WO2023245807A1 - 一种扬声器 - Google Patents

一种扬声器 Download PDF

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Publication number
WO2023245807A1
WO2023245807A1 PCT/CN2022/108479 CN2022108479W WO2023245807A1 WO 2023245807 A1 WO2023245807 A1 WO 2023245807A1 CN 2022108479 W CN2022108479 W CN 2022108479W WO 2023245807 A1 WO2023245807 A1 WO 2023245807A1
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WO
WIPO (PCT)
Prior art keywords
area
vibration
vibration component
resonance peak
frequency
Prior art date
Application number
PCT/CN2022/108479
Other languages
English (en)
French (fr)
Inventor
周文兵
张磊
王庆依
齐心
廖风云
Original Assignee
深圳市韶音科技有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 深圳市韶音科技有限公司 filed Critical 深圳市韶音科技有限公司
Priority to EP22947552.0A priority Critical patent/EP4418687A1/en
Priority to CN202280070391.7A priority patent/CN118140495A/zh
Priority to TW112101228A priority patent/TWI835518B/zh
Publication of WO2023245807A1 publication Critical patent/WO2023245807A1/zh
Priority to US18/649,005 priority patent/US20240292156A1/en

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    • H—ELECTRICITY
    • H04—ELECTRIC COMMUNICATION TECHNIQUE
    • H04R—LOUDSPEAKERS, MICROPHONES, GRAMOPHONE PICK-UPS OR LIKE ACOUSTIC ELECTROMECHANICAL TRANSDUCERS; DEAF-AID SETS; PUBLIC ADDRESS SYSTEMS
    • H04R1/00—Details of transducers, loudspeakers or microphones
    • H04R1/02—Casings; Cabinets ; Supports therefor; Mountings therein
    • H—ELECTRICITY
    • H04—ELECTRIC COMMUNICATION TECHNIQUE
    • H04R—LOUDSPEAKERS, MICROPHONES, GRAMOPHONE PICK-UPS OR LIKE ACOUSTIC ELECTROMECHANICAL TRANSDUCERS; DEAF-AID SETS; PUBLIC ADDRESS SYSTEMS
    • H04R17/00—Piezoelectric transducers; Electrostrictive transducers
    • H—ELECTRICITY
    • H04—ELECTRIC COMMUNICATION TECHNIQUE
    • H04R—LOUDSPEAKERS, MICROPHONES, GRAMOPHONE PICK-UPS OR LIKE ACOUSTIC ELECTROMECHANICAL TRANSDUCERS; DEAF-AID SETS; PUBLIC ADDRESS SYSTEMS
    • H04R1/00—Details of transducers, loudspeakers or microphones
    • H04R1/02—Casings; Cabinets ; Supports therefor; Mountings therein
    • H04R1/021—Casings; Cabinets ; Supports therefor; Mountings therein incorporating only one transducer
    • H—ELECTRICITY
    • H04—ELECTRIC COMMUNICATION TECHNIQUE
    • H04R—LOUDSPEAKERS, MICROPHONES, GRAMOPHONE PICK-UPS OR LIKE ACOUSTIC ELECTROMECHANICAL TRANSDUCERS; DEAF-AID SETS; PUBLIC ADDRESS SYSTEMS
    • H04R1/00—Details of transducers, loudspeakers or microphones
    • H04R1/20—Arrangements for obtaining desired frequency or directional characteristics
    • H04R1/22—Arrangements for obtaining desired frequency or directional characteristics for obtaining desired frequency characteristic only 
    • H04R1/28—Transducer mountings or enclosures modified by provision of mechanical or acoustic impedances, e.g. resonator, damping means
    • H—ELECTRICITY
    • H04—ELECTRIC COMMUNICATION TECHNIQUE
    • H04R—LOUDSPEAKERS, MICROPHONES, GRAMOPHONE PICK-UPS OR LIKE ACOUSTIC ELECTROMECHANICAL TRANSDUCERS; DEAF-AID SETS; PUBLIC ADDRESS SYSTEMS
    • H04R1/00—Details of transducers, loudspeakers or microphones
    • H04R1/20—Arrangements for obtaining desired frequency or directional characteristics
    • H04R1/22—Arrangements for obtaining desired frequency or directional characteristics for obtaining desired frequency characteristic only 
    • H04R1/28—Transducer mountings or enclosures modified by provision of mechanical or acoustic impedances, e.g. resonator, damping means
    • H04R1/2807—Enclosures comprising vibrating or resonating arrangements
    • H04R1/2811—Enclosures comprising vibrating or resonating arrangements for loudspeaker transducers
    • H—ELECTRICITY
    • H04—ELECTRIC COMMUNICATION TECHNIQUE
    • H04R—LOUDSPEAKERS, MICROPHONES, GRAMOPHONE PICK-UPS OR LIKE ACOUSTIC ELECTROMECHANICAL TRANSDUCERS; DEAF-AID SETS; PUBLIC ADDRESS SYSTEMS
    • H04R9/00—Transducers of moving-coil, moving-strip, or moving-wire type
    • H04R9/06—Loudspeakers
    • H—ELECTRICITY
    • H10—SEMICONDUCTOR DEVICES; ELECTRIC SOLID-STATE DEVICES NOT OTHERWISE PROVIDED FOR
    • H10N—ELECTRIC SOLID-STATE DEVICES NOT OTHERWISE PROVIDED FOR
    • H10N30/00—Piezoelectric or electrostrictive devices
    • H10N30/20—Piezoelectric or electrostrictive devices with electrical input and mechanical output, e.g. functioning as actuators or vibrators
    • H10N30/204—Piezoelectric or electrostrictive devices with electrical input and mechanical output, e.g. functioning as actuators or vibrators using bending displacement, e.g. unimorph, bimorph or multimorph cantilever or membrane benders
    • H10N30/2041—Beam type
    • H10N30/2042—Cantilevers, i.e. having one fixed end
    • H—ELECTRICITY
    • H10—SEMICONDUCTOR DEVICES; ELECTRIC SOLID-STATE DEVICES NOT OTHERWISE PROVIDED FOR
    • H10N—ELECTRIC SOLID-STATE DEVICES NOT OTHERWISE PROVIDED FOR
    • H10N30/00—Piezoelectric or electrostrictive devices
    • H10N30/20—Piezoelectric or electrostrictive devices with electrical input and mechanical output, e.g. functioning as actuators or vibrators
    • H10N30/204—Piezoelectric or electrostrictive devices with electrical input and mechanical output, e.g. functioning as actuators or vibrators using bending displacement, e.g. unimorph, bimorph or multimorph cantilever or membrane benders
    • H10N30/2047—Membrane type

Definitions

  • the present application relates to the field of acoustic technology, and in particular to a loudspeaker.
  • the speaker is a commonly used electroacoustic transducer device, which mainly includes a shell, a vibration component and a driving component located in the shell.
  • the vibration component generally divides the inside of the housing into two cavities, such as the front cavity and the back cavity, and the driving component is located in the back cavity. Since the air in the back cavity acts on the vibration component and the driving component, there will be Have an impact on speaker performance. Therefore, it is desired to provide a speaker that can improve the impact of the air in the back cavity on the performance of the speaker.
  • An embodiment of the present specification provides a speaker, including: a driving component that generates vibration based on an electrical signal; a vibration component that receives the vibration of the driving component and vibrates; a housing, the driving component and The vibration component is disposed in a cavity formed by the housing; wherein the cavity includes a front cavity located on one side of the vibration component and one or more rear cavities located on the other side of the vibration component, so The housing includes a back cavity plate, at least one of the one or more back cavities is enclosed by at least the driving assembly, the vibration assembly and the back cavity plate, and the back cavity plate is provided with a through hole.
  • the vibrating surface of the drive assembly forms at least a portion of a side wall of at least one of the one or more rear cavities.
  • the drive assembly includes a piezoelectric acoustic driver.
  • the piezoelectric acoustic driver includes a cantilever beam.
  • the gap between adjacent cantilever beams is no greater than 25 ⁇ m.
  • no less than 90% of the surface area of the vibrating surface of the drive assembly is continuous.
  • the drive component includes a piezoelectric membrane.
  • the number of the back cavities includes at least two, and at least two of the back cavities are connected to each other through the through hole.
  • the housing includes a rear cavity, and the rear cavity, the rear cavity plate, and the driving assembly form a first rear cavity; the driving assembly, the vibration assembly, the The rear cavity portion and the rear cavity plate enclose a second rear cavity.
  • the rear cavity portion includes side panels and a sealing panel.
  • At least two of the back cavities are connected to the outside world through one or more sound guide holes on the back cavity part.
  • the difference between the distance between the center line of at least one of the through holes and the center line of the cavity and the equivalent radius of the drive assembly is equal to the equivalent radius of the cavity.
  • the difference between the effective radius and the equivalent radius of the driving component has a first preset ratio; wherein the first preset ratio is 0.3 to 0.9.
  • the sum of the projected area of the through hole in the plane and the projected area of the cavity in the plane are equal to the sum of the projected area of the through hole in the plane and the driving area.
  • the component has a second preset ratio between the differences between the projected areas in the plane; wherein the second preset ratio is 0.02 to 1.
  • At least one of the through holes has a diameter of 0.2 to 2 mm.
  • At least one of the through holes is provided with a damping net.
  • the acoustic resistance of the damping network is 3 to 10000 MKS rayls.
  • the pore size of the damping mesh is 18-285um.
  • the damping mesh has a porosity of 13% to 44%.
  • Figure 1 is a schematic diagram of a vibration component and its equivalent vibration model according to some embodiments of this specification
  • Figure 2 is a schematic diagram of the deformation of the vibration component at the first resonance peak according to some embodiments of this specification
  • Figure 3 is a schematic diagram of the deformation of the vibration component at the second resonance peak according to some embodiments of this specification.
  • Figure 4 is a schematic diagram of the deformation of the vibration component at the third resonance peak according to some embodiments of this specification.
  • Figure 5 is a schematic diagram of the deformation of the vibration component at the fourth resonance peak according to some embodiments of this specification.
  • Figure 6 is a schematic diagram of the frequency response curve of a vibration component with different third and fourth resonant frequency differences according to some embodiments of this specification;
  • Figure 7A is a schematic diagram of a frequency response curve of a vibration component according to some embodiments of this specification.
  • Figure 7B is a schematic diagram of the frequency response curve of a vibration component according to other embodiments of this specification.
  • Figure 7C is a schematic diagram of the frequency response curve of a vibration component according to other embodiments of this specification.
  • Figure 7D is a schematic diagram of the frequency response curve of a vibration component according to other embodiments of this specification.
  • Figure 8A is a schematic structural diagram of a vibration assembly according to some embodiments of this specification.
  • Figure 8B is a schematic diagram of the frequency response curve of a vibration component according to other embodiments of this specification.
  • Figure 9A is a partial structural schematic diagram of a vibration component shown according to some embodiments of this specification.
  • Figure 9B is a schematic diagram of the frequency response curve of a vibration component according to other embodiments of this specification.
  • Figure 9C is a schematic diagram of the frequency response curve of a vibration component according to other embodiments of this specification.
  • Figure 10A is a schematic diagram of the deformation of the vibration component at the fourth resonance peak according to other embodiments of this specification.
  • Figure 10B is a schematic diagram of the frequency response curve of a vibration component according to other embodiments of this specification.
  • Figure 10C is a schematic diagram of the frequency response curve of a vibration component according to other embodiments of this specification.
  • Figure 11 is a schematic diagram of the deformation of the vibration component at the fourth resonance peak according to other embodiments of this specification.
  • Figure 12A is a schematic diagram of the frequency response curve of the vibration component shown in Figure 11;
  • Figure 12B is a schematic diagram of the frequency response curve of a vibration component according to other embodiments of this specification.
  • Figure 13A is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 13B is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 14A is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 14B is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 14C is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 14D is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 15A is a schematic structural diagram of a vibration assembly according to other embodiments of this specification.
  • Figure 15B is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 16A is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 16B is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 16C is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 16D is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 16E is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 16F is a schematic diagram of the frequency response curve of a vibration component according to other embodiments of this specification.
  • Figure 17A is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 17B is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 17C is a schematic diagram of the frequency response curve of a vibration component according to other embodiments of this specification.
  • Figure 18A is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 18B is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 18C is a schematic structural diagram of a vibration assembly according to other embodiments of this specification.
  • Figure 19 is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 20A is a schematic structural diagram of a vibration assembly according to other embodiments of this specification.
  • Figure 20B is a schematic diagram of the frequency response curve of a vibration component according to other embodiments of this specification.
  • Figure 21A is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 21B is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 21C is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 21D is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 21E is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 22 is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 23 is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 24A is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 24B is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 24C is a schematic diagram of the frequency response curve of a vibration component according to other embodiments of this specification.
  • Figure 25A is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 25B is a schematic structural diagram of a vibration assembly according to other embodiments of this specification.
  • Figure 25C is a schematic structural diagram of a vibration assembly according to other embodiments of this specification.
  • Figure 26A is a schematic structural diagram of a vibration assembly according to other embodiments of this specification.
  • Figure 26B is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 26C is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 26D is a schematic structural diagram of a vibration component according to other embodiments of this specification.
  • Figure 26E is a schematic cross-sectional structural diagram of a reinforcement shown in some embodiments of this specification.
  • Figure 27 is an exemplary structural diagram of a speaker according to some embodiments of this specification.
  • Figure 28 is a schematic structural diagram of a speaker according to some embodiments of this specification.
  • Figure 29 is a schematic diagram of a speaker and its equivalent model according to some embodiments of this specification.
  • Figure 30 is a schematic diagram of a speaker and its equivalent model according to some embodiments of this specification.
  • Figure 31 is a partial three-dimensional structural diagram of a speaker according to some embodiments of this specification.
  • Figure 32 is a cross-sectional view parallel to the axis of the housing cavity of the speaker according to some embodiments of the present specification
  • Figure 33 is a view of the speaker perpendicular to the axis of the housing cavity according to some embodiments of the present specification
  • Figure 34 is a frequency response curve diagram of a speaker according to some embodiments of this specification.
  • Figure 35A is a schematic diagram of the distribution of several through holes on the back cavity plate according to some embodiments of this specification.
  • Figure 35B is a schematic diagram of the distribution of several through holes on the back cavity plate according to some embodiments of this specification.
  • Figure 35C is a schematic diagram of the distribution of several through holes on the back cavity plate according to some embodiments of this specification.
  • Figure 35D is a schematic diagram of the distribution of several through holes on the back cavity plate according to some embodiments of this specification.
  • Figure 35E is a schematic diagram of the distribution of several through holes on the back cavity plate according to some embodiments of this specification.
  • Figure 35F is a schematic diagram of the distribution of several through holes on the back cavity plate according to some embodiments of this specification.
  • Figure 36 is a frequency response curve diagram of a speaker under different first preset ratios ⁇ according to some embodiments of this specification.
  • Figure 37 is a view of the speaker perpendicular to the axis of the housing cavity according to some embodiments of the present specification.
  • Figure 38 is a view of the speaker perpendicular to the axis of the housing cavity according to some embodiments of the present specification.
