elastic element 2711 and a reinforcing member 2712. The elastic element 2711 mainly includes a central region 2711A, an edge region 2711B located on the outer periphery of the central region 2711A, and a fixed region 2711C located on the outer periphery of the edge region 2711B. The elastic element 2711 is configured to vibrate along a direction perpendicular to the central region 2711A. The reinforcing member 2712 is connected to the central region 2711A. The reinforcing member 2712 includes a reinforcing portion and a plurality of openwork portions, and the vibration of the reinforcing member 2712 and the elastic element 2711 generates at least two resonance peaks within the audible range of the human ear (20 Hz to 20 kHz).

[0260] The drive assembly 2720 may be an acoustic device with an energy transduction function. In some embodiments, the drive assembly 2720 may be electrically connected to other assemblies of the speaker 2700 (e.g., a signal processor) to receive electrical signals and convert the electrical signals into mechanical vibration signals that may be transmitted to the vibrating assembly 2710 to cause the vibrating assembly 2710 to vibrate, pushing air in the cavity to vibrate and generating sound.

[0261] In some embodiments, the drive assembly 2720 may include a drive unit 2722 and a vibration transmission unit 2724. The drive unit 2722 is electrically connected to other assemblies of the speaker 2700 (e.g., a signal processor) to receive electrical signals and convert the electrical signals into mechanical vibration signals. The vibration transmission unit 2724 is connected between the drive unit 2722 and the vibration assembly 2710 to transmit the vibration signals generated by the drive unit 2722 to the vibration assembly 2710.

[0262] In some embodiments, the drive unit 2722 may include, but is not limited to, a moving coil acoustic driver, a balanced armature acoustic driver, an electrostatic acoustic driver, or a piezoelectric acoustic driver. In some embodiments, the moving coil acoustic driver may include a magnetic member that generates a magnetic field and a coil disposed within the magnetic field, and when energized, the coil can vibrate within the magnetic field to convert electrical energy into mechanical energy. In some embodiments, the balanced armature acoustic driver may include a coil that generates an alternating magnetic field and a ferromagnetic member disposed within the alternating magnetic field, and the ferromagnetic member vibrates under the action of the alternating magnetic field to convert electrical energy into mechanical energy. In some embodiments, the electrostatic acoustic driver can convert electrical energy into mechanical energy by driving a diaphragm to vibrate using an electrostatic field disposed therein. In some embodiments, the piezoelectric acoustic driver can convert electrical energy into mechanical energy using a piezoelectric material disposed therein through the electrostrictive effect.

[0263] In some embodiments, the drive unit 2722 and the vibration transmission unit 2724 may be located on the same side of the vibration direction of the vibrating assembly. In some embodiments, one end of the vibration transmission unit 2724 along the vibration direction of the central region 2711A may be connected to the drive unit 2722, and the other end of the vibration transmission unit 2724 remote from the drive unit 2722 may be connected to the central region 2711A of the vibrating assembly 2710. In other embodiments, the reinforcing member 2712 may include a central connection portion 27121, which covers the center of the central region 2711A. In some embodiments, the other end of the vibration transmission unit 2724 remote from the drive unit 2722 may be directly connected to the central connection portion 27121, i.e., the vibration transmission unit 2724 is connected to the central region 2711A via the central connection portion 27121. In some embodiments, the other end of vibration transmission unit 2724 remote from drive unit 2722 may be indirectly connected to central connection portion 27121, i.e., vibration transmission unit 2724 is directly connected to central region 2711A and connected to central connection portion 27121 via central region 2711A. In some embodiments, the dimensions of vibration transmission unit 2724 may be the same as or approximately the same as (e.g., within 10% of) the dimensions of central connection portion 27121.

[0264] In some embodiments, the center of one end connected to central region 2711A of vibration transmission unit 2724 and the center of central region 2711A are projected along the vibration direction of elastic element 2711 so as to overlap or nearly overlap, and by arranging them in this manner, it is possible to improve the uniformity and stability of the vibration of elastic element 2711 while controlling the third resonance peak output from speaker 2700 within the frequency range (e.g., 5000 Hz to 12000 Hz) described in the embodiments of this specification. In the embodiments of this specification, nearly overlapping means that the distance between the center of one end connected to central region 2711A of vibration transmission unit 2724 and the center of central region 2711A does not exceed 5% of the diameter of central region 2711A. In some other embodiments, when the vibration transmission unit 2724 is connected to the central region 2711A via the central connection portion of the reinforcing member 2712, the dimensions of the vibration transmission unit 2724 are matched to (e.g., the same as) the dimensions of the central connection portion, so that the center of one end of the vibration transmission unit 2724 connected to the central connection portion and the center of the central connection portion 27121 overlap or nearly overlap, and in this case, the center of the central connection portion and the center of the central region 2711A may overlap or nearly overlap when projected along the vibration direction of the elastic element 2711. For specific details of the central connection portion of the reinforcing member 2712, please refer to the related description of the central connection portion 123 of the reinforcing member 120.