  • Figure 39 is a frequency response curve diagram of the speaker under different second preset ratios ⁇ when the through hole is a round hole according to some embodiments of this specification;
  • Figure 40 is a frequency response curve diagram of the speaker under different second preset ratios ⁇ when the through hole is a fan-shaped hole according to some embodiments of this specification;
  • Figure 41 is a cross-sectional view of a speaker parallel to the axis of the housing cavity according to some embodiments of this specification;
  • Figure 42 is a cross-sectional view parallel to the axis of the housing cavity of the speaker according to some embodiments of this specification;
  • Figure 43 is a cross-sectional view parallel to the axis of the housing cavity of the speaker according to some embodiments of the present specification.
  • Figure 44 is a view of the speaker perpendicular to the axis of the housing cavity according to some embodiments of the present specification.
  • Figure 45 is a frequency response graph of a speaker according to some embodiments of the present specification.
  • Figure 46 is a cross-sectional view parallel to the axis of the housing cavity of the speaker according to some embodiments of the present specification
  • Figure 47 is a schematic structural diagram of a damping net according to some embodiments of this specification.
  • Figure 48 is a schematic structural diagram of a driving unit according to some embodiments of this specification.
  • Figure 49 is a frequency displacement graph of a driving unit according to some embodiments of this specification.
  • vibration component 100, 2710; elastic element: 110, 2711; 112, central area: 2711A; suspended area: 1121, 2711E; ring area: 114, 2711B; connection area: 115, 2711D; fixed area : 116, 2711C; reinforcement: 120, 2712; ring structure: 122; first ring structure: 1221; second ring structure: 1222; third ring structure: 1223; central connection: 123; strip structure: 124; The first strip structure: 1241; the second strip structure: 1242; the third strip structure: 1243; reinforced part: 125; local mass structure: 126; hollow part: 127; first resonance peak: 210; second resonance Peak: 220; Third resonance peak: 230; Fourth resonance peak: 240; Frequency response curve: 710; Frequency response curve: 720; Frequency response curve: 810, 820, 830, 910, 920, 940, 950, 1010, 1020, 1030, 1040, 1050,
  • the embodiment of this specification provides a vibration component that can be applied to various acoustic output devices.
  • Acoustic output devices include, but are not limited to, speakers, hearing aids, etc.
  • the vibration components provided in the embodiments of this specification mainly include elastic elements and reinforcements.
  • the elastic elements or reinforcements can be connected to the driving part of the speaker, and the edges of the elastic elements are fixed (for example, connected to the housing of the speaker).
  • the driving part of the loudspeaker serves as an electrical energy-mechanical energy conversion unit, which provides driving force for the loudspeaker by converting electrical energy into mechanical energy.
  • the vibration component can receive the force or displacement transmitted by the driving part and generate corresponding vibration output, thus pushing the air to move and generate sound pressure.
  • the elastic element can be regarded as partially connected to the air inertia load through springs and dampers, and achieves the radiation of sound pressure by promoting air movement.
  • the elastic element mainly includes a central area, a folding area arranged on the periphery of the central area, and a fixed area arranged on the periphery of the folding area.
  • a preset pattern can be designed in the ring area of the elastic element to destroy the ring of the elastic element.
  • the mode shape of the region in the corresponding frequency range avoids the occurrence of sound cancellation caused by local segmentation vibration of the elastic element.
  • the local stiffness of the elastic element is increased through the pattern design.
  • the vibration component provided by the embodiment of this specification has a structural design of elastic elements and reinforcements, where the reinforcements include one or more ring structures and one or more strip structures, and the one or more strip structures in the Each one is connected to at least one of one or more ring structures, so that the vibration component can appear the required high-order mode at medium and high frequencies (above 3kHz), and multiple resonance peaks appear on the frequency response curve of the vibration component, thereby making the vibration component It has high sensitivity in a wide frequency band range; at the same time, through the structural design of the reinforcement, the mass of the vibration component is smaller, which improves the overall sensitivity of the vibration component.
  • Figure 1 is a schematic diagram of a vibration component and its equivalent vibration model according to some embodiments of this specification.
  • the vibration component 100 mainly includes an elastic element 110 .
  • the elastic element 110 includes a central area 112 , a ring area 114 disposed on the periphery of the central area 112 , and a fixed area 116 disposed on the periphery of the ring area 114 .
  • the elastic element 110 is configured to vibrate in a direction perpendicular to the central area 112 to transmit the force and displacement received by the vibration assembly 100 to promote air movement.
  • the reinforcement 120 is connected to the central region 112 and includes one or more annular structures 122 and one or more strip structures 124 , each of the one or more strip structures 124 being connected to the one or more annular structures 122 At least one of the strip structures 124 extends toward the center of the central region 112 .
  • the ring structure 122 and the strip structure 124 cooperate with each other so that the reinforcement 120 has an appropriate proportion of reinforcement parts and hollow parts (ie, hollow parts), which reduces the mass of the reinforcement 120 and improves the overall sensitivity of the vibration assembly 100.
  • the positions of multiple resonance peaks of the vibration component 100 can be adjusted, thereby controlling the vibration output of the vibration component 100.
  • the elastic element 110 may be an element capable of elastic deformation under the action of an external load.
  • the elastic element 110 can be a high-temperature resistant material, so that the elastic element 110 maintains performance during the manufacturing process when the vibration assembly 100 is applied to a speaker.
  • Young's modulus and shear modulus have no change or a very small change (such as a change within 5%), where Young's modulus The modulus can be used to characterize the deformation ability of the elastic element 110 when it is stretched or compressed, and the shear modulus can be used to characterize the deformation ability of the elastic element 110 when it is sheared.
  • the elastic element 110 can be a material with good elasticity (that is, easy to undergo elastic deformation), so that the vibration component 100 has good vibration response capability.
  • the material of the elastic element 110 may be one or more of organic polymer materials, glue materials, and the like.
  • the organic polymer material may be polycarbonate (PC), polyamides (PA), acrylonitrile-butadiene-styrene copolymer (Acrylonitrile Butadiene Styrene, ABS), polystyrene Ethylene (Polystyrene, PS), High Impact Polystyrene (HIPS), Polypropylene (PP), Polyethylene Terephthalate (PET), Polyvinyl Chloride, PVC), Polyurethanes (PU), Polyethylene (PE), Phenol Formaldehyde (PF), Urea-Formaldehyde (UF), Melamine-Formaldehyde (MF) , Polyarylate (PAR), Polyetherimide (PEI), Polyimide (PI), Polyethylene Naphthalate two formic acid glycol ester (PEN) , any one or combination of polyetheretherketone (PEEK), carbon fiber, graphene, silica gel, etc.
  • PC polycarbonate
  • PA polyamides
  • PA
  • the organic polymer material can also be various glues, including but not limited to gels, organic silica gels, acrylics, polyurethanes, rubbers, epoxy, hot melt, light curing, etc. , preferably can be silicone bonding glue or silicone sealing glue.
  • the elastic element 110 may have a Shore hardness of 1-50 HA. In some embodiments, the elastic element 110 may have a Shore hardness of 1-15 HA. In some embodiments, the elastic element 110 may have a Shore hardness of 14.9-15.1 HA.
  • the Young's modulus of the elastic element 110 ranges from 5E8Pa to 1E10Pa. In some embodiments, the Young's modulus of the elastic element 110 ranges from 1E9Pa to 5E9Pa. In some embodiments, the Young's modulus of the elastic element 110 ranges from 1E9 Pa to 4E9 Pa. In some embodiments, the Young's modulus of the elastic element 110 ranges from 2E9Pa to 5E9Pa.
  • the density of the elastic element 110 ranges from 1E3kg/m 3 to 4E3kg/m 3 . In some embodiments, the density of the elastic element 110 ranges from 1E3kg/m 3 to 2E3kg/m 3 . In some embodiments, the density of the elastic element 110 ranges from 1E3kg/m 3 to 3E3kg/m 3 . In some embodiments, the density of the elastic element 110 ranges from 1E3kg/m 3 to 1.5E3kg/m 3 . In some embodiments, the elastic element 110 has a density in the range of 1.5E3kg/m 3 -2E3kg/m 3 .
  • the central region 112 of the elastic element 110 when the vibrating assembly is applied to a speaker, the central region 112 of the elastic element 110 may be directly connected to the driving part of the speaker.
  • the reinforcement 120 disposed in the central region 112 of the elastic element 110 may be directly connected to the driving part of the speaker.
  • the central area 112 of the elastic element 110 and the reinforcement 120 can transmit the force and displacement of the driving part to promote air movement and output sound pressure.
  • the central area 112 refers to a certain area of the elastic element 110 extending from the center (for example, the centroid) to the circumferential side, and the reinforcement 120 is connected to the central area 112 .
  • the elastic element 110 is configured to vibrate in a direction perpendicular to the central region 112 .
  • the central area 112 can transmit force and displacement and output vibration response.
  • the ring area 114 is located outside the central area 112 .
  • the ring area 114 can be designed with a pattern of a characteristic shape, thereby destroying the mode shape of the ring area 114 of the elastic element 110 in the corresponding frequency range, and avoiding the occurrence of sound cancellation caused by the partial division vibration of the elastic element 110 , and at the same time, the local stiffness of the elastic element 110 is increased through the pattern design.
  • the ring region 114 may include a ring structure.
  • the stiffness of the ring region 114 corresponding to the ring structure can be made different, and the corresponding frequency ranges of the high-frequency local segmented vibration shapes can also be different.
  • the ring width may be the radial width of the projection of the ring area 114 along the vibration direction of the elastic element 110 .
  • the arch height refers to the height of the ring area 114 protruding from the central area 112 or the fixed area 116 along the vibration direction of the elastic element 110 .
  • the maximum area projected along the vibration direction of the elastic element 110 of one or more annular structures 122 of the reinforcement 120 is smaller than the area of the central region 112 . That is, there is an area that is not supported by the reinforcement 120 between the outermost projection of the reinforcement 120 and the folding ring area 114.
  • This specification refers to a part of the central area 112 between the folding ring area 114 and the reinforcement 120 as a suspended area 1121. .
  • the area of the suspended region 1121 can be adjusted, thereby adjusting the mode shape of the vibration assembly.
  • the fixing area 116 is provided on the periphery of the ring area 114 .
  • the elastic element 110 can be connected and fixed through the fixing area 116 .
  • the elastic element 110 may be connected and fixed to a speaker casing or the like through the fixing area 116 .
  • the fixed area 116 is installed and fixed in the housing of the speaker and can be regarded as not participating in the vibration of the elastic element 110 .
  • the fixing area 116 of the elastic element 110 can be connected to the housing of the speaker through a supporting element.
  • the support element may include a soft material that is easily deformed, so that the support element may also deform when the vibration assembly 100 vibrates, thereby providing a greater displacement for the vibration of the vibration assembly 100 .
  • the support element may also include a rigid material that is not easily deformed.
  • the elastic element 110 may further include a connecting area 115 disposed between the fold area 114 and the fixing area 116 .
  • the connection area 115 can provide additional stiffness and damping for the vibration of the elastic element 110, thereby adjusting the mode shape of the vibration assembly 100.
  • the thickness and elastic coefficient of the elastic element 110 can be set within a reasonable range.
  • the thickness of the elastic element 110 may range from 3um to 100um. In some embodiments, the thickness of the elastic element 110 may range from 3um to 50um. In some embodiments, the thickness of the elastic element 110 may range from 3um to 30um.
  • the reinforcement 120 may be an element used to increase the stiffness of the elastic element 110 .
  • the reinforcement 120 is connected to the central area 112, and the reinforcement 120 and/or the central area 112 are connected to the driving part of the speaker to transmit force and/or displacement, so that the vibration assembly 100 pushes the air to move and output sound. pressure.
  • the reinforcement 120 may include one or more annular structures 122 and one or more strip structures 124, each of the one or more strip structures 124 being connected to at least one of the one or more annular structures 122 to provide for
  • the central region 112 of the elastic element 110 forms a staggered support. Wherein, at least one of the one or more strip structures 124 extends toward the center of the central region 112 .
  • one or more strip structures 124 may pass through the center of the central region 112 to provide support for the center of the central region 112 .
  • the reinforcement 120 may also include a central connection part 123, and one or more strip structures 124 may not pass through the center of the central area 112, but cover the center of the central area 112 with the central connection part 123. Or multiple strip structures 124 are connected to the central connecting portion 123 .
  • the annular structure 122 may be a structure extending around a specific center. In some embodiments, the center around which the annular structure 122 surrounds may be the center of the central region 112 . In other embodiments, the center surrounded by the annular structure 122 may also be other positions on the central area 112 that are off-center. In some embodiments, the annular structure 122 may be a structure with closed outline lines. In some embodiments, the projected shape of the ring structure 122 along the vibration direction of the elastic element 110 may include, but is not limited to, one or a combination of a circular ring, a polygonal ring, a curved ring, or an elliptical ring.
  • the annular structure 122 may also be a structure with unclosed outline lines.
  • the annular structure 122 may be a circular annular shape with a gap, a polygonal annular shape, a curved annular shape or an elliptical annular shape, etc.
  • the number of ring structures 122 may be one.
  • the number of annular structures 122 may also be multiple, and the multiple annular structures may have the same centroid.
  • the number of ring structures 122 may range from 1-10.
  • the number of ring structures 122 may range from 1-5.
  • the number of ring structures 122 may range from 1-3.
  • the quality and stiffness of the reinforcement 120 can be adjusted by designing the number of annular structures 122 .
  • the size of the annular structure 122 located at the outermost periphery of the reinforcement 120 may be regarded as the largest size of the reinforcement.
  • the size (or area) of the suspended area 1121 between the ring area 114 and the stiffener 120 can be adjusted by setting the size of the outermost annular structure 122 , thereby changing the mode shape of the vibration assembly 100 .
  • one or more annular structures 122 may include a first annular structure and a second annular structure, the first annular structure having a radial dimension that is smaller than the radial dimension of the second annular structure.
  • the first annular structure is disposed inside the second annular structure.
  • the centroids of the first and second annular structures may coincide.
  • the centroids of the first annular structure and the second annular structure may not coincide with each other.
  • the first annular structure and the second annular structure may be connected by one or more strip structures 124 .
  • the first annular structure and the second annular structure may be adjacent annular structures.
  • the first annular structure and the second annular structure may also be non-adjacent annular structures, and one or more annular structures may be disposed between the first annular structure and the second annular structure.
  • the strip structure 124 may be a structure with a certain extension pattern. In some embodiments, the strip structure 124 may extend along a straight line. In some embodiments, the strip structure 124 may also extend along a curve. In some embodiments, the curved extension may include, but is not limited to, arc-shaped extension, spiral extension, spline-shaped extension, arc-shaped extension, S-shaped extension, etc. In some embodiments, the strip structure 124 is connected to the annular structure 122 to divide the reinforcement 120 into a plurality of hollow parts. In some embodiments, the area on the central area 112 corresponding to the hollow portion may be called a hollow area. In some embodiments, the number of bar structures 124 may be one.
  • one strip structure 124 can be arranged along any diameter direction of the annular structure 122 (for example, any annular structure).
  • the strip structure 124 may simultaneously connect the center of the central region (ie, the centroid of the annular structure 122) and the annular structure 122.
  • the number of strip structures 124 may also be multiple.
  • multiple strip structures 124 may be disposed along multiple diameter directions of the annular structure 122 .
  • at least a portion of the plurality of strip structures 124 may extend toward a central location of the central region 112 , which may be the centroid of the elastic element 110 .
  • the plurality of strip structures 124 may include another portion extending in other directions.
  • At least a portion of the plurality of strip structures 124 may be connected to a central location of the central region and form a central connection portion 123 at the central location.
  • the central connecting part 123 may also be a separate structure, and at least a part of the plurality of strip structures 124 may be connected to the central connecting part 123 .
  • the shape of the central connecting 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 connecting portion 123 can also be set arbitrarily.
  • adjacent ring structures 122 may be connected by one or more strip structures 124 .
  • the strip structures 124 connected between adjacent annular structures 122 may extend toward the center of the central region 112 , or may not extend toward the center of the central region 112 .
  • the number of strip structures 124 may range from 1 to 100. In some embodiments, the number of strip structures 124 may range from 1-50. In some embodiments, the number of strip structures 124 may range from 1-50. In some embodiments, the number of strip structures 124 may range from 1-30.
  • the projected shape of the strip structure 124 along the vibration direction of the elastic element 110 includes at least one of a rectangle, a trapezoid, a curve, an hourglass shape, and a petal shape.
  • the structural description of the ring structure 122 and the strip structure 124 in the embodiment of this specification is only an optional structure selected to facilitate the reasonable arrangement of the structure of the reinforcement 120, and should not be understood as a description of the reinforcement 120 and its respective structures. Part shape restrictions.
  • the reinforcing member 120 in the embodiment of the present description can form a reinforcing part through the annular structure 122 and the strip structure 124 and a hollow part (ie, a hollow part, corresponding to the central area 112 ) located between the annular structure 122 and the strip structure 124 hollow area).
  • the area where one or more annular structures 122 are located and the area where one or more strip structures 124 are located together form a reinforced part.
  • the area not covered by the one or more annular structures 122 and the one or more strip structures 124 constitutes a hollow portion.
  • the vibration characteristics of the vibration component 100 for example, the number of resonance peaks and the frequency range
  • any shape of reinforcement with a reinforced part and a hollow part can be set using the parameter setting method of the reinforced part and the hollow part provided in this specification to adjust the vibration performance of the vibration component (for example, the resonance peak number and location, shape of the frequency response curve, etc.), these solutions should be included in the scope of this application.
  • connection area 115 between the fixed area 116 and the ring area 114 of the elastic element 110 is suspended.
  • This partial area has an equivalent mass Mm 1 , and the elastic element 110 can provide elasticity and damping. , therefore this area can be equivalent to being fixedly connected to the shell through the spring Km and the damping Rm.
  • connection area 115 is connected to the front-end air load of the elastic element 110 through the spring Ka 1 and the damping Ra 1 to transmit force and displacement to push the air. sports.
  • the ring area 114 of the elastic element 110 has a local equivalent mass Mm 2 , and this area is connected to the connection area 115 of the elastic element 110 through the spring Ka 1 ′ and the damping Ra 1 ′, while the ring area 114
  • the spring Ka 2 and the damping Ra 2 are connected to the air load at the front end of the elastic element 110 to transmit force and displacement to promote air movement.
  • the central region 112 of the elastic element 110 is provided with a reinforcement 120, the reinforcement 120 is connected to the central region 112 of the elastic element 110, and the contact area between the reinforcement 120 and the central region 112 is smaller than the area of the central region 112, so that There is a part of the suspended area 1121 between the area where the central area 112 of the elastic element 110 is supported by the reinforcement 120 and the ring area 114 .
  • This area has a local equivalent mass Mm 3 and is connected to the ring area 114 through the spring Ka 2 ′ and the damping Ra 2 ′.
  • the area where the reinforcement 120 is located is connected to the front end air load of the elastic element 110 through the spring Ka3 and the damping Ra3. , transmit force and displacement to promote air movement.
  • the reinforcing member 120 itself has an equivalent mass Mm n , and the reinforcing member 120 is connected to the central area 112 through the spring Kan ′ and the damping Ran ′ , while the reinforcing member 120 is connected to the central area 112 through the spring Kan ′ and the damping Ran ′ .
  • the front end of the elastic element 110 is connected with an air load. When the reinforcement 120 itself resonates, it drives the central area 112 to drive the elastic element 110 to produce a greater movement speed and displacement, thereby producing a greater sound pressure level.
  • each mass-spring-damping system has its own resonance peak frequency f0, and a large motion speed and displacement can occur at f0.
  • the vibration component 100 For example, the structural parameters of the elastic element 110 and/or the reinforcement 120
  • the mass-spring-damping system formed by the structures at different positions of the vibration component 100 can resonate in the required frequency range, thereby causing the frequency of the vibration component 100 to resonate.
  • the reinforcement 120 the vibration component 100 can be made to have a lighter mass, and the vibration component 100 can have a higher sound pressure level output. .
  • Figure 2 is a deformation diagram of the first resonance peak of the vibration component according to some embodiments of this specification.
  • Figure 3 is a diagram of the second resonance peak deformation of the vibration component according to some embodiments of this specification.
  • Figure 4 is a diagram of the second resonance peak deformation of the vibration component according to some embodiments of this specification.
  • the third resonance peak deformation diagram of the vibration component is shown in the example.
  • Figure 5 is the fourth resonance peak deformation diagram of the vibration component shown in some embodiments of this specification.
  • each part of the vibration component 100 will produce velocity resonance in different frequency bands, causing a larger velocity value to be output in the corresponding frequency band, so that the vibration component 100
  • the frequency response curve outputs a larger sound pressure value in the corresponding frequency range and has a corresponding resonance peak; at the same time, through multiple resonance peaks, the frequency response of the vibration component 100 has a relatively high sound pressure value in the audible sound range (for example, 20Hz-20kHz). High sensitivity.
  • the mass of the reinforcement 120, the mass of the elastic element 110, the equivalent air mass, and the equivalent mass of the driving end are combined to form a total equivalent mass Mt, and the equivalent damping of each part forms a total equivalent damping Rt.
  • the elasticity The element 110 (especially the elastic element 110 in the folded ring area 114, the suspended area between the folded ring area 114 and the reinforcement 120) has greater compliance and provides stiffness Kt for the system, thus forming a mass Mt-spring Kt- Damped Rt system, this system has a resonant frequency.
  • the system When the driving end excitation frequency is close to the speed resonance frequency of the system, the system resonates (as shown in Figure 2), and in the frequency band near the speed resonance frequency of the Mt-Kt-Rt system Output a larger speed value v a . Since the output sound pressure amplitude of the vibrating component 100 is positively correlated with the sound speed (p a ⁇ v a ), a resonance peak will appear in the frequency response curve, which is defined in this specification as The first resonance peak of the vibration component 100.
  • FIG. 2 which shows the vibration condition of the vibration assembly 100 at the AA cross-section position.
  • the white structure in FIG. 2 represents the shape and position of the reinforcement 120 before deformation, and the black structure represents the reinforcement 120 at the cross-section position.
  • FIG. 2 only shows the structural condition of the vibration assembly 100 on the AA cross-section from the center of the reinforcement 120 to one edge of the elastic element 110, that is, half of the AA cross-section. The other part of the AA cross-section is not shown. One half is symmetrical to the situation shown in Figure 2. It can be seen from the vibration of the vibration component 100 at the AA cross-sectional position that at the position of the first resonance peak, the main deformation position of the vibration component 100 is the part of the elastic element 110 connected to the fixed area 116 .
  • the frequency of the first resonance peak of the vibration component 100 may be related to the ratio of the mass of the vibration component 100 and the elastic coefficient of the elastic element 110 .
  • the frequency range of the first resonance peak includes 180 Hz-3000 Hz.
  • the frequency range of the first resonance peak includes 200 Hz-3000 Hz.
  • the frequency range of the first resonance peak includes 200 Hz-2500 Hz.
  • the frequency range of the first resonance peak includes 200 Hz-2000 Hz.
  • the frequency range of the first resonance peak includes 200 Hz-1000 Hz.
  • the first resonance peak of the vibration component 100 can be located within the above frequency range.
  • connection area 115 between the fixed area 116 of the elastic element 110 and the ring area 114 is in a suspended state. This part of the area has an equivalent mass Mm 1 , and this area is fixedly connected to the shell through the spring Km and the damping Rm. At the same time, the connection area 115 The spring Ka 1 , the damper Ra 1 are connected to the air load at the front end of the elastic element 110 to transmit force and displacement to promote air movement.
  • the ring area 114 has a local equivalent mass Mm 2 , and this area is connected to the connection area 115 through the spring Ka 1 ′ and the damping Ra 1 ′. At the same time, the ring area 114 is connected to the front end air of the elastic element 110 through the spring Ka 2 and the damping Ra 2
  • the load connection transmits force and displacement to promote air movement.
  • the suspended area 1121 There is a suspended area 1121 between the area where the reinforcement 120 is provided in the central area 112 and the ring area 114 .
  • the suspended area 1121 has a local equivalent mass Mm 3 , and this area is connected to the ring area 114 through spring Ka 2 ′ and damping Ra 2 ′.
  • the area where the reinforcement 120 is located is connected to the front end of the elastic element 110 through spring Ka 3 , damping Ra 3 Air-loaded connections transmit force and displacement to propel air movement.
  • This resonance peak is mainly generated by the vibration mode of the suspended area between the connecting area 115, the ring area 114, the area where the reinforcement 120 is provided in the central area 112, and the ring area 114.
  • Figure 3 respectively shows the first The deformation positions of the vibration component 100 before the second resonance peak (the upper structural illustration in FIG. 3 ) and after the second resonance peak (the lower structural illustration in FIG. 3 ).
  • FIG. 3 it can be seen from the vibration of the vibration component 100 at the AA cross-sectional position that the main deformation positions of the vibration component 100 before and after the frequency of the second resonance peak are the ring area 114 and the suspended area 1121 .
  • the frequency of the second resonance peak of the vibration component 100 may be related to the ratio of the mass of the elastic element 110 to the elastic coefficient of the elastic element 110 .
  • the frequency range of the second resonance peak of the vibration component 100 may include 1000 Hz-10000 Hz.
  • the frequency range of the second resonance peak of the vibration component 100 may include 3000 Hz-7000 Hz.
  • the frequency range of the second resonance peak of the vibration component 100 may include 3000 Hz-6000 Hz.
  • the frequency range of the second resonance peak of the vibration component 100 may include 4000 Hz-6000 Hz.
  • the range of the second resonance peak of the vibration component 100 can be within the above frequency range.
  • the reinforcement 120 itself has an equivalent mass Mm n , and the reinforcement 120 is connected to the central area 112 through the spring Kan ' and the damping Ran '. At the same time, the reinforcement 120 is connected to the front end air load of the elastic element 110 through the spring Kan ' , the damping Ran ' Connection, when the reinforcement 120 itself resonates, it drives the central area 112 to drive the elastic element 110 to produce a greater movement speed and displacement, thereby producing a greater sound pressure level.
  • the reinforcement 120, the connection area 115, the folding area 114, the suspended area 1121 between the area where the reinforcement 120 is provided in the central area 112 and the folding area 114, the equivalent air mass, and the driving end equivalent mass are combined to form a total equivalent
  • the mass Mt 1 and the equivalent damping of each part form the total equivalent damping Rt 1 .
  • the reinforcement 120 and the elastic element 110 (especially the area where the central area 112 is covered by the reinforcement 120 ) have relatively large stiffness and provide stiffness Kt for the system. 1 , so a mass Mt 1 - spring Kt 1 - damper Rt 1 system is formed.
  • This system has an annular area in the diameter direction of the central area 112 as an equivalent fixed fulcrum.
  • the inner edge of the annular area moves in the opposite direction to the outer edge of the annular area.
  • a vibration mode of the flipping motion is formed.
  • the connecting area 115, the folding ring area 114, the suspended area 1121 between the area where the reinforcing member 120 is provided in the central area 112 and the folding area 114 vibrates under the driving of the reinforcing member 120, achieving a The resonance mode with flipping motion as the vibration shape (as shown in Figure 4), this resonance is also the resonance frequency point of the equivalent mass Mt 1 - spring Kt 1 - damping Rt 1 system.
  • the Mt 1 -Kt 1 -Rt 1 system When the driving end excitation frequency is close to the system At the speed resonance frequency, the Mt 1 -Kt 1 -Rt 1 system resonates and outputs a large speed value v a in the frequency band near the speed resonance frequency of the Mt 1 -Kt 1 -Rt 1 system. Due to the vibration component 100 The output sound pressure amplitude is positively correlated with the sound speed (p a ⁇ v a ), so a resonance peak will appear in the frequency response curve, which is defined as the third resonance peak of the vibrating component 100 in this specification. In some embodiments, see FIG. 4 , which respectively shows the vibration before the third resonance peak (the structural illustration located above in FIG. 4 ) and after the third resonance peak (the structural illustration located below in FIG. 4 ).
  • the deformation position of the component 100 can be known from the vibration of the vibration component 100 at the AA cross-sectional position.
  • the main deformation position of the vibration component 100 is the flipping of the reinforcement 120 Deformation.
  • the third resonance peak of vibration assembly 100 may be related to the stiffness of stiffener 120 .
  • the frequency range of the third resonance peak may include 5000 Hz-12000 Hz.
  • the frequency range of the third resonance peak may include 6000 Hz-12000 Hz.
  • the frequency range of the third resonance peak may include 6000 Hz-10000 Hz.
  • the range of the third resonance peak of the vibration component 100 can be within the above frequency range.
  • the reinforcement 120 has no less than one hollow area corresponding to the central area 112.
  • Each hollow area is a mass-spring-damping system with equivalent mass Mm i , equivalent stiffnesses Kai and Kai ' , and equivalent damping. Ra i and Ra i '.
  • the hollow area is connected to adjacent hollow areas through the spring Kai ' and the damping Ra i ', and is connected to the area and folds supported by the reinforcement 120 in the central area 112 through the spring Kai ' and the damping Ra i '.
  • the suspended areas 1121 between the ring areas 114 are connected, and at the same time, the hollow area is connected to the air load at the front end of the elastic element 110 through the spring Kai and the damping Ra i , transmitting force and displacement to promote air movement.
  • each hollow area is separated by the strip structure 124 of the reinforcement 120, each hollow area can form a different resonant frequency, and independently promote the movement of the air area connected to it to generate corresponding sound pressure; further , by designing the position, size, and quantity of each strip structure 124 of the reinforcement 120, each hollow area with different resonant frequencies can be realized, so that there is no less than one high frequency on the frequency response curve of the vibration component 100.
  • Frequency resonance peak (the fourth resonance peak).
  • the range of no less than one high-frequency resonance peak (ie, the fourth resonance peak) as described above may include 10,000 Hz-18,000 Hz.
  • each strip structure 124 are designed so that the resonant frequencies of each hollow area are equal or close to each other.
  • the difference in resonant frequencies of each hollow area is within the range of 4000 Hz, so that the frequency response curve of the vibration component 100 has a high-frequency resonance peak with a large output sound pressure level, which is defined in this specification. is the fourth resonance peak of the vibration component 100 (as shown in Figure 5).
  • the resonant frequency of each hollow region can be adjusted, so that the fourth resonance peak of the vibration component 100 is located in the above frequency range.
  • the ratio of the area of each hollow region to the thickness of the elastic element 110 ranges from 100 mm to 1000 mm. In some embodiments, in order to make the range of the fourth resonance peak of the vibration component 100 fall within the above frequency range, the ratio of the area of each hollow region to the thickness of the elastic element 110 ranges from 120 mm to 900 mm.
  • the ratio of the area of each hollow region to the thickness of the elastic element 110 ranges from 150 mm to 800 mm. In some embodiments, in order to make the range of the fourth resonance peak of the vibration component 100 fall within the above frequency range, the ratio of the area of each hollow region to the thickness of the elastic element 110 ranges from 150 mm to 700 mm.