[0265] In some embodiments, the vibrating assembly 2710 can receive force and displacement transmitted from the vibration transmission unit 2724 to push and move air to generate sound. In some embodiments, the structure of the vibrating assembly 2710 can be the same as the structure of the vibrating assembly 100.

[0266] In some embodiments, the edge region 2711B may be designed with a unique pattern to disrupt the vibration mode of the edge region 2711B of the elastic element 2711 in the corresponding frequency band, avoiding sound cancellation caused by the localized partial vibration of the elastic element 2711, and making the vibrating assembly 2710 have a flat sound pressure level curve. And the pattern design increases the local stiffness of the elastic element 2711.

[0267] In some embodiments, the modal vibration type of vibrating assembly 2710 can be adjusted by adjusting the structure of stiffening member 2712 .

[0268] In some embodiments, the reinforcing member 2712 includes one or more annular structures and one or more elongated structures, each of which is connected to at least one of the one or more annular structures, and at least one of the one or more elongated structures extends toward the center of the central region 2711A. The area where the one or more annular structures are located and the area where the one or more elongated structures are located together constitute a reinforcing portion. The area not covered by the one or more annular structures and the one or more elongated structures within the projection range of the maximum contour of the reinforcing member 2712 along the vibration direction of the elastic element 2711 constitutes an openwork portion. For specific details of the annular structures and elongated structures of the reinforcing member 2712, please refer to the relevant descriptions of the annular structures and elongated structures elsewhere in this specification.

[0269] In some embodiments, by rationally positioning the reinforcing member 2712 and locating multiple openwork regions in the central region 2711A, it is possible to achieve controllable adjustment of the local stiffness of the central region 2711A of the elastic element 2711, thereby utilizing the divided vibration style of each openwork region in the central region 2711A of the elastic element 2711 of the vibrating assembly 2710 to achieve controllable adjustment of the resonance peak output from the vibrating assembly 2710, so that the vibrating assembly 2710 has a flat sound pressure level curve. In some embodiments, by connecting the annular structure and the elongated structure to each other, the reinforcing member 2712 has an appropriate proportion of reinforcement and openwork portions (i.e., openwork portions), which reduces the mass of the reinforcing member 2712 and improves the sensitivity of the entire vibrating assembly 2710. In some embodiments, by designing the shape, dimensions, and number of the annular and elongated structures, the position and bandwidth of multiple resonant peaks (e.g., the third resonant peak, the fourth resonant peak, etc.) of the vibrating assembly 2710 can be adjusted to control the vibration output of the vibrating assembly 2710.

[0270] In some embodiments, the mass of stiffening member 2712, the mass of elastic element 2711, the equivalent air mass, and the equivalent drive end mass combine to form a total equivalent mass Mt, and the equivalent damping of each component forms a total equivalent damping Rt. Elastic element 2711 provides a stiffness Kt to the system, forming a mass Mt-spring Kt-damping Rt system. When the excitation frequency of drive assembly 2720 is close to a resonant frequency of the system, a resonant peak, i.e., a first resonant peak of vibrating assembly 2710, appears in the frequency response curve of vibrating assembly 2710. In some embodiments, the frequency range of the first resonant peak is 180 Hz to 3000 Hz. In some embodiments, the frequency range of the first resonant peak is 200 Hz to 3000 Hz. In some embodiments, the frequency range of the first resonant peak is 200 Hz to 2500 Hz. In some embodiments, the frequency range of the first resonant peak is 200 Hz to 2000 Hz. In some embodiments, the frequency range of the first resonant peak is between 200 Hz and 1000 Hz.

[0271] In some embodiments, edge region 2711B, connection region 2711D, and suspension region 2711E between the area of ​​center region 2711A where reinforcing member 2712 is installed and edge region 2711B form an equivalent mass Ms, equivalent stiffness Ks, and equivalent damping Rs, forming a mass Ms-spring Ks-damping Rs system. When the excitation frequency of drive assembly 2720 is close to a resonant frequency of the system, a resonant peak, i.e., a second resonant peak of vibrating assembly 2710, appears in the frequency response curve of vibrating assembly 2710. In some embodiments, the frequency range of the second resonant peak of vibrating assembly 2710 may be 3000 Hz to 7000 Hz. In some embodiments, the frequency range of the second resonant peak of vibrating assembly 2710 may be 3000 Hz to 6000 Hz. In some embodiments, the frequency range of the second resonant peak of vibrating assembly 2710 may be 4000 Hz to 6000 Hz. In some embodiments, the parameters of the elastic element 2711 (eg, parameters of the edge region 2711B, the suspension region 2711E) can be set to bring the second resonant peak of the vibrating assembly 2710 into the above frequency range.