  • Figure 6 is a frequency response curve of a vibration component 100 with different third and fourth resonant frequency differences according to some embodiments of this specification.
  • the abscissa represents frequency (unit Hz), and the ordinate represents Sensitivity(SPL).
  • SPL Sensitivity
  • the frequency difference ⁇ f between the fourth resonant peak 240 and the third resonant peak 230 is too small (as shown in Figure 6 ⁇ f1), the frequency of the fourth resonant peak 240 will decrease, resulting in The sound pressure level in the high-frequency frequency range (for example: 12kHz-20kHz) decreases, and the frequency band of the vibration component becomes narrower.
  • the third resonance peak 230 can be moved to the left and/or the fourth resonance peak 240 can be moved to the right, thereby increasing the frequency difference between the fourth resonance peak 240 and the third resonance peak 230 ⁇ f.
  • the frequency difference ⁇ f between the fourth resonance peak 240 and the third resonance peak 230 ranges from 80 Hz to 15000 Hz. In some embodiments, the frequency difference ⁇ f between the fourth resonance peak 240 and the third resonance peak 230 ranges from 100 Hz to 13000 Hz. In some embodiments, the frequency difference ⁇ f between the fourth resonance peak 240 and the third resonance peak 230 ranges from 200 Hz to 12000 Hz. In some embodiments, the frequency difference ⁇ f between the fourth resonance peak 240 and the third resonance peak 230 ranges from 300 Hz to 11000 Hz. In some embodiments, the frequency difference ⁇ f between the fourth resonance peak 240 and the third resonance peak 230 ranges from 400 Hz to 10000 Hz.
  • the frequency difference ⁇ f between the fourth resonance peak 240 and the third resonance peak 230 ranges from 500 Hz to 9000 Hz. In some embodiments, the frequency difference ⁇ f between the fourth resonance peak 240 and the third resonance peak 230 ranges from 200 Hz to 11000 Hz. In some embodiments, the frequency difference ⁇ f between the fourth resonance peak 240 and the third resonance peak 230 ranges from 200 Hz to 10000 Hz. In some embodiments, the frequency difference ⁇ f between the fourth resonance peak 240 and the third resonance peak 230 ranges from 2000 Hz to 15000 Hz. In some embodiments, the frequency difference ⁇ f between the fourth resonance peak 240 and the third resonance peak 230 ranges from 3000 Hz to 14000 Hz. In some embodiments, the frequency difference ⁇ f between the fourth resonance peak 240 and the third resonance peak 230 ranges from 4000 Hz to 13000 Hz.
  • the vibration component 100 can be made to appear the required high-order mode within the audible range of the human ear (20Hz-20000Hz).
  • the above-mentioned first resonant peak 210, second resonant peak 220, third resonant peak 230 and fourth resonant peak 240 appear, that is, the number of resonant peaks in the frequency response curve of the vibrating component 100 in the frequency range of 20Hz-20000Hz is 4.
  • the vibration component 100 has higher sensitivity in a wider frequency band range.
  • the vibration component 100 can have only three resonance peaks in the audible sound range (20 Hz-20000 Hz). For example, when the frequency difference between the second resonance peak and the third resonance peak of the vibration component 100 is less than 2000 Hz, the second resonance peak and the third resonance peak appear as one resonance peak on the frequency response sound pressure level curve of the vibration component 100 .
  • the reinforcement 120 has no less than one suspended area corresponding to the central area 112.
  • FIG. 7B is a schematic diagram when the second and third resonance peaks overlap according to some embodiments of this specification.
  • the structure and size of the reinforcement 120 are designed, including the overall size of the reinforcement 120, the number and size of the strip structures 124, the arrangement position of the strip structures 124, the area where the reinforcement 120 is located in the central area 112, and the size of the reinforcement 120.
  • the area of the suspended area 1121 between the ring areas 114, the pattern design of the ring area 114 (such as the width of the ring, arch height, arch shape), and the area of the connecting area 115 can be used to design the second resonant peak 220 and the second resonant peak 220 of the vibration component 100.
  • the frequency difference of the three resonant peaks 230 when the frequency difference between the second resonance peak 220 and the third resonance peak 230 of the vibration component 100 is in the range of 2000Hz-3000Hz, the frequency response sound pressure level curve (such as the frequency response curve 710) of the vibration component 100, There is no valley between the second resonance peak 220 and the third resonance peak 230 , and the existence of the second resonance peak 220 and the third resonance peak 230 can still be discerned on the frequency response curve (corresponding to the dotted line in the figure).
  • the frequency response sound pressure level curve (such as the frequency response curve 720 ) of the vibration component 100
  • the second resonance peak 220 and the third resonance peak 230 are embodied as one resonance peak (corresponding to the solid line in the figure), which can make the medium and high frequency range (3000Hz-10000Hz) have higher sensitivity.
  • the reinforcement 120 has no less than one hollow area corresponding to the central area 112.
  • Each hollow area is a mass-spring-damping system.
  • the position, size, and number of each strip structure 124 are such that the resonant frequencies of each hollow area are equal or close to each other. In some embodiments, the difference in resonant frequencies of each hollow region is within the range of 4000 Hz, which can cause one or more high-frequency resonance peaks with a large output sound pressure level (i.e., the fourth) on the frequency response curve of the vibration component 100 resonance peak).
  • the resonant frequency of each hollow area is higher than the audible sound range, or the resonant frequency of each hollow area is different.
  • the vibration phases of different hollow areas in different frequency bands are different, forming the effect of sound superposition and cancellation, and a high-frequency roll-off effect can be obtained.
  • the sound pressure level frequency response curve of the vibration component 100 Does not reflect the fourth resonance peak.
  • FIG. 7D is a schematic diagram of the frequency response curve when the vibration component 100 has two resonance peaks according to some embodiments of this specification.
  • the structure of the reinforcement 120 when the frequency difference between the second resonance peak 220 and the third resonance peak 230 of the vibration component 100 is less than 2000 Hz, on the frequency response sound pressure level curve of the vibration component 100 , the second resonance The peak 220 and the third resonance peak 230 are embodied as one resonance peak.
  • the position, size, and quantity of each strip structure 124 of the reinforcement 120 the resonant frequency of each hollow area is higher than the audible sound range, or the resonant frequency of each hollow area is different and in the high frequency range.
  • the vibration phases of different hollow areas in different frequency ranges are different, forming the effect of sound superposition and cancellation, and a high-frequency roll-off effect can be obtained.
  • the fourth resonance is not reflected in the sound pressure level frequency response curve of the vibration component 100 peak.
  • the vibration component 100 has a certain bandwidth and has high sensitivity output characteristics in the mid-to-high frequency range (3000Hz-10000Hz).
  • the area and thickness of the suspended region 1121 and the ring region 114 of the elastic element 110 can be designed to ensure that the second resonance peak of the vibration component 100 is in the required frequency range.
  • the second resonance peak of the vibration component 100 may range from 1000 Hz to 10000 Hz.
  • the second resonance peak of the vibration component 100 may range from 3000 Hz to 7000 Hz.
  • the frequency difference between the second resonance peak and the third resonance peak of the vibration component 100 is less than 3000 Hz.
  • FIG. 8A is a schematic structural diagram of a vibration assembly having a reinforcement member with a single ring structure according to some embodiments of this specification.
  • the horizontal plane projected area of the suspended region 1121 i.e., the projected area of the suspended region 1121 along the vibration direction of the elastic element 110
  • the horizontal plane projected area of the folded ring region 114 i.e., the folded ring region 114 along the elastic element 110
  • the projected area of the vibration direction is Se
  • the sum of the horizontal plane projected area S v of the suspended region 1121 and the horizontal plane projected area Se of the ring region 114 is S s .
  • the physical quantity ⁇ (unit: mm) as the ratio of S s to the thickness Hi of the elastic element 110 (also called the diaphragm):
  • the ratio ⁇ of S s to the diaphragm thickness Hi may be in the range of 5000mm-12000mm.
  • the value range of ⁇ is 6000 mm-10000 mm.
  • the value range of ⁇ may be 6000mm-9000mm.
  • the value range of ⁇ may be 6000mm-8000mm. In some embodiments, in order to further adjust the frequency range of the second resonance peak of the vibration component 100 to move to high frequency, the value range of ⁇ may be 6000mm-7000mm.
  • the relationship between the areas of the suspended region 1121 and the ring region 114 and the thickness of the elastic element 110 will affect the local equivalent mass Mm 3 and the local equivalent mass Mm 2 , the local area stiffness Ka 2 ′ and the local area stiffness Ka 1 ', and then affects the equivalent mass Ms, equivalent stiffness Ks, and equivalent damping Rs formed by the connection area 115, the ring area 114, and the suspended area 1121, thereby controlling the range of the second resonance peak of the vibration component 100.
  • the second resonance peak of the vibration component 100 can also be controlled through the arch height design of the ring in the ring region 114 .
  • FIG. 8B is a schematic diagram of the frequency response curve of a vibration component according to other embodiments of this specification.
  • FIG. 9A is a partial structural diagram of a vibration component according to some embodiments of this specification.
  • the ring arch height ⁇ h of the ring region 114 can be defined, and the physical quantity ⁇ (unit: mm) is defined as the ratio of S s to the ring arch height ⁇ h of the diaphragm:
  • the value range of ⁇ may be 50mm-600mm. In some embodiments, the value range of ⁇ may be 100mm-500mm. In some embodiments, in order to make the frequency range of the second resonance peak of the vibration component 100 be 3000 Hz-7000 Hz, the value range of ⁇ may be 200 mm-400 mm. In some embodiments, in order to further move the frequency range of the second resonance peak of the vibration component 100 to a low frequency within 3000 Hz-7000 Hz, the value range of ⁇ may be 300 mm-400 mm.
  • the value range of ⁇ in order to further move the frequency range of the second resonance peak of the vibration component 100 to a low frequency within 3000 Hz-7000 Hz, the value range of ⁇ may be 350 mm-400 mm. In some embodiments, in order to move the frequency range of the second resonance peak of the vibration component 100 to a high frequency within the range of 3000 Hz to 7000 Hz, the value range of ⁇ may be 200 mm to 300 mm. In some embodiments, in order to further move the frequency range of the second resonance peak of the vibration component 100 to a high frequency within the range of 3000 Hz to 7000 Hz, the value range of ⁇ may be 200 mm to 250 mm.
  • the three-dimensional size of the fold region 114 can be changed while the horizontal projected areas of the fold region 114 and the suspended region 1121 remain unchanged, thereby changing the fold region 114 The stiffness Ka 1 ', thereby achieving control of the second resonance peak of the speaker.
  • the output sound pressure level of the speaker can also be controlled by coordinating the design of the size of the reinforcement.
  • FIG. 9B is a schematic diagram of the frequency response curve of a vibration component according to other embodiments of this specification.
  • the resonant frequency of the second resonant peak 220 decreases, and when ⁇ ranges from 200 mm to 400 mm, the frequency range of the second resonant peak of the vibration component 100 can be better controlled to be from 3000 Hz to 3000 Hz. 7000Hz.
  • the horizontal projected area of the central area 112 is defined as Sc
  • the value range is 0.05-0.7. In some embodiments, The value range is 0.1-0.5. In some embodiments, in order to make the frequency range of the second resonance peak of the vibration component 100 be 3000Hz-7000Hz, The value range is 0.15-0.35. In some embodiments, in order to further move the second resonance peak of the vibration component 100 to a high frequency in the frequency range 3000Hz-7000Hz, The value range is 0.15-0.25. In some embodiments, The value range is 0.15-0.2. In some embodiments, in order to further move the second resonance peak of the vibration component 100 to a low frequency in the frequency range 3000Hz-7000Hz, The value range is 0.25-0.35. In some embodiments, in order to further move the second resonance peak of the vibration component 100 to a low frequency in the frequency range 3000Hz-7000Hz, The value range is 0.3-0.35.
  • the suspended area 1121 and the ring area 114 will generate local resonance.
  • the size of the reinforcement 120 i.e., the size of the reinforcement 120
  • the design can make the reinforcement 120 achieve a certain bending deformation in this frequency range, thereby achieving a superposition and increase of the sound pressure in different areas of the diaphragm, thereby achieving the maximum vibration component or speaker at the second resonance peak. Sound pressure level output.
  • FIG. 9C is a schematic diagram of the frequency response curve of a vibration component according to other embodiments of this specification.
  • the frequency response curve 940 in the figure represents when The frequency response curve of the vibration component when frequency response curve of the vibrating component. It can be seen from the frequency response curve 940 that When , the frequency of the second resonance peak 220 of the vibration component 100 is 4000Hz; it can be seen from the frequency response curve 950 that, , the frequency of the second resonance peak 220 of the vibration component 100 is approximately 6000 Hz. Therefore, with decreases, the resonant frequency of the second resonant peak 220 increases, and when When the value range is 0.15-0.35, the frequency range of the second resonance peak of the vibration component 100 can be better controlled to be 3000Hz-7000Hz.
  • the strip structures 124 may have different widths, shapes, and quantities to change the hollow area of the reinforcement 120 (corresponding to the suspended area of the central area 112), thereby adjusting the frequency response of the speaker.
  • the strip structures 124 may have different widths, shapes, and quantities to change the hollow area of the reinforcement 120 (corresponding to the suspended area of the central area 112), thereby adjusting the frequency response of the speaker.
  • the resonant frequency of the vibration component 100 can be controlled by designing the area of the hollow region (for example, designing the number and position of the strip structures 124 of the reinforcement 120, the number and position of the ring structures 122, etc.). To improve the performance of the vibration component 100.
  • the fourth resonance peak of the vibration component 100 may range from 8000 Hz to 20000 Hz. In some embodiments, the fourth resonance peak of the vibration component 100 may range from 10,000 Hz to 18,000 Hz.
  • FIG. 10A is a deformation diagram of the CC cross-section of a vibration assembly with a single-ring structure reinforcement shown near the fourth resonance peak frequency according to some embodiments of this specification. It can be seen from FIG. 6 that the frequency difference ⁇ f between the fourth resonance peak 240 and the third resonance peak 230 has a great influence on the flatness of the high-frequency response curve of the vibration component 100 . In some embodiments, referring to FIG. 10A , it can be seen from the vibration of the vibration component 100 at the CC cross-sectional position that near the frequency of the fourth resonance peak, the main deformation position of the vibration component 100 is the deformation produced by the hollow area of the central area 112 .
  • the fourth resonance peak of the vibration component 100 can be achieved by controlling each hollow area of the reinforcement 120 corresponding to the central area 112 to be a mass-spring-damping system, corresponding to the equivalent mass Mmi and the equivalent stiffness Kai. 240 control.
  • the number and size of the strip structures 124 and the annular structure 122 can be designed to design the area of each hollow area in the central region 112, and the area of each hollow area is defined as Si .
  • FIG. 10A shows the fourth resonance peak deformation diagram of the vibration assembly 100 with the reinforcement 120 of a single ring structure, this conclusion still applies to the vibration assembly of the reinforcement 120 with a multi-ring structure (such as Vibration assembly 100 shown in Figure 5).
  • this specification defines a physical quantity: the area of any hollow region (that is, the projected area of the hollow part along the vibration direction of the elastic element 110) S i and the vibration of each hollow region part
  • the ratio of the thickness H i of the membrane (such as the elastic element 110) is the area to thickness ratio ⁇ (unit: mm):
  • the frequency position of the fourth resonance peak of the vibration component can be adjusted by designing the ⁇ value.