[0272] In some embodiments, the stiffening member 2712, the connection region 2711D, the edge region 2711B, the suspension region 2711E between the region where the stiffening member 2712 is installed in the center region 2711A and the edge region 2711B, the equivalent air mass, and the equivalent mass of the drive assembly 2720 combine to form a total equivalent mass Mt1, and the equivalent damping of each portion forms a total equivalent damping Rt1. The stiffening member 2712 and the elastic element 2711 provide stiffness Kt1 to the system, forming a mass Mt1-spring Kt1-damping Rt1 system. When the excitation frequency of the drive assembly 2720 is close to the velocity resonance frequency of the system, a resonance peak, i.e., a third resonance peak of the vibrating assembly 2710, appears in the frequency response curve of the vibrating assembly 2710. In some embodiments, the frequency range of the third resonance peak may be 5000 Hz to 12000 Hz. In some embodiments, the frequency range of the third resonance peak may be 6000 Hz to 12000 Hz. In some embodiments, the frequency range of the third resonant peak may be between 6000 Hz and 10000 Hz.

[0273] In some embodiments, reinforcing member 2712 has one or more openwork regions corresponding to central region 2711A, and each openwork region vibrates at a different resonant frequency, resulting in one or more high-frequency resonant peaks in the frequency response curve of vibrating assembly 2710. In some embodiments, the structure of reinforcing member 2712 is designed so that the resonant frequencies of each openwork region are equal or close (e.g., the difference is less than 4000 Hz), thereby resulting in a high-frequency resonant peak with a high output sound pressure level, i.e., a fourth resonant peak of vibrating assembly 2710, in the frequency response curve of vibrating assembly 2710. In some embodiments, the frequency range of the fourth resonant peak may be 8000 Hz to 20000 Hz. In some embodiments, the frequency range of the fourth resonant peak may be 10000 Hz to 18000 Hz. In some embodiments, the frequency range of the fourth resonant peak may be 12000 Hz to 18000 Hz. In some embodiments, the frequency range of the fourth resonant peak may be 15,000 Hz to 18,000 Hz. In other embodiments, the frequency range of the fourth resonant peak may be greater than 20,000 Hz. In other embodiments, the resonant frequencies of each openwork region are different, and the vibration phases of different openwork regions are different in different frequency bands in the high frequency range (e.g., 8,000 Hz to 20,000 Hz), achieving an audio overlap cancellation effect, and the vibrating assembly 2710 does not output the fourth resonant peak.

[0274] In some embodiments, the structure of vibrating assembly 2710 is designed so that speaker 2700 exhibits two, three, or four resonant peaks within the audible range of the human ear (eg, 20 Hz to 20 kHz).

[0275] In some embodiments, the frequency difference between the second and third resonance peaks of the vibrating assembly 2710 can be designed by designing the structure and dimensions of the vibrating assembly 2710, including the overall dimensions of the reinforcing member 2712, the number and dimensions of the elongated structures, the arrangement positions of the elongated structures, the area of ​​the hanging region 2711E, the structure of the edge region 2711B (e.g., edge width, arch height, arch shape, pattern, etc.), and the area of ​​the connecting region 2711D. In some embodiments, when the frequency difference between the second and third resonance peaks of the vibrating assembly 2710 is less than 2000 Hz, the second and third resonance peaks tend to be combined, i.e., the second and third resonance peaks appear as a single resonance peak, thereby providing high sensitivity in the mid-to-high frequency band (3000 Hz to 10000 Hz) and significantly improving the bandwidth of the combined resonance peaks. In some embodiments, the frequency range of the fourth resonant peak may be greater than 20,000 Hz, i.e., the fourth resonant peak does not appear within the audible range of the human ear. In some embodiments, if the frequency difference between the second resonant peak and the third resonant peak is less than 2,000 Hz and the fourth resonant peak does not appear within the audible range of the human ear, when the vibrating assembly 2710 vibrates, only two resonant peaks exist within the audible range of the human ear, and the 3 dB bandwidth of at least one resonant peak is 1,000 Hz or greater. The 3 dB bandwidth refers to the width of a frequency band (e.g., the abscissa in FIG. 7D ) corresponding to a 3 dB drop in sound pressure level amplitude (e.g., the ordinate in FIG. 7D ) corresponding to the resonant peak. In some embodiments, when the vibrating assembly 2710 vibrates, the 3 dB bandwidth of at least one resonant peak within the audible range of the human ear is 1,500 Hz or greater. In some embodiments, when vibrating assembly 2710 vibrates, the 3 dB bandwidth of at least one resonant peak within the audible range of the human ear is 1000 Hz or greater. In some embodiments, when vibrating assembly 2710 vibrates, the 3 dB bandwidth of at least one resonant peak within the audible range of the human ear is 500 Hz or greater.

[0276] In some embodiments, due to the design of the reinforcing member 2712 and the elastic element 2711, the required higher order modes of the vibration assembly 2710 appear within the audible range (20 Hz to 20,000 Hz), and the above-mentioned first, second, third and fourth resonance peaks appear on the frequency response curve of the vibration assembly 2710, i.e., there are four resonance peaks appearing on the frequency response curve of the vibration assembly 2710 within the frequency range of 20 Hz to 20,000 Hz.

[0277] In some embodiments, by designing the structures of the reinforcing member 2712 and the elastic element 2711, the vibrating assembly 2710 can have only three resonance peaks within the audible range of the human ear (20 Hz to 20,000 Hz). For example, if the frequency difference between the second and third resonance peaks of the vibrating assembly 2710 is less than 2,000 Hz, the second and third resonance peaks will appear as one resonance peak on the frequency response sound pressure level curve of the vibrating assembly 2710, and together with the first and fourth resonance peaks, form three resonance peaks of the vibrating assembly 2710 within the audible range of the human ear (20 Hz to 20,000 Hz). In addition, for example, if the reinforcing member 2712 has one or more hanging areas corresponding to the central area 2711A, and the resonant frequency of each openwork area is higher than the audible range, or the resonant frequency of each openwork area is different, and different hanging areas have different vibration phases in different frequency bands in the high frequency range (10,000 Hz to 18,000 Hz), thereby achieving the effect of sound overlap cancellation, the effect of high frequency roll-off can be obtained, and no fourth resonant peak appears in the sound pressure level frequency response curve of the vibration assembly 2710. At this time, the first resonant peak, the second resonant peak, and the third resonant peak form three resonant peaks of the vibration assembly 2710 within the audible range of the human ear (20 Hz to 20,000 Hz).

[0278] In some embodiments, by designing the structure of the reinforcing member 2712 or the elastic element 2711, it is possible to adjust not only the frequencies of the multiple resonant peaks, but also the 3 dB bandwidth of the multiple resonant peaks (e.g., the third resonant peak) and the Q value of the speaker.

[0279] In some embodiments, the 3 dB bandwidth of the third resonance peak output from speaker 2700 and the Q value of speaker 2700 can be adjusted by designing the included angle θ between two sides of the shape of the projection of the elongated structure along the vibration direction. In some embodiments, if speaker 2700 needs to exhibit frequency response characteristics with a low Q value and a wide bandwidth, the included angle θ of the elongated structure may be large. In some embodiments, by setting the included angle θ of the elongated structure in the range of −90° to 150°, speaker 2700 has a low Q value and the 3 dB bandwidth of the third resonance peak output from speaker 2700 is 1000 Hz or more. In some embodiments, by setting the included angle θ of the elongated structure in the range of −0° to 60°, speaker 2700 has a low Q value and the 3 dB bandwidth of the third resonance peak output from speaker 2700 is 1000 Hz or more.

[0280] In some embodiments, if speaker 2700 is required to exhibit frequency response characteristics with a high Q factor and a narrow bandwidth, the included angle θ of the elongated structure may be designed to be small. In some embodiments, by setting the included angle θ of the elongated structure to be in the range of -150° to 90°, speaker 2700 will have a high Q factor and the 3 dB bandwidth of the third resonance peak output from speaker 2700 will be 1000 Hz or less. In some embodiments, by setting the included angle θ of the elongated structure to be in the range of -60° to 0°, speaker 2700 will have a high Q factor and the 3 dB bandwidth of the third resonance peak output from speaker 2700 will be 1000 Hz or less.

[0281] In some embodiments, the 3 dB bandwidth of the third resonance peak output from speaker 2700 and the Q value of speaker 2700 can be adjusted by designing the area ratio τ between the inside and outside of a semi-outline of the shape of the projection of reinforcing member 2712 along the vibration direction of elastic element 2711. If speaker 2700 needs to exhibit frequency response characteristics with a low Q value and a wide bandwidth, the mass concentrated in the central region of reinforcing member 2712 can be designed to be large. In some embodiments, by setting the area ratio τ between the inside and outside of the semi-outline of the shape of the projection of reinforcing member 2712 along the vibration direction of elastic element 2711 in the range of 0.3 to 2, speaker 2700 has a low Q value and the 3 dB bandwidth of the third resonance peak output from speaker 2700 is 1000 Hz or more. In some embodiments, by setting the area ratio τ of the inside to the outside of a semi-outline of the shape of the projection of the reinforcing member 2712 along the vibration direction of the elastic element 2711 in the range of 0.5 to 1.2, the speaker 2700 has a low Q value, and the 3 dB bandwidth of the third resonance peak output from the speaker 2700 is 1000 Hz or more. If the speaker 2700 needs to exhibit frequency response characteristics with a high Q value and a narrow bandwidth, the mass concentrated in the edge region of the reinforcing member 2712 can be designed to be large. In some embodiments, by setting the area ratio τ of the inside to the outside of a semi-outline of the shape of the projection of the reinforcing member 2712 along the vibration direction of the elastic element 2711 in the range of 1 to 3, the speaker 2700 has a high Q value, and the 3 dB bandwidth of the third resonance peak output from the speaker 2700 is 1000 Hz or less. In some embodiments, by setting the area ratio τ of the inside to the outside of the half contour of the projection shape of elastic element 2711 of reinforcing member 2712 along the vibration direction to be in the range of 1.2 to 2.8, speaker 2700 has a high Q value, and the 3 dB bandwidth of the third resonance peak output from speaker 2700 is 1000 Hz or less.