  • the preset range of the Young's modulus of the diaphragm is 5*10 ⁇ 8Pa-1*10 ⁇ 10Pa.
  • the preset range of the Young's modulus of the diaphragm is 1*10 ⁇ 9Pa-5*10 ⁇ 9Pa.
  • the preset range of diaphragm density is 1*10 ⁇ 3kg/m3-4*10 ⁇ 3kg/m3.
  • the preset range of diaphragm density is 1*10 ⁇ 3kg/m3-2*10 ⁇ 3kg/m3.
  • the area to thickness ratio ⁇ ranges from 1000 mm to 10000 mm. In some embodiments, the area to thickness ratio ⁇ ranges from 1500 mm to 9000 mm. In some embodiments, the area to thickness ratio ⁇ ranges from 2000 mm to 8000 mm. In some embodiments, the area to thickness ratio ⁇ ranges from 2500 mm to 7500 mm. In some embodiments, the area to thickness ratio ⁇ ranges from 3000 mm to 7000 mm. In some embodiments, the area to thickness ratio ⁇ ranges from 3500 mm to 6500 mm. In some embodiments, the area to thickness ratio ⁇ ranges from 4000 mm to 6000 mm.
  • the equivalent mass Mmi and equivalent stiffness Kai of each hollow region can be controlled, thereby achieving control of the fourth resonance peak of the speaker.
  • the fourth resonance peak frequency of the response curve 1030 is approximately 16000 Hz
  • the reinforcing member 120 has a multi-annular structure (eg, a double annular structure), that is, the reinforcing member 120 includes a plurality of radially adjacent annular structures (eg, a first annular structure). , second annular structure, etc.), each annular structure has a different diameter, and the annular structure with a smaller diameter is arranged inside the annular structure with a larger diameter.
  • This specification defines the area of each hollow area of the elastic element 110 inside the first annular structure as S 1i .
  • the elastic element between the first annular structure and the second annular structure The area of each hollow area of 110 is S 2i .
  • the reinforcement 120 may also have more ring structures 122 , and outwardly define the area of each hollow area of the elastic element 110 between the n-1th ring and the nth ring as S ni .
  • the hollow area between the annular structures of different diameters may include a first hollow area and a second hollow area, a distance between the centroid of the first hollow area and the center of the central area, and a distance between the centroid of the second hollow area and the central area. The distance between the centers is different.
  • This specification defines the physical quantity elastic element 110's hollow area area ratio ⁇ (unit is 1) as the ratio of the first hollow area area S ki to the second hollow area area S ji :
  • Figure 12A is the frequency response curve of the vibration component corresponding to Figure 11.
  • S 2i i.e., the first hollow area
  • S 1i i.e., the second hollow area
  • area ratio ⁇ are 5.9, 4.7, 3.9, and 3.2 in sequence.
  • the area ratio of each hollow area in the central area 112 is as small as possible.
  • the ratio ⁇ between the areas S ki and S ji of the first and second hollow areas ranges from 0.1 to 10.
  • the ratio ⁇ between the areas S ki and S ji of the first hollow region and the second hollow region ranges from 0.16 to 6.
  • the ratio ⁇ between the areas S ki and S ji of the first hollow region and the second hollow region ranges from 0.2 to 5.
  • the ratio ⁇ between the areas S ki and S ji of the first hollow region and the second hollow region ranges from 0.25 to 4.
  • the ratio ⁇ between the areas S ki and S ji of the first hollow region and the second hollow region ranges from 0.25 to 1. In some embodiments, the ratio ⁇ between the areas S ki and S ji of the first hollow region and the second hollow region ranges from 0.25 to 0.6. In some embodiments, the ratio ⁇ between the areas S ki and S ji of the first hollow region and the second hollow region ranges from 0.1 to 4. In some embodiments, the ratio ⁇ between the areas S ki and S ji of the first hollow region and the second hollow region ranges from 0.1 to 3. In some embodiments, the ratio ⁇ between the areas S ki and S ji of the first hollow region and the second hollow region ranges from 0.1 to 2. In some embodiments, the ratio ⁇ between the areas S ki and S ji of the first hollow region and the second hollow region ranges from 0.1 to 1.
  • the ratio of the area of each hollow area of the elastic element 110 will affect the difference in resonant frequency of each hollow area, and the resonant frequencies of each hollow area are equal or close, which can make the sound pressure of each hollow area superimpose, thereby increasing the sound pressure of each hollow area.
  • the output sound pressure level of the speaker at the fourth resonance peak position is equal or close.
  • FIG. 10C is a schematic diagram of a frequency response curve of a vibration component according to other embodiments of this specification.
  • the output sound pressure level (amplitude) of the frequency response curve 1050 at the fourth resonance peak is relatively high, and the output sound pressure level (amplitude) of the frequency response curve 1060 at the fourth resonance peak is relatively low. . Therefore, when the value range of ⁇ is 0.25-4, the vibration component 100 can have a higher output sound pressure level in the high frequency range (eg, 10000Hz-18000Hz).
  • the mass, center of mass, stiffness of the reinforcement 120 , and the central area 112 can be achieved.
  • the quality and stiffness of the hollow region are adjusted to realize the adjustment of the first resonance peak, the third resonance peak and the fourth resonance peak of the vibration component 100 .
  • the lateral area ratio ⁇ (unit is 1) of the reinforced part 120 and the reinforced part 120 is defined as the projected area S r of the reinforced part and the projected area S r of the reinforced part 120 in the projected shape of the reinforced part 120 along the vibration direction.
  • the lateral area ratio ⁇ of the reinforcing part 120 to the reinforcing part 120 is 0.1-0.8. In some embodiments, the lateral area ratio ⁇ of the reinforcing part 120 to the reinforcing part 120 is 0.2-0.7. In some embodiments, the lateral area ratio ⁇ of the reinforcing part 120 to the reinforcing part 120 is 0.1-0.7. In some embodiments, the lateral area ratio ⁇ of the reinforcing part 120 to the reinforcing part 120 is 0.2-0.6. In some embodiments, the lateral area ratio ⁇ of the reinforcing part 120 to the reinforcing part 120 is 0.3-0.6.
  • the projected area of the reinforcement 120 along the vibration direction and the projected area of the maximum profile of the reinforcement 120 along the vibration direction it is possible to control the mass, center of mass, and stiffness of the reinforcement 120 and to hollow out the central area 112
  • the mass and stiffness of the area are adjusted to control the total equivalent mass Mt formed by the combination of the mass of the reinforcement 120, the mass of the elastic element 110, the equivalent air mass, and the equivalent mass of the driving end, thereby controlling the first resonance of the speaker. peak, the third resonance peak and the fourth resonance peak.
  • FIG. 12B is a schematic diagram of the frequency response curve of a vibration component according to other embodiments of this specification.
  • the frequency response curve 1210, the frequency response curve 1220 and the frequency response curve 1230 have a first resonance peak 210, a second resonance peak 220, a third resonance peak 230 and a fourth resonance peak 240.
  • Figures 13A and 13B are schematic structural diagrams of vibration components with different numbers of strip structures according to some embodiments of this specification.
  • the overall mass of the vibration assembly 100 can be adjusted, so that the mass of the reinforcement 120, the mass of the elastic element 110, the equivalent air mass, and the equivalent mass of the driving end are combined to form a total equivalent
  • the mass Mt changes, so the resonant frequency of the mass Mt-spring Kt-damping Rt system changes, which in turn causes the first-order resonant frequency of the vibration component 100 to change, causing the low-frequency band before the first resonant frequency of the vibration component 100 and the first
  • the mid-band sensitivity changes after the resonant frequency.
  • a larger number of strip structures 124 can be designed, so that the total equivalent mass Mt is increased, and the first resonant frequency of the vibration component 100 is advanced, so that the sensitivity of the low frequency band before the first resonant frequency of the vibration component 100 is improved.
  • a smaller number of strip structures 124 is designed, so that the total equivalent mass Mt is reduced, and the first resonant frequency of the vibration component 100 is moved backward, so that the sensitivity of the mid-frequency band after the first resonant frequency of the vibration component 100 is improved, for example , which can improve the sensitivity of the frequency range after 3000Hz.
  • the sensitivity of the frequency range after 2000Hz can be improved.
  • the sensitivity of the frequency range after 1000Hz can be improved.
  • the sensitivity of the frequency range after 500Hz can be improved.
  • the sensitivity of the frequency range after 300Hz can be improved.
  • the stiffness of the reinforcement 120 can also be adjusted, so that if the stiffness Kt 1 provided by the reinforcement 120 and the elastic element 110 for the system changes, then the reinforcement 120, the connection area 115, The suspended area between the ring area 114, the central area 112 covered by the reinforcement 120 and the ring area 114, the equivalent air mass, and the equivalent mass of the drive end combine to form a total equivalent mass Mt 1 , and the equivalent damping of each part forms
  • the total equivalent damping Rt1, forming a mass Mt 1 - spring Kt 1 - damping Rt 1 system takes a certain annular area in the diameter direction of the reinforcement 120 as an equivalent fixed fulcrum, and the resonant frequency of the ring's flipping motion changes, so that This causes the third resonance position of the vibration component 100 to change.
  • the number of the strip structures 124 of the reinforcement 120 is adjustable, and the positions of the first resonance peak, the third resonance peak, and the fourth resonance peak of the vibration component 100 can be adjusted according to actual application requirements, so that the vibration can be adjusted.
  • the frequency response of the component 100 enables controllable adjustment.
  • the shape of the strip structure 124 along the vibration direction of the elastic element 110 includes at least one of a rectangle, a trapezoid, a curve, an hourglass shape, and a petal shape
  • the shape of the strip structure 124 can be adjusted by adjusting the shape of the strip structure 124 .
  • Figures 14A-14D are schematic structural diagrams of vibration components with bar-shaped structures of different widths according to some embodiments of this specification, wherein the bar-shaped structure 124 in Figure 14A is an inverted trapezoid (i.e. The short side of the trapezoid is close to the center of the reinforcement 120), the bar-shaped structure 124 in Figure 14B is trapezoidal (that is, the short side of the trapezoid is far away from the center of the reinforcement 120), the bar-shaped structure 124 in Figure 14C is an outer arc shape, Figure The strip structure 124 in 14D is an inner arc shape.
  • the bar-shaped structure 124 in Figure 14A is an inverted trapezoid (i.e. The short side of the trapezoid is close to the center of the reinforcement 120)
  • the bar-shaped structure 124 in Figure 14B is trapezoidal (that is, the short side of the trapezoid is far away from the center of the reinforcement 120)
  • the center of mass position of the reinforcement 120 can be effectively adjusted.
  • the stiffness of the reinforcement 120 can also be changed without changing the mass of the reinforcement 120, so that the reinforcement 120 and the elastic element 110 (especially the area where the central area 112 is covered by the reinforcement 120) provide the system with
  • the change in stiffness Kt 1 further causes the resonant frequency of the flipping motion of the mass Mt 1 -spring Kt 1 -damping Rt 1 system to change, thereby causing the third resonant frequency of the vibration component 100 to change.
  • the bar-shaped structure 124 can have different local stiffnesses at different locations extending from the center to the periphery.
  • the driving end frequency is close to the resonance frequency of the Mt 1 - spring Kt 1 - damping Rt 1 system
  • the connection area 115 between the fixed area 116 and the ring area 114, the ring area 114, and the central area 112 are covered by the reinforcement 120.
  • the suspended area between the ring areas 114 vibrates driven by the reinforcement 120 and achieves a resonance peak with an adjustable 3dB bandwidth.
  • the outer arc shape (defined as an outer arc shape that protrudes outward and an inner arc shape that is concave inward), the outer arc shape can be an arc, an ellipse, a higher-order function arc, and any other external arc) strip structure 124, which can obtain the third resonance peak of the vibration component 100 with a larger 3dB bandwidth, and can be applied to scenarios requiring low Q value and wide bandwidth.
  • the inner arc can be an arc, an ellipse, a high-order function arc, and other arbitrary internal arcs
  • the third resonant peak of the vibration component 100 with high sensitivity and small 3dB bandwidth can be obtained, and can be applied to scenes requiring high Q value and local high sensitivity.
  • Figures 15A and 15B are schematic structural diagrams of vibration components with bar-shaped structures of different shapes according to some embodiments of this specification.
  • the bar-shaped structure 124 in Figure 15A is a rotating shape.
  • Figure The strip structure 124 in 15B is S-shaped.
  • the stiffness of the reinforcement 120 can be adjusted, so that the reinforcement 120 and the elastic element 110 (especially the area where the central area 112 is covered by the reinforcement 120) are The stiffness Kt 1 provided by the system changes, which further causes the mass Mt 1 - spring Kt 1 - damping Rt 1 system to change the resonant frequency of the flipping motion, thereby causing the third resonance position of the vibration component 100 to change.
  • the size of the suspended area corresponding to the central area 112 of the reinforcement member can also be adjusted, so that each has an equivalent mass Mmi , equivalent stiffnesses Kai and Kai ', and an equivalent damping Ra.
  • the stress distribution inside the reinforcement 120 can also be adjusted and the processing deformation of the reinforcement 120 can be controlled.
  • FIGS. 16A-16E are schematic structural views of reinforcement members with strip structures of different shapes according to some embodiments of this specification.
  • the width gradually decreases from the center to the edge.
  • the spoke angle ⁇ is defined as the angle between the two sides of the projected shape of the bar structure on the projection plane perpendicular to the vibration direction.
  • the vibration component can be adjusted by setting the size of ⁇ resonance peak.
  • the included angle ⁇ is the angle between the two sides of the spoke. In some embodiments, for a bar-shaped structure 124 with curved sides (as shown in FIG. 16E ), the included angle ⁇ is the angle between the tangent lines of the two sides of the bar-shaped structure 124 .
  • the spoke angle is defined as ⁇ i .
  • the resonance peak of the vibrating component can be adjusted.
  • the included angle ⁇ i is the included angle between the two sides of the spoke.
  • the included angle ⁇ i is the angle between the tangent lines of the two side edges of the spoke.
  • the stiffness of the reinforcement 120 itself can be changed without changing or changing the mass of the reinforcement 120 , so that the reinforcement 120 and the elastic element 110 provides the system with a change in stiffness Kt 1 , which further causes the mass Mt 1 - spring Kt 1 - damping Rt 1 system to change the resonant frequency of the flipping motion, thereby causing the third resonance position of the vibration component 100 to change, and at the same time, it can be controlled
  • the 3dB bandwidth of the third resonance peak of the vibration component 100 can be effectively increased by increasing the angle ⁇ (or ⁇ i ) of the strip structure 124 .
  • a larger included angle ⁇ (or ⁇ i ) of the strip structure 124 can be designed.
  • the included angle ⁇ of the strip structure 124 may range from 0 to 150°.
  • the included angle ⁇ of the strip structure 124 may range from 0 to 120°.
  • the included angle ⁇ of the strip structure 124 may range from 0 to 90°.
  • the included angle ⁇ of the strip structure 124 may range from 0 to 80°.
  • the included angle ⁇ of the strip structure 124 may range from 0° to 60°.
  • the included angle ⁇ i of the strip structure 124 may range from 0 to 90°. In some embodiments, the included angle ⁇ i of the strip structure 124 may range from 0 to 80°. In some embodiments, the included angle ⁇ i of the strip structure 124 may range from 0 to 70°. In some embodiments, the included angle ⁇ i of the strip structure 124 may range from 0 to 60°. In some embodiments, the included angle ⁇ i of the strip structure 124 may range from 0 to 45°.
  • the included angle ⁇ of the strip structure 124 may range from 0 to 90°. In some embodiments, the included angle ⁇ of the strip structure 124 may range from 0 to 80°. In some embodiments, the included angle ⁇ of the strip structure 124 may range from 0 to 70°. In some embodiments, the included angle ⁇ of the strip structure 124 may range from 0 to 60°. In some embodiments, the included angle ⁇ of the strip structure 124 may range from 0 to 45°.
  • the included angle ⁇ i of the strip structure 124 may range from 0 to 60°. In some embodiments, the included angle ⁇ i of the strip structure 124 may range from 0 to 80°. In some embodiments, the included angle ⁇ i of the strip structure 124 may range from 0 to 90°. In some embodiments, the included angle ⁇ i of the strip structure 124 may range from 0 to 120°. In some embodiments, the included angle ⁇ i of the strip structure 124 may range from 0 to 150°.
  • the relationship between ⁇ and ⁇ i is defined as:
  • a larger included angle ⁇ of the strip structure 124 can be designed.
  • the included angle ⁇ of the strip structure 124 may range from -90° to 150°.
  • the included angle ⁇ of the strip structure 124 may range from -45° to 90°.
  • the included angle ⁇ of the strip structure 124 may range from 0° to 60°.
  • a smaller included angle ⁇ of the bar-shaped structure 124 can be designed.
  • the range of the included angle ⁇ of the bar-shaped structure 124 can be -150°. to 90°.
  • the included angle ⁇ of the strip structure 124 may range from -90° to 45°.
  • the included angle ⁇ of the strip structure 124 may range from -60° to 0°.
  • the area method can be used for design, and the mass of the reinforcement 120 can be unchanged or changed at the same time.
  • Changing the stiffness of the reinforcement 120 causes the stiffness Kt 1 provided by the reinforcement 120 and the elastic element 110 to the system to change, further causing the mass Mt 1 -spring Kt 1 -damping Rt 1 system to change the resonant frequency of the flipping motion, thereby causing
  • the third resonance position of the vibration component 100 changes; further, the 3dB bandwidth of the third resonance peak of the vibration component 100 can also be controlled.
  • Figure 16F is a schematic diagram of the frequency response curve of a vibration component according to other embodiments of this specification.
  • the vibration component By structurally designing the vibration component, the second resonance peak 220 and the third resonance peak 230 of the vibration component can be merged, so that the vibration component The frequency response curve only shows two resonance peaks.
  • Figure 16F shows the frequency response curves of the vibration component when the included angle ⁇ of the strip structure 124 is 20°, 10° and 1° respectively. As shown in Figure 16F, as the included angle ⁇ increases, the vibration The 3dB bandwidth of the mid-to-high frequency resonant peak of the component (eg, the combined resonant peak of the second resonant peak 220 and the third resonant peak 230 ) gradually increases.
  • the 3dB bandwidth of the mid-to-high frequency resonance peak of the vibration component can be adjusted.
  • the 3dB bandwidth of at least one mid-to-high frequency resonance peak of the vibration component can be made not less than 1000 Hz.
  • FIGS. 17A and 17B are schematic structural views of reinforcements with irregular strip structures according to some embodiments of this specification.
  • a circle with a radius R is defined by the maximum profile of the reinforcement 120, and the radius R of the circle defined by the maximum profile is 1/2 defines the radius as R/2, defines the horizontal projection area of the reinforcement 120 within the range of the radius R/2 as S in , and defines the horizontal projection of the reinforcement 120 within the range between the circle with the radius R/2 and the radius R (i.e. The projection area along the vibration direction of the vibrating component is S out .
  • the physical quantity ⁇ is defined as the ratio of the horizontal projected area of the reinforcement 120, S out , to the horizontal projected area of the reinforcement 120, S in :
  • the mass distribution of the reinforcing member 120 can be controlled by adjusting the ratio ⁇ of the horizontal projected area of the reinforcing member 120 S out to the horizontal projected area S in of the reinforcing member 120 , thereby achieving the third resonance peak of the vibration component 100 bandwidth control.
  • regular reinforcement 120 structures see FIG. 17B , such as ellipses, rectangles, squares, and other polygonal structures.
  • the maximum outline of the reinforcement 120 is defined by a figure similar to the reinforcement 120 for enveloping, and the center area of the figure is defined as
  • the distance from the reference point to each point on the contour envelope is R (for example, R i ,..., R i+3 ), and all correspond to R/2 (for example, R i /2,..., R i+3 /2 ) point forming area, the horizontal projection area of the reinforcement 120 is S in , and the horizontal projection area of the reinforcement 120 within the range between the distance R/2 and the distance R is S out ; for other irregular reinforcement 120 structures, the maximum outline Envelope with regular graphics of similar structure, and define S in , S out , and the ratio ⁇ in the same manner as above.
  • the ratio ⁇ of the horizontal projected area S out to the horizontal projected area S in may range from 0.3 to 2. In some embodiments, the ratio ⁇ of the horizontal projected area S out to the horizontal projected area S in may range from 0.5 to 1.5.
  • the ratio ⁇ of the horizontal projected area S out to the horizontal projected area S in may range from 0.5 to 1.2; in some embodiments, the ratio ⁇ of the horizontal projected area S out to the horizontal projected area S in The value range of ⁇ may be 0.5-1.3; in some embodiments, the ratio of the horizontal projected area S out to the horizontal projected area S in ⁇ may be in the range 0.5-1.4; in some embodiments, the horizontal projected area is The value range of the ratio ⁇ between S out and the horizontal projected area S in may be 0.3-1.2; in some embodiments, the value range ⁇ of the ratio ⁇ between the horizontal projected area S out and the horizontal projected area S in may be 0.3-1.6; In some embodiments, the ratio ⁇ of the horizontal projected area S out to the horizontal projected area S in may range from 0.5 to 2; in some embodiments, the ratio ⁇ of the horizontal projected area S out to the horizontal projected area S in The value range of ⁇ may be 0.5-2.2; in some embodiments, the ratio of the horizontal projected area S out to the
  • the ratio ⁇ of the horizontal projected area S out to the horizontal projected area S in may range from 1 to 3. In some embodiments, the ratio ⁇ of the horizontal projected area S out to the horizontal projected area S in may range from 1.2 to 2.8. In some embodiments, the ratio ⁇ of the horizontal projected area S out to the horizontal projected area S in may range from 1.4 to 2.6. In some embodiments, the ratio ⁇ of the horizontal projected area S out to the horizontal projected area S in may range from 1.6 to 2.4.
  • the ratio ⁇ of the horizontal projected area S out to the horizontal projected area S in may range from 1.8 to 2.2. In some embodiments, the value range of the ratio ⁇ between the horizontal projected area S out and the horizontal projected area S in may be 1.2-2. In some embodiments, the ratio ⁇ of the horizontal projected area S out to the horizontal projected area S in may range from 1 to 2. In some embodiments, the ratio ⁇ of the horizontal projected area S out to the horizontal projected area S in may range from 2 to 2.8. In some embodiments, the ratio ⁇ of the horizontal projected area S out to the horizontal projected area S in may range from 2 to 2.5.
  • FIG. 17C is a schematic diagram of a frequency response curve of a vibration component according to other embodiments of this specification. As shown in Figure 17C, Figure 17C shows the frequency response curves of the vibrating component when ⁇ values are 1.68 and 1.73, respectively, and the 3dB bandwidth at the third resonance peak 230 of the two frequency response curves is narrow. Moreover, when the value of ⁇ increases from 1.68 to 1.73, the third resonance peak 230 moves to low frequency. Therefore, as the value of ⁇ increases, the frequency corresponding to the third resonance peak 230 decreases. By adjusting the value of ⁇ of the vibration component, the bandwidth and position of the third resonance peak can be effectively adjusted.
  • the area of the hollow area of the reinforcement 120 (corresponding to the suspended area of the central area 112 within the projection range of the reinforcement 120) can be changed by adjusting the number of annular structures 122 (for example, in the range of 1-10).
  • the number of annular structures 122 for example, in the range of 1-10.
  • the relationship between the hollow area area and the thickness of the elastic element 110 area-to-thickness ratio ⁇
  • the relationship between the hollow area areas (hollow-out ratio) between different annular structures 122 of the reinforcement 120 can also be changed.
  • the annular structure 122 may include a first annular structure and a second annular structure with coincident centroids, in which case the radial size of the first annular structure is smaller than the radial size of the second annular structure.
  • the bar-shaped structure 124 may also include at least one first bar-shaped structure and at least one second bar-shaped structure. The at least one first bar-shaped structure is disposed inside the first annular structure and connected with the first annular structure.
  • at least one second strip structure is disposed between the first annular structure and the second annular structure, and is connected to the first annular structure and the second annular structure respectively, so that the reinforcement 120 forms a plurality of different hollow areas.
  • Figures 18A-18C are schematic structural diagrams of vibration components with different numbers of ring structures according to some embodiments of this specification.
  • the ring structure 122 of Figure 18A is a single ring structure, and the ring structure 122 of Figure 18B
  • the ring structure 122 is a double ring structure, and the ring structure 122 in Figure 18C is a three ring structure.
  • the number of annular structures 122 may range from 1 to 10.
  • the number of ring structures 122 may range from 1 to 5.
  • the number of ring structures 122 may range from 1 to 3.
  • the quality of the reinforcement 120 can be adjusted, so that the mass of the reinforcement 120, the mass of the elastic element 110, the equivalent air mass, and the driving end equivalent mass are combined to form a total equivalent mass Mt. changes, so the resonant frequency of the mass Mt-spring Kt-damping Rt system changes, thereby causing the first-order resonant frequency of the vibration component 100 to change.
  • the stiffness of the reinforcement 120 can also be adjusted, so that the reinforcement 120 and the elastic element 110 (especially the area where the central area 112 is covered by the reinforcement 120 ) provide stiffness Kt 1 for the system.
  • the change further causes the mass Mt 1 - spring Kt 1 - damper Rt 1 system to change the resonant frequency of the flipping motion, thereby causing the third resonance position of the vibration component 100 to change.
  • the bar structure 124 can also have different stiffness distributions at different positions extending from the center to the surroundings.
  • the size of the hollow area of the central region 112 can also be adjusted, so that each hollow area has an equivalent mass Mmi , equivalent stiffness Kai and Kai ' , an equivalent The damping Ra i and Ra i ' change, so that the fourth resonance peak position of the vibration component 100 changes.
  • the size of the outermost annular structure 122 can also be adjusted, and the area of the partial hollow area between the area of the central area 112 covered by the reinforcement 120 and the folded ring area 114 can be adjusted. , and this area, the connection area 115, and the ring area 114 can form the equivalent mass Ms, equivalent stiffness Ks, and equivalent damping Rs.
  • the resonant frequency of the mass Ms-spring Ks-damping Rs system is changed, thereby achieving the change of the second resonance peak position of the vibration component 100. adjust.
  • the fourth resonance peak of the vibration component 100 can be located in the range of 10kHz-18kHz, and the ratio of the area Si of each hollow region to the thickness Hi of the diaphragm Hi of each hollow region is the area-thickness ratio ⁇ , and the range is 150mm-700mm; the ratio ⁇ between the hollow area areas S ki and S ji of any two elastic elements 110 ranges from 0.25 to 4; the lateral area ratio ⁇ between the reinforced part of the reinforcing member 120 and the reinforcing member 120 ranges from 0.2 to 0.7.
  • the fourth resonance peak of the vibration component 100 can be located in the range of 10kHz-18kHz, and the ratio of the area Si of each hollow region to the thickness Hi of the diaphragm Hi of each hollow region is the area-thickness ratio ⁇ , and the range is 100mm-1000mm; the ratio ⁇ between the hollow area areas S ki and S ji of any two elastic elements 110 ranges from 0.1 to 10; the lateral area ratio ⁇ between the reinforced part of the reinforcing member 120 and the reinforcing member 120 ranges from 0.1 to 0.8.
  • Figure 19 is a schematic structural diagram of a vibration component with discontinuous inner and outer ring strip structures according to some embodiments of this specification.
  • the annular structure 122 divides the bar-shaped structure into multiple areas along the direction extending from the center of 124 to the surroundings, and the bar-shaped structures 124 in each area can be continuously arranged. It can also be set discontinuously.
  • one or more annular structures 122 of vibration assembly 100 may include at least a first annular structure 1221 .
  • the annular structure 122 may include a first annular structure 1221 and a second annular structure 1222 with coincident centroids, and the radial size of the first annular structure 1221 is smaller than the radial size of the second annular structure 1222 .
  • the bar-shaped structure 124 may include at least one first bar-shaped structure 1241 and at least one second bar-shaped structure 1242, and any first bar-shaped structure 1241 is disposed inside a first ring-shaped structure 1221. position, and is connected to the first ring structure 1221, and any second strip structure 1242 is connected to the outside of the first ring structure 1221 at a second position.
  • a plurality of first strip structures 1241 are connected to a plurality of first positions, and a plurality of second strip structures 1242 are connected to a plurality of second positions.
  • at least one first position is connected to the first annular structure 1221
  • the line connecting the centers does not pass through any second position.
  • a line connecting at least one second position and the center of the first annular structure 1221 does not pass through any first position.
  • the plurality of first positions and the plurality of second positions are different, that is, the first positions, the second positions and the center of the first annular structure 1221 are not collinear, and the first strip structure 1241 and the second
  • the connection positions of the strip structure 1242 on the first ring structure 1221 may be different.
  • the numbers of the first strip structures 1241 and the second strip structures 1242 may be the same or different.
  • the strip structures 124 in the inner and outer areas of the annular structure 122 are arranged in a discontinuous manner, it is possible to realize that the number of the strip structures 124 in the inner and outer areas of the annular structure 122 is different, and the bar structures 124 in the inner and outer areas have different lateral widths.
  • the transverse shapes are different, so that the mass, stiffness and center of mass distribution of the reinforcement 120 can be adjusted within a wide range, as well as the number and area of the hollow areas in the central area 112.
  • the total equivalent mass Mt can be controlled to change, so that the resonant frequency of the mass Mt-spring Kt-damping Rt system changes, thereby causing the first-order resonance of the vibration component 100 Frequency changes.
  • the stiffness of the reinforcement 120 the Mt 1 - spring Kt 1 - damping Rt 1 system can be adjusted to flip the resonant frequency of the motion, thereby changing the third resonant position of the vibration component 100; causing the bar structure 124 to extend from the center to the surroundings
  • the stiffness distribution is different at different positions, achieving a third resonance peak of the vibration component 100 with an adjustable 3dB bandwidth.
  • the position and sensitivity of the fourth resonance peak of the vibration component 100 can be changed.
  • the strip structures 124 in the inner and outer areas of the annular structure 122 are arranged discontinuously, so that the fourth resonance peak of the vibration component 100 is located in the range of 10kHz-18kHz, and the area Si of each hollow area and the thickness of the elastic element 110 of each hollow area are
  • the H i ratio is the area-to-thickness ratio ⁇ in the range of 150mm-700mm.
  • the ratio ⁇ between the hollow area areas S ki and S ji of any two elastic elements 110 ranges from 0.25-4.
  • the lateral area ratio of the reinforced part of the reinforcement 120 to the reinforcement 120 ⁇ is 0.2-0.7.