[0282] In some embodiments, at least one of the one or more elongated structures has a plurality of steps whose thicknesses vary along the vibration direction of the elastic element 2711, the steps including a first step located at the outermost position in the radial direction of the elongated structure and a second step located at the innermost position in the radial direction of the elongated structure. In some embodiments, the 3 dB bandwidth of the third resonance peak output from the speaker 2700 and the Q value of the speaker 2700 can be adjusted by adjusting the thickness ratio φ between the first step and the second step. If the speaker 2700 needs to exhibit frequency response characteristics with a low Q value and a wide bandwidth, the mass concentrated at a position close to the center of the reinforcing member 2712 can be designed to be large. In some embodiments, by setting the thickness ratio φ between the first step and the second step in the range of 0.1 to 1, the speaker 2700 has a low Q value and the 3 dB bandwidth of the third resonance peak output from the speaker 2700 is 1000 Hz or more. In some embodiments, by setting the thickness ratio φ of the first step to the second step in the range of 0.2 to 0.8, speaker 2700 has a low Q value, and the 3 dB bandwidth of the third resonance peak output from speaker 2700 is 1000 Hz or more. If speaker 2700 is required to exhibit frequency response characteristics with a high Q value and a narrow bandwidth, the mass concentrated at the edge region of reinforcing member 2712 can be designed to be large. In some embodiments, by setting the thickness ratio φ of the first step to the second step in the range of 1 to 10, speaker 2700 has a high Q value, and the 3 dB bandwidth of the third resonance peak output from speaker 2700 is 1000 Hz or less. In some embodiments, by setting the thickness ratio φ of the first step to the second step in the range of 1.2 to 6, speaker 2700 has a high Q value, and the 3 dB bandwidth of the third resonance peak output from speaker 2700 is 1000 Hz or less.

[0283] In some embodiments, the housing 2730 may be a hollow, regular or irregular three-dimensional structure (i.e., having a cavity therein). For example, the 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 shapes. In some embodiments, the 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 material (e.g., metal matrix composite or non-metal matrix composite), etc. In some embodiments, the drive assembly 2720 may be located within an acoustic cavity formed by the housing 2730, or may be suspended at least partially within the acoustic cavity of the housing 2730.

[0284] In some embodiments, the periphery of the elastic element 2711 may be connected to an inner wall of the housing 2730 to divide the cavity formed by the housing 2730 into multiple cavities. Specifically, the elastic element 2711 divides the cavity of the housing 2730 along its vibration direction into a front cavity 2731 and a rear cavity 2733 located on either side of the elastic element 2711. In some embodiments, the front cavity 2731 is located on the side of the elastic element 2711 away from the drive unit 2722.

[0285] In some embodiments, the rear cavity 2733 is located on the side of the elastic element 2711 adjacent to the drive unit 2722 , ie, the drive assembly 2720 may be located within the rear cavity 2733 .

[0286] In some embodiments, one or more holes may be formed in the side walls of the housing 2730 corresponding to the front cavity 2731 and the rear cavity 2733. Illustratively, a first hole 2732 is provided in the housing 2730 on the side of the front cavity 2731 away from the elastic element 2711, and the front cavity 2731 communicates with the outside of the speaker 2700 via the first hole 2732, and a second hole 2734 is provided in the housing 2730 on the side of the rear cavity 2733 away from the elastic element 2711, and the rear cavity 2733 communicates with the outside of the speaker 2700 via the second hole 2734. The sound generated by the vibration assembly 2710 may be radiated into the front cavity 2731 and / or the rear cavity 2733 and transmitted to the outside of the speaker 2700 through the first hole 2732 and / or the second hole 2734 on the housing 2730.

[0287] In some embodiments, one or more of the holes (e.g., second hole 2734) may be provided with a damping mesh or dust-proof cloth (e.g., damping mesh 27341). In some embodiments, the damping mesh can adjust (e.g., reduce) the amplitude of sound waves leaking through the holes, thereby improving the performance of speaker 2700.