  • the fourth resonance peak of the vibration component 100 can be located in the range of 10kHz-18kHz by discontinuously disposing the strip structures 124 in the inner and outer regions of the annular structure 122.
  • the area S i of each hollow region and the partial diaphragm thickness of each hollow region The H i ratio is the area to thickness ratio ⁇ in the range of 100mm-1000mm; the ratio ⁇ between the hollow area areas S ki and S ji of any two elastic elements 110 ranges from 0.1 to 10; the lateral area of the reinforced part of the reinforcement 120 and the reinforcement 120 The ratio ⁇ is 0.1-0.8.
  • FIG. 20A is a schematic structural diagram of a vibration assembly with multiple annular structures according to some embodiments of this specification.
  • the mass distribution design of the reinforcement 120 can be achieved by designing multiple annular structures 122 to design the spacing areas of the multiple annular structures 122, and by designing the number of strip structures 124 in different spacing areas. It should be noted that the number of bar-shaped structures 124 designed in the spacing areas of each ring-shaped structure 122 may be different, the shapes may be different, and the positions may not correspond to each other.
  • each annular structure 122 from the center outward can be defined as a first annular structure 1221, a second annular structure 1222, a third annular structure 1223, ... the nth annular structure, the nth annular structure and the nth annular structure.
  • the strip structure 124 in the interval area between -1 ring structures is the nth strip structure (such as the first strip structure 1241, the second strip structure 1242, the third strip structure 1243), and the nth strip structure is defined ( That is, the number of strip structures) connected to the inside of the n-th ring structure is Q n , where n is a natural number.
  • the physical quantity q as the ratio of the number Q i of any i-th strip structure to the number Q j of the j-th strip structure:
  • the ratio q between the number Q i of any i-th strip structure and the number Q j of the j-th strip structure may range from 0.05 to 20. In some embodiments, the ratio q between the number Q i of any i-th strip structure and the number Q j of the j-th strip structure may range from 0.1 to 10. In some embodiments, the ratio q between the number Q i of any i-th strip structure and the number Q j of the j-th strip structure may range from 0.1 to 8. In some embodiments, the ratio q between the number Q i of any i-th strip structure and the number Q j of the j-th strip structure may range from 0.1 to 6.
  • the ratio q between the number Q i of any i-th strip structure and the number Q j of the j-th strip structure may range from 0.2 to 5. In some embodiments, the ratio q between the number Q i of any i-th strip structure and the number Q j of the j-th strip structure may range from 0.3 to 4. In some embodiments, the ratio q between the number Q i of any i-th strip structure and the number Q j of the j-th strip structure may range from 0.5 to 6. In some embodiments, the ratio q between the number Q i of any i-th strip structure and the number Q j of the j-th strip structure may range from 1 to 4.
  • the ratio q between the number Q i of any i-th strip structure and the number Q j of the j-th strip structure may range from 1 to 2. In some embodiments, the ratio q between the number Q i of any i-th strip structure and the number Q j of the j-th strip structure may range from 0.5 to 2.
  • the mass distribution design of the reinforcement 120 is achieved, thereby improving the performance of the reinforcement.
  • changing the stiffness of the reinforcement 120 causes the equivalent stiffness Kt 1 of the reinforcement 120 and the diaphragm to change, further causing the mass Mt 1 - spring Kt 1 - damping Rt 1 system
  • the resonant frequency of the flipping motion changes, causing the position of the third resonant peak of the speaker to change.
  • Figure 20B is a schematic diagram of a frequency response curve of a vibration assembly according to some embodiments of this specification.
  • the shape of the ring structure 122 may include at least one of a circular ring, an elliptical ring, a polygonal ring, and a curved ring.
  • the size and shape of the suspended area 1121 can be controlled by the size and shape of the area of the central area 112 covered by the reinforcement 120 and the size and shape of the reinforcement 120 .
  • the area and shape of the ring region 114 can also be adjusted to adjust the total horizontal projection area of the suspended region 1121 and the ring region 114 (that is, the projection along the vibration direction of the vibration component), and by controlling the suspended area 1121 and the ring region 114
  • the total horizontal projected area of the region 1121 and the ring region 114, the thickness of the elastic element 110, the ring arch height and other data can accurately control the second resonance peak of the vibration component 100 to be located in the required frequency range.
  • the second resonance peak of the vibration component 100 may be located in the range of 3000Hz-7000Hz. In some embodiments, by controlling the area ratio of the suspended area 1121 and the ring area 114, the vibration displacement of the local area of the vibration component 100 in its second resonance peak frequency range can be adjusted, thereby maximizing the vibration component 100 in the second resonance peak frequency range. Output sensitivity at peak position.
  • the second resonance peak of the vibration component 100 can be located in the range of 3000Hz to 7000Hz. .
  • the second resonance peak of the vibration component 100 can be located in the range of 3000Hz to 7000Hz. .
  • the level of the folded ring area 114 and the suspended area 1121 can be achieved.
  • the three-dimensional size of the ring area 114 of the elastic element 110 is changed, thereby changing the stiffness Ka 1 ' of the ring area 114, thereby achieving control of the second resonance peak of the vibration component 100.
  • the ratio ⁇ between S s and the ring arch height ⁇ h may range from 50 mm to 600 mm.
  • the ratio ⁇ between S s and the ring arch height ⁇ h may range from 100 mm to 500 mm. In some embodiments, the ratio ⁇ between S s and the ring arch height ⁇ h may range from 200 mm to 400 mm.
  • the relationship between the size of the suspended area 1121 and the area of the central area 112 allows the reinforcement 120 to achieve a certain bending deformation in this frequency range, thereby realizing the superposition and subtraction of sound pressures in different areas of the elastic element 110.
  • the ratio of the horizontal projected area of the suspended area 1121, S v , to the horizontal projected area of the diaphragm center of the vibration component 100, S c The value range can be 0.05-0.7.
  • the value range can be 0.1-0.5.
  • the value range can be 0.15-0.35.
  • FIGS. 21A-21E are schematic structural diagrams of vibration components with different structures according to some embodiments of this specification.
  • the outer contour of the reinforcement 120 may be a structure with outwardly extending spokes (as shown in FIG. 21A ), or may be a circular annular structure, an elliptical annular structure or a curved annular structure (as shown in FIG.
  • polygons can include triangles, quadrilaterals, pentagons, hexagons (shown in Figure 21C- Figure 21D), heptagons, octagons, nonagons, Decagon etc.
  • the elastic element 110 can also be a polygon, such as a triangle, a quadrilateral (as shown in Figure 21D and Figure 21E), a pentagon, a hexagon, a heptagon, an octagon, a nonagon,
  • the reinforcing member 120 can be designed to have similar or dissimilar structures, thereby controlling the shape of the suspended area 1121 through the shapes of the reinforcing member 120 , the central area 112 , and the ring area 114 , thereby realizing the adjustment of the performance of the vibration component 100.
  • FIG. 22 is a schematic structural diagram of a vibration component with a variable width annular structure according to some embodiments of this specification.
  • the mass of the reinforcement 120 can be effectively adjusted, and the total equivalent mass Mt can be controlled to change, thus forming a mass Mt-spring.
  • the resonant frequency of the Kt-damping Rt system changes, thereby causing the first-order resonant frequency of the vibration component 100 to change.
  • any annular structure 122 by designing local structures with unequal widths at different positions (for example, adjacent positions) of any annular structure 122, the stiffness and center of mass distribution of the reinforcement 120 can be adjusted, thereby adjusting the flipping motion of the Mt1-spring Kt1-damping Rt1 system.
  • the resonant frequency causes the third resonant position of the vibration component 100 to change.
  • the design of the annular structure 122 with unequal widths can also make the bar structure 124 have different stiffness distributions at different positions extending from the center to the surroundings, thereby achieving a third resonance peak of the vibration component 100 with an adjustable 3dB bandwidth.
  • the design of the annular structure 122 with unequal widths can also adjust the number and area of the suspended areas in the central region 112, so that the position and sensitivity of the fourth resonance peak of the vibration component 100 are changed.
  • at least one of the one or more annular structures 122 has a different radial width on both sides of the connection location with any one of the one or more strip structures 124, as shown in FIG. 22 .
  • at least one of the one or more annular structures 122 has different circumferential widths between connection locations with any two of the one or more strip structures 124 .
  • local structures with unequal widths are designed at any position (for example, adjacent positions) of any annular structure 122, so that the fourth resonance peak of the vibration component 100 is located in the range of 15kHz-18kHz, and the area Si of each hollow area is equal to
  • the ratio of the thickness H i of the elastic elements 110 in each hollow area is the area-to-thickness ratio ⁇ in the range of 150mm-700mm.
  • the ratio ⁇ between the areas S ki and S ji of the hollow areas of any two elastic elements 110 ranges from 0.25 to 4.
  • the reinforcement of the reinforcement 120 The lateral area ratio ⁇ between the part and the reinforcement 120 is 0.2-0.7.
  • local structures with unequal widths are designed at any position of any annular structure 122, so that the fourth resonance peak of the vibration component 100 is located in the range of 15kHz-18kHz, and the area S i of each hollow area and the partial diaphragm thickness of each hollow area
  • the Hi ratio is the area-to-thickness ratio ⁇ in the range of 100mm-1000mm; the ratio ⁇ between the hollow area areas S ki and S ji of any two elastic elements 110 ranges from 0.1-10; the lateral area ratio of the reinforced part of the reinforcement 120 to the reinforcement 120 ⁇ is 0.1-0.8.
  • FIG. 23 is a schematic structural diagram of a vibration component with an irregular annular structure according to some embodiments of this specification.
  • the size, position, and shape of the local area of the annular structure 122 can be more flexibly controlled, the mass of the reinforcement 120 can be effectively adjusted, and the total equivalent mass Mt can be controlled to change, thus forming a mass Mt-spring Kt-damping Rt system.
  • the resonant frequency changes, thereby causing the first resonant frequency of the vibration component 100 to change.
  • the Mt1-spring Kt1-damping Rt1 system can be adjusted to flip the resonant frequency of the motion, thereby causing the third resonance peak position of the vibration component 100 to change; causing the bar structure 124 to move from the center Extending to the surroundings, the stiffness distribution is different at different positions to achieve a third resonance peak of the vibration component 100 with an adjustable 3dB bandwidth.
  • the number and area of the suspended areas in the central region 112 can be effectively adjusted, so that the fourth resonance peak position and sensitivity of the vibration component 100 are changed.
  • stress concentration can be effectively avoided, resulting in smaller deformation of the reinforcement 120 .
  • the reinforcement 120 includes a double annular structure including a first annular structure 1221 located on the inner side and a second annular structure 1222 located on the outer side.
  • the shapes of the first annular structure 1221 and the second annular structure 1222 may be different.
  • the first annular structure 1221 may be a curved annular shape
  • the second annular structure 1222 may be a circular annular shape.
  • the fourth resonance peak of the vibration component 100 can be located in the range of 10kHz-18kHz, and the ratio of the area S i of each hollow region to the partial diaphragm thickness H i of each hollow region is the area-thickness ratio ⁇ ranges from 150mm to 700mm, the ratio ⁇ between the areas S ki and S ji of any two diaphragm hollow areas ranges from 0.25 to 4, and the lateral area ratio ⁇ between the reinforcing part of the reinforcing member 120 and the reinforcing member 120 ranges from 0.2 to 0.7.
  • the irregular ring structure 122 is designed so that the fourth resonance peak of the vibration component 100 is located in the range of 15kHz-18kHz, and the ratio of the area S i of each hollow region to the thickness H i of the diaphragm of each hollow region is the area-thickness ratio ⁇
  • the range is 100mm-1000mm; the ratio ⁇ between the hollow area areas S ki and S ji of any two elastic elements 110 ranges from 0.1 to 10; the lateral area ratio ⁇ between the reinforcing part of the reinforcing member 120 and the reinforcing member 120 is 0.1-0.8.
  • FIG. 24A is a schematic structural diagram of a vibration component with a bar-shaped structure having a step structure shown in some embodiments of this specification.
  • FIG. 24B is a schematic structural diagram of a vibration component with a bar-shaped structure having a stepped structure shown in other embodiments of this specification. In some embodiments, referring to FIG.
  • the reinforcement 120 by designing the reinforcement 120 with the bar-shaped structure 124 of a stepped structure, it is possible to ensure that the hollow area of the central area 112 (affecting the fourth resonance peak of the vibration component 100), the suspended area 1121 ( Without changing the second resonant peak (affecting the second resonant peak) of the vibration component 100, the stiffness, mass, and center of mass distribution of the reinforcement 120 are changed, so that the vibration can be improved without changing the second resonant peak and the fourth resonant peak of the vibration component 100.
  • the first resonant peak position, the third resonant peak position and the bandwidth of the component 100 are effectively adjusted, and different frequency response curves can be adjusted according to actual application requirements.
  • the mass distribution of the reinforcement 120 may be unchanged or the mass of the reinforcement 120 may be changed simultaneously according to the actual required mass distribution.
  • the stiffness of the reinforcement 120 causes the stiffness Kt 1 provided by the reinforcement 120 and the elastic element 110 to the system to change, further causing the mass Mt 1 - spring Kt 1 - damping Rt 1 system to change the resonant frequency of the flipping motion, thereby causing vibration
  • the third resonance position of the component 100 changes; further, the 3dB bandwidth of the third resonance peak of the vibration component 100 can be controlled.
  • the strip structure 124 may have a plurality of steps with different thicknesses along the vibration direction of the elastic element 110 , that is, the strip structure 124 has a stepped shape. In some embodiments, at least one of the plurality of strip structures has a stepped shape. In some embodiments, all of the plurality of strip structures have a stepped shape.
  • Figure 24B shows the structure of the reinforcement 120 with the stepped-shaped strip structure 124 and the cross-sectional structure of the DD section.
  • the thickness of the most edge step of the structure of the reinforcement 120 i.e., the first step located on the radial outermost side of the strip structure 124) to be h 1
  • the thickness of the secondary edge step to be h 2 ...
  • the thickness of the center step i.e., the first step located at the radial outermost side of the strip structure 124 .
  • the thickness of the second radially innermost step is h n
  • the physical quantity ⁇ is defined as the ratio of the thickness of any two steps h j and h k (k>j):
  • the physical quantity ⁇ is defined as the thickness of the edge step of the reinforcement 120 structure (i.e., the first step located on the radially outermost side of the strip structure 124) h 1 and the center step (and the second step located on the radially innermost side of the strip structure 124). step) thickness h n ratio:
  • the ratio ⁇ of any two step thicknesses h j and h k ranges from 0.1 to 10. In some embodiments, the ratio ⁇ of any two step thicknesses h j and h k ranges from 0.1 to 8. In some embodiments, the ratio ⁇ of any two step thicknesses h j and h k ranges from 0.2 to 8. In some embodiments, the ratio ⁇ of any two step thicknesses h j and h k ranges from 0.1 to 7. In some embodiments, the ratio ⁇ of any two step thicknesses h j and h k ranges from 0.1 to 6. In some embodiments, the ratio ⁇ of any two step thicknesses h j and h k ranges from 0.2 to 6.
  • the ratio ⁇ of any two step thicknesses h j and h k ranges from 0.2 to 5. In some embodiments, the ratio ⁇ of any two step thicknesses h j and h k ranges from 0.25 to 4.