[0288] In some embodiments, speaker 2700 may further include a support element 2740, which is connected to housing 2730 and fixed region 2711C, respectively. In some embodiments, as shown in Fig. 27, fixed region 2711C of elastic element 2711 of vibration assembly 2710 is located on the outer periphery of connection region 2711D and is connected to surrounding the peripheral side of connection region 2711D. Support element 2740 may be located on either surface of central region 2711A of fixed region 2711C along the vibration direction and connected to connection region 2711D via fixed region 2711C.

[0289] In some embodiments, the support element 2740 may be fitted into the inner wall of the housing 2730 and connected to the housing 2730 to support the elastic element 2711. When the support element 2740 is fitted into the inner wall of the housing 2730, a hole that mates with the support element 2740 may be provided in the inner wall of the housing 2730, so that the support element 2740 is positioned within the hole to achieve the fitting of the support element 2740.

[0290] 27 , the support element 2740 may be installed in a cavity formed by the housing 2730, and the support element 2740 may be connected to the housing 2730 along the lower surface (the surface close to the drive unit 2722) or the peripheral side surface in the vibration direction of the vibration assembly 2710 to support the elastic element 2711. In some embodiments, when the support element 2740 is installed in the cavity formed by the housing 2730, the inner wall of the housing 2730 may be installed to have a protruding structure that matches the support element 2740, so that the support element 2740 is installed on the surface along the vibration direction of the protruding structure to realize the connection between the support element 2740 and the housing 2730. In such an installation, installing the support element 2740 in the cavity formed by the housing 2730 can prevent the support element 2740 from getting caught and being damaged during use of the speaker 2700, and further prevent damage to the speaker 2700 (particularly the vibration assembly 2710).

[0291] In some embodiments, the support element 2740 may be a rigid structure that is not easily deformed, providing support only to the elastic element 2711 during vibration of the vibrating assembly 2710. In some embodiments, to further reduce the system stiffness during vibration of the vibrating assembly 2710 and increase the compliance of the loudspeaker 2700, the support element 2740 may be mounted on a flexible structure that is more easily deformed, providing additional displacement during vibration of the vibrating assembly 2710.

[0292] In some embodiments, the support element 2740 can deform in response to a vibration signal from the elastic element 2711, providing a displacement to the elastic element 2711 along its vibration direction, thereby increasing the total displacement of the elastic element 2711 in that vibration direction and further improving the low frequency sensitivity of the vibrating assembly 2710. In some embodiments, the material of the support element 2740 can include one or more of a rigid material, a semiconductor material, an organic polymer material, a rubber-based material, etc. In some embodiments, the rigid material can include, but is not limited to, a metal material, an alloy material, etc. The semiconductor material can include, but is not limited to, one or more of silicone, silicon dioxide, silicon nitride, silicon carbide, etc. The organic polymer material can include, but is not limited to, one or more of polyimide (PI), parylene, polydimethylsiloxane (PDMS), hydrogel, etc. The rubber-based material may include, but is not limited to, one or more of gel-based, silicone gel-based, acrylic-based, polyurethane-based, rubber-based, epoxy-based, hot melt-based, photocurable, etc. In some embodiments, the material of the support element 2740 may be a silicone adhesive, a silicone sealing adhesive, etc., to strengthen 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. In some embodiments, the cross-sectional shape of the support element 2740 in a cross section parallel to the vibration direction of the reinforcement region may be a regular geometric shape such as a rectangle, a circle, an ellipse, a pentagon, etc., and / or an irregular geometric shape. In addition, installing the support element 2740 with a flexible structure can not only change the vibration characteristics of the vibration assembly 2710, but also prevent the elastic element 2711 from directly contacting the housing 2730, thereby reducing stress concentration at the end of the elastic element 2711 directly connected to the housing 2730 (the housing is usually a rigid body), and further protecting the elastic element 2711.

[0293] Having described the basic concepts above, it will be apparent to those skilled in the art that the detailed disclosure above is provided by way of example only and is not intended to limit the scope of the present application. Although not expressly described herein, those skilled in the art may make various changes, improvements, and modifications to the present application. These changes, improvements, and modifications are intended to be suggested by the present application and are therefore within the spirit and scope of the exemplary embodiments of the present application.

[0294] Furthermore, certain terms are used herein to describe embodiments of the present application. For example, "one embodiment," "one embodiment," and / or "some embodiments" refer to particular features, structures, or characteristics associated with at least one embodiment of the present application. Therefore, it is emphasized and understood that references to "one embodiment" or "one embodiment" or "one alternative embodiment" in various parts of this specification do not necessarily all refer to the same embodiment. Furthermore, particular features, structures, or characteristics of one or more embodiments of the present application may be combined as appropriate.

[0295] Additionally, as will be appreciated by those skilled in the art, aspects of the present application may be illustrated and described in several patentable classes or contexts, including any new and useful process, machine, manufacture, or combination of matter, or any new and useful improvement thereto. Accordingly, aspects of the present application may be implemented entirely in hardware, entirely in software (including firmware, resident software, microcode, etc.), or a combination of hardware and software. Such hardware or software may be referred to as a "data block," "module," "engine," "unit," "assembly," or "system." Additionally, aspects of the present application may take the form of a computer program product embodied in one or more computer-readable medium(s) containing computer-readable program code.

[0296] The computer storage medium may include a propagated data signal, propagated in baseband or as part of a carrier wave, for carrying computer program code. The propagated signal may take various forms, such as an electromagnetic signal, an optical signal, or a suitable combination. The computer storage medium may be any computer-readable medium other than a computer-readable storage medium, which can be coupled to an instruction execution system, device, or apparatus to achieve communication, propagation, or transmission of a program used therein. The program code on the computer storage medium may be propagated via any suitable medium, including wireless, cable, fiber optic cable, RF, or similar media, or any combination of the above media.

[0297] Computer program code necessary for the operation of portions of this application may be coded in one or more programming languages, including object-oriented programming languages ​​such as Java, Scala, Smalltalk, Eiffel, JADE, Emerald, C++, C#, VB.NET, Python, etc.; traditional procedural programming languages ​​such as C, Visual Basic, Fortran 2003, Perl, COBOL 2002, PHP, ABAP, etc.; dynamic programming languages ​​such as Python, Ruby, and Groovy, or other programming languages. The program code may run entirely on the user's computer, on the user's computer as a separate software package, partially on the user's computer and partially on a remote computer, or entirely on a remote computer or server. In the latter case, the remote computer may be connected to the user's computer by any form of network, such as a local area network (LAN) or wide area network (WAN), connected to an external computer (e.g., via the Internet), in a cloud computing environment, or used as a service, such as Software as a Service (SaaS).

[0298] Furthermore, unless expressly stated in the claims, the enumerated order, use of alphanumeric characters, or use of other designations of processing elements or sequences described herein does not limit the order of the procedures and methods herein. While the above disclosure has set forth through various examples what are presently believed to be various useful embodiments of the invention, it should be understood that such details are for illustrative purposes only, and that the appended claims are not limited to the disclosed embodiments, but rather are intended to cover all modifications and equivalent combinations within the spirit and scope of the embodiments herein. For example, the system assembly described above may be implemented by a hardware device, or may be implemented as a software-only solution, e.g., by installing the described system on an existing server or mobile device.

[0299] Similarly, in the foregoing description of embodiments of the present application, various features may be grouped together in a single embodiment, drawing, or description for the purpose of simplifying the application and facilitating an understanding of one or more embodiments of the present invention. However, this method of disclosure should not be interpreted as reflecting an intention that the claimed subject matter requires more features than are recited in each claim. In fact, an embodiment may include fewer than all features of a single embodiment disclosed above.

[0300] In some embodiments, numbers describing the number of components and attributes are used; it should be understood that the numbers describing such embodiments are, in some instances, modified by the modifiers "about," "approximately," or "generally." Unless otherwise specified, "about," "approximately," or "generally" indicates that the number may vary by ±20%. Thus, in some embodiments, all numerical parameters used in the specification and claims are approximations that may vary depending on the specific requirements of a particular embodiment. In some embodiments, numerical parameters should be used with the stated number of significant digits and with ordinary rounding techniques. While in some embodiments, the numerical ranges and parameters used to determine ranges are approximations, in specific embodiments, such numerical values ​​are set as precisely as possible.

[0301] All patents, patent applications, published patent applications, and other materials, such as papers, books, specifications, publications, and documents, referenced in this application are incorporated herein by reference in their entirety, except for prosecution history documents that are inconsistent with or inconsistent with the content of this application and documents that may have a limiting effect on the broadest scope of the claims of this application (now or later related to this application). Furthermore, if the explanations, definitions, and / or term usage in the accompanying materials of this application are inconsistent with or inconsistent with the content set forth in this application, the explanations, definitions, and / or term usage in this application shall control.

[0302] Finally, it should be understood that the embodiments described herein are merely illustrative of the principles of the present embodiments. Other variations may be within the scope of the present application. Thus, by way of example, and not of limitation, alternative configurations of the present embodiments may be considered consistent with the teachings of the present application. Thus, the present embodiments are not limited to the embodiments expressly introduced and described herein. [Explanation of symbols]

[0303] 100, 2710 Vibration Assembly 110, 2711 Elastic elements 112, 2711A central area 1121, 2711E Hanging Area 114, 2711B Edge Area 115, 2711D connection area 116, 2711C fixed area 120, 2712 Reinforcing members 122 Ring Structure 1221 First ring structure 1222 Second ring structure 1223 Third Ring Structure 123 Center Connection 124 Long structure 1241 first elongated structure 1242 Second elongated structure 1243 Third elongated structure 125 Reinforcement 126 Local Mass Structure 127 Openwork section 210 First Resonance Peak 220 Second Resonance Peak 230 Third Resonant Peak 240 Fourth Resonance Peak 710 Frequency Response Curve 720 Frequency Response Curve 810, 820, 830, 910, 920, 940, 950, 1010, 1020, 1030, 1040, 1050, 1060, 1210, 1220, 1230 Frequency response curves 2700 speakers 2720 ​​Drive Assembly 2722 Drive Unit 2724 Vibration Transmission Unit 2730 Housing 2731 Front Cavity 2732 First hole 2733 Rear Cavity 2734 Second hole 27341 Attenuation Mesh 2740 Supporting Elements

Claims

1. a drive assembly that vibrates based on an electrical signal; a vibration assembly that vibrates in response to vibration from the drive assembly, the vibration assembly includes a resilient element and a stiffening member; the elastic element includes a central region, an edge region disposed on an outer periphery of the central region, and a fixing region disposed on an outer periphery of the edge region, and is configured to vibrate along a direction perpendicular to the central region; the reinforcing member is connected to the central region and includes a reinforcing portion and a plurality of openwork portions, and vibrations of the reinforcing member and the elastic element produce at least two resonance peaks within the audible range of the human ear; the reinforcing member includes one or more annular structures and one or more elongated structures, each of the one or more elongated structures being connected to at least one of the one or more annular structures to form the reinforcing portion and the openwork portion, and at least one of the one or more elongated structures extending toward a center of the central region; A speaker, wherein one or more openwork areas are configured between the one or more annular structures and the one or more elongated structures, and the ratio of the area of ​​at least one of the one or more openwork areas to the thickness of the elastic element is in the range of 100 mm to 1000 mm, so that the at least two resonance peaks include a resonance peak in the frequency range of 10,000 Hz to 18,000 Hz.

2. The loudspeaker of claim 1 , wherein a maximum area of ​​the projection of the one or more annular structures along the vibration direction of the elastic element is smaller than an area of ​​the central region.

3. 2. The speaker of claim 1, wherein the one or more annular structures include a first annular structure and a second annular structure, the radial dimension of the first annular structure being smaller than the radial dimension of the second annular structure, and the first annular structure being positioned inside the second annular structure.

4. 4. The speaker of claim 3, wherein the one or more elongated structures include at least one first elongated structure and at least one second elongated structure, the at least one first elongated structure being located inside the first annular structure and connected to the first annular structure, and the at least one second elongated structure being located between the first annular structure and the second annular structure and connected to the first annular structure and the second annular structure, respectively.

5. The loudspeaker of claim 4 , wherein the at least one first elongated structure and the at least one second elongated structure are connected to the first annular structure at different locations.

6. 2. The loudspeaker of claim 1, wherein at least one of the one or more elongated structures has a plurality of different thicknesses along a vibration direction of the elastic element, and the one or more elongated structures has a stepped structure.

7. 7. A speaker according to claim 1, wherein when the vibration assembly vibrates, only two resonance peaks exist within the audible range of the human ear, and the 3 dB bandwidth of at least one resonance peak is 1000 Hz or greater.

8. 7. The speaker of claim 1, wherein the resonant peaks include a first resonant peak in a frequency range of 200 Hz to 3000 Hz, a second resonant peak in a frequency range of 3000 Hz to 7000 Hz, and a third resonant peak in a frequency range of 5000 Hz to 12000 Hz.

9. 9. The speaker of claim 8, wherein when the vibrating assembly vibrates, there are only three resonance peaks within the audible range of the human ear.

10. 2. The speaker of claim 1, wherein when the vibrating assembly vibrates, there are only four resonant peaks within the audible range of the human ear.

11. The loudspeaker of claim 8 , wherein the difference between the third resonance peak and the second resonance peak is less than 3000 Hz.

12. the drive assembly includes a drive unit and a vibration transmission unit, one end of the vibration transmission unit along the vibration direction of the central region is connected to the drive unit, and the other end is connected to the central region; the reinforcing member includes a central connection portion, and the vibration transmission unit is directly connected to the central connection portion and connected to the central region via the central connection portion, or the vibration transmission unit is directly connected to the central region and indirectly connected to the central connection portion via the central region; The speaker according to claim 1 , wherein a projection of the center of the one end of the vibration transmission unit connected to the central region and a projection of the center region along the vibration direction of the elastic element overlap.

Images