  • the mass distribution of the reinforcement 120 can be adjusted, thereby changing the stiffness of the reinforcement 120 itself without changing or changing the mass of the reinforcement 120, so that the reinforcement 120,
  • the stiffness Kt 1 provided by the elastic element 110 for the system changes, thereby adjusting the position of the third resonance peak of the vibration component 100 and controlling the 3dB bandwidth of the third resonance peak of the vibration component 100 .
  • Figure 24C is a frequency response curve of a vibration component according to other embodiments of this specification.
  • the second resonance peak 220 and the third resonance peak 230 of the vibration component can be merged, so that the vibration component The frequency response curve only shows two resonance peaks.
  • the 3dB bandwidth at the resonance peak is also different, and as the value of ⁇ becomes smaller, the resonance of the mid-to-high frequency resonance peak of the vibration component (such as the resonance peak after the second resonance peak 220 and the third resonance peak 230 are combined) As the frequency gradually increases, the 3dB bandwidth gradually increases. Therefore, by adjusting the value of ⁇ , the frequency position and 3dB bandwidth of the mid-to-high frequency resonance peak of the vibrating component can be adjusted.
  • the ratio ⁇ of any two step thicknesses h j and h k is in the range of 0.25-4, which can make the mid-to-high frequency resonance peak of the vibration component located in the range of 3000Hz-12000Hz, and the resonance peak has a large 3dB bandwidth.
  • the ratio ⁇ of the thickness of the outermost edge step of the structure of the reinforcement member 120 is h 1 to the thickness of the center step hn and is in the range of 0.1-1. In some embodiments, the ratio ⁇ of the edgemost step thickness h 1 to the center step thickness h n of the structure of the reinforcement 120 ranges from 0.2 to 0.8. In some embodiments, the ratio ⁇ of the thickness of the most edge step of the structure of the reinforcement member 120 is h 1 to the thickness of the center step is h n , ranging from 0.2 to 0.6. In some embodiments, the ratio ⁇ of the edgemost step thickness h 1 to the center step thickness h n of the structure of the reinforcement 120 ranges from 0.2 to 0.4.
  • the ratio ⁇ of the thickness of the outermost edge step of the structure of the reinforcing member 120 is h 1 to the thickness of the central step is h n , ranging from 1 to 10.
  • the ratio ⁇ of the edgemost step thickness h 1 to the center step thickness h n of the structure of the reinforcement 120 ranges from 1.2 to 6.
  • the ratio ⁇ of the thickness of the outermost edge step of the structure of the reinforcement member 120 is h 1 to the thickness of the center step hn and ranges from 2 to 6.
  • the ratio ⁇ of the thickness of the outermost edge step of the structure of the reinforcement member 120 is h 1 to the thickness of the center step hn and ranges from 3 to 6. In some embodiments, the ratio ⁇ of the thickness of the outermost edge step of the structure of the reinforcement member 120 is h 1 to the thickness of the center step is h n , and the value range is 4-6. In some embodiments, the ratio ⁇ of the thickness of the outermost edge step of the structure of the stiffener 120 is h 1 to the thickness of the center step of h n , and the value range is 5-6.
  • FIGS. 25A-25C are schematic structural views of vibration assemblies of different shapes of reinforcements according to some embodiments of this specification.
  • the reinforcing member 120 in Figure 25A is rectangular in shape, the ring structure 122 is a single ring rectangular structure, and the strip structure 124 is a trapezoidal structure;
  • the reinforcing member 120 in Figure 21B is rectangular in shape, and the ring structure 122 is a double ring rectangular structure.
  • the strip structure 124 is a trapezoidal structure;
  • the reinforcing member 120 in FIG. 21C is hexagonal, the ring structure 122 is a single-ring hexagonal structure, and the strip structure 124 is a trapezoidal structure.
  • the shape of the reinforcement 120 of the vibration assembly 100 may match the shape of the elastic element 110 .
  • the elastic element 110 can also have various structures, such as circular, square, polygonal, etc.
  • the shape of the corresponding reinforcing member 120 can also be designed into different shapes, including but not limited to circles, squares (eg, rectangles, squares), triangles, hexagons, octagons, other polygons, ovals, and other irregular shapes. Structure.
  • Different shapes of reinforcements 120 and different shapes of elastic elements 110 can be flexibly designed to change the mass and stiffness of the reinforcement 120 , the mass and stiffness of the vibration component 100 , etc., thereby changing the resonant frequency of the vibration component 100 .
  • the shape of the reinforcing member 120 and the shape of the elastic element 110 can include a variety of different shapes.
  • different widths and widths can be designed for its lateral direction.
  • the annular structure 122 can also be designed with different shapes, numbers, and sizes.
  • the annular structure 122 can be designed as a whole annular structure or a partial annular structure 122; different annular structures 122 will be bar-shaped.
  • the structure 124 is divided into different areas. In the different areas, the strip structures 124 in different areas from the center to the surrounding areas may be continuous or staggered, and the number may be equal or unequal.
  • the annular structure 122 can also be designed as a circle, a square (eg, a rectangle, a square), a triangle, a hexagon, an octagon, other polygons, an ellipse, and other irregular structures.
  • the vibration component 100 including different shapes of reinforcements 120 can be designed so that the fourth resonance peak of the vibration component 100 is located in the range of 10kHz-18kHz; the area Si of each hollow area and the thickness of the elastic element 110 of each hollow area
  • the Hi ratio is the area-to-thickness ratio ⁇ , which ranges from 150mm to 700mm; the ratio ⁇ between the suspended area areas S ki and S ji of any two elastic elements 110 ranges from 0.25 to 4; the lateral area ratio ⁇ between the hollow area area and the reinforcement 120 is 0.2-0.7.
  • the vibration component 100 including different shapes of reinforcements 120 can be designed so that the fourth resonance peak of the vibration component 100 is located in the range of 10kHz-18kHz; the area Si of each hollow area and the thickness of the elastic element 110 of each hollow area
  • the Hi ratio is the area-to-thickness ratio ⁇ , which ranges from 100mm to 1000mm; the ratio ⁇ between the suspended area areas S ki and S ji of any two elastic elements 110 ranges from 0.1 to 10; the lateral area ratio ⁇ between the hollow area area and the reinforcement 120 is 0.1-0.8.
  • FIGS. 26A-26D are schematic structural diagrams of the vibration assembly 100 including a local mass structure according to some embodiments of this specification.
  • Figure 26A shows a local mass structure 126 with double elastic connections
  • Figure 26B shows a local mass structure 126 with four elastic connections
  • Figure 26C shows an S-shaped local mass structure 126 with four elastic connections
  • Figure 26D shows S-shaped irregular local mass structure 126 with four elastic connections.
  • the local mass structure 126 can be designed in the suspended area of the central area 112 to flexibly adjust the equivalent mass Mmi, equivalent stiffness Kai and Kai ' , and equivalent damping Ra i of each hollow area. and Ra i ', so that the fourth resonance peak of the vibration component 100 is effectively adjusted.
  • the mass and stiffness of the reinforcement 120 can also be adjusted within a wide range, thereby adjusting the first resonance peak and the third resonance peak of the vibration component 100.
  • the local mass structure 126 can be circumferentially connected to the adjacent strip structure 124 through a dual elastic structure (as shown in Figure 26A), or can be circumferentially connected to the adjacent annular structure 122 through a dual elastic structure. .
  • each local mass structure 126 may not be connected to either the strip structure 124 or the annular structure 122 , but only be connected to the elastic element 110 .
  • the partial mass structure 126 may also be partially connected to the elastic element 110 and another part to the annular structure 122 and/or the strip structure 124 .
  • the local mass structure 126 can also be connected to the adjacent strip structure 124 and the ring structure 122 simultaneously through four elastic structures (as shown in Figure 26B).
  • the planar shape of the elastic structure can be a regular shape (as shown in Figure 26A and Figure 26B) or an irregular shape (as shown in Figure 26C).
  • the local mass structure 126 can be a regular shape (as shown in Figures 26A-26C) or any irregular shape (as shown in Figure 26D).
  • the fourth resonance peak of the vibration component 100 can be located in the range of 10 kHz to 18 kHz; each hollow
  • the ratio of the area Si to the thickness Hi of the elastic elements 110 in each hollow area is the area-to-thickness ratio ⁇ , which ranges from 150 mm to 700 mm; the ratio ⁇ between the suspended area areas S ki and S ji of any two elastic elements 110 ranges from 0.25 to 0.25. 4;
  • the ratio ⁇ of the lateral area of the hollow area to the reinforcement 120 is 0.2-0.7.
  • the fourth resonance peak of the vibration component 100 can be located in the range of 10 kHz to 18 kHz; each hollow
  • the ratio of the area Si to the thickness Hi of the elastic elements 110 in each hollow area is the area-to-thickness ratio ⁇ , which ranges from 100 mm to 1000 mm; the ratio ⁇ between the suspended area areas S ki and S ji of any two elastic elements 110 ranges from 0.1 to 0.1. 10;
  • the ratio ⁇ of the lateral area of the hollow area to the reinforcement 120 is 0.1-0.8.
  • Figure 26E is a schematic cross-sectional structural diagram of a reinforcement shown in some embodiments of this specification.
  • the reinforcement 120 may include a central connection part 123 , a reinforcement part 125 and a hollow part 127 .
  • the hollow portion 127 can be obtained by carving out part of the material on the reinforcing member 120 , and the portion of the reinforcing member 120 that is not cut out constitutes the reinforcing portion 125 .
  • the hollow portion 127 may be configured in a circular shape. In some embodiments, the hollow portion 127 may also be configured in other shapes.
  • the central connecting portion 123 and the reinforcing portion 125 have different thicknesses along the vibration direction of the elastic element 110 .
  • the thickness of the central connecting 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 .
  • Embodiments of this specification also provide a speaker.
  • the speaker has the vibration component provided by the embodiment of this specification.
  • the vibration component for example, elastic elements, reinforcements
  • the speaker can be made within the audible range of the human ear. It has multiple resonant peaks within the frequency band (e.g., 20kHz-20kHz), thereby improving the frequency band and sensitivity of the speaker, and increasing the sound pressure level output by the speaker.
  • Figure 27 is an exemplary structural diagram of a speaker according to some embodiments of the present specification.
  • the speaker 2700 may include a housing 2730, a driving assembly 2720, and the vibration assembly 2710 described above.
  • the driving component 2720 can generate vibration based on the electrical signal, and the vibration component 2710 can receive the vibration of the driving component 2720 and generate vibration.
  • the housing 2730 forms a cavity, and the driving component 2720 and the vibration component 2710 are disposed in the cavity.
  • the structure of the vibration component 2710 may be the same as any vibration component in the embodiments of this specification.
  • the vibration component 2710 mainly includes an elastic element 2711 and a reinforcement 2712.
  • the elastic element 2711 mainly includes a central area 2711A, a folding area 2711B provided on the periphery of the central area 2711A, and a fixed area 2711C provided on the periphery of the turning area 2711B.
  • the elastic element 2711 is configured to vibrate in a direction perpendicular to the central area 2711A.
  • Reinforcement member 2712 is connected to central area 2711A.
  • the reinforcement 2712 includes a reinforcement part and a plurality of hollow parts. The vibration of the reinforcement 2712 and the elastic element 2711 generates at least two resonance peaks within the audible range of the human ear (20Hz-20kHz).
  • the driving component 2720 may be an acoustic device with an energy conversion function.
  • the driving component 2720 can be electrically connected to other components of the speaker 2700 (e.g., a signal processor) to receive electrical signals and convert the electrical signals into mechanical vibration signals, which can be transmitted to the vibration component 2710. This causes the vibration component 2710 to vibrate, thereby pushing the air in the cavity to vibrate and generate sound.
  • the driving assembly 2720 may include a driving unit 2722 and a vibration transmission unit 2724.
  • the driving unit 2722 may be electrically connected to other components of the speaker 2700 (eg, signal processor) to receive electrical signals and convert the electrical signals into mechanical vibration signals.
  • the vibration transmission unit 2724 is connected between the driving unit 2722 and the vibration component 2710, and is used to transmit the vibration signal generated by the driving unit 2722 to the vibration component 2710.
  • the drive unit 2722 may include, but is not limited to, a moving coil acoustic driver, a moving iron acoustic driver, an electrostatic acoustic driver, or a piezoelectric acoustic driver.
  • the dynamic acoustic driver may include a magnetic component that generates a magnetic field and a coil disposed in the magnetic field. When the coil is energized, it may generate vibration in the magnetic field to convert electrical energy into mechanical energy.
  • the moving iron acoustic driver may include a coil that generates an alternating magnetic field and a ferromagnetic component disposed in the alternating magnetic field.
  • the ferromagnetic component vibrates under the action of the alternating magnetic field to convert electrical energy into mechanical energy.
  • the electrostatic acoustic driver can drive the diaphragm to vibrate through an electrostatic field disposed inside it, thereby converting electrical energy into mechanical energy.
  • the piezoelectric acoustic driver can convert electrical energy into mechanical energy under the action of the electrostrictive effect through the piezoelectric material disposed inside it.
  • the driving unit 2722 may be a piezoelectric acoustic driver as shown in Figure 48.
  • the piezoelectric acoustic driver is composed of a plurality of piezoelectric beams 27221, and elastic connectors 27222 are used between the plurality of piezoelectric beams 27221. Connect to each other.
  • multiple piezoelectric beams 27221 and/or elastic connectors should cover the plane surrounded by the fixed ends as much as possible, that is, as many as possible.
  • the gap width 27223 between each piezoelectric beam and the elastic connector should be as small as possible, such as not greater than 25 ⁇ m.
  • the driving unit 2722 and the vibration transmission unit 2724 may be located on the same side of the vibration direction of the vibration component.
  • one end of the vibration transmission unit 2724 along the vibration direction of the central region 2711A is connected to the driving unit 2722, and the other end of the vibration transmission unit 2724 away from the driving unit 2722 may be connected to the central region 2711A of the vibration assembly 2710.
  • the reinforcement 2712 may include a central connection 27121 covering the center of the central region 2711A.
  • the other end of the vibration transmission unit 2724 away from the driving unit 2722 may be directly connected to the central connection part 27121, that is, the vibration transmission unit 2724 is connected to the central area 2711A through the central connection part 27121.
  • the other end of the vibration transmission unit 2724 away from the driving unit 2722 may be indirectly connected to the central connection part 27121, that is, the vibration transmission unit 2724 is directly connected to the central area 2711A, and connected to the central connection part 27121 through the central area 2711A.
  • the size of the vibration transmission unit 2724 may be the same or substantially the same as the size of the central connection portion 27121 (eg, the size difference is within 10%).
  • the center of one end of the vibration transmission unit 2724 connected to the central area 2711A coincides or substantially coincides with the projection of the center of the central area 2711A along the vibration direction of the elastic element 2711.
  • the elastic element can be improved 2711 vibration uniformity and stability
  • the third resonance peak output by the speaker 2700 can be controlled within the frequency range (for example, 5000Hz-12000Hz) described in the embodiment of this specification.
  • substantially coinciding means that the distance between the center of one end of the vibration transmission unit 2724 connected to the central area 2711A and the center of the central area 2711A does not exceed 5% of the diameter of the central area 2711A.
  • the vibration transmission unit 2724 when the vibration transmission unit 2724 is connected to the central area 2711A through the central connection portion of the reinforcement 2712, since the size of the vibration transfer unit 2724 matches the size of the central connection portion (eg, has the same size), The center of one end of the vibration transmission unit 2724 connected to the central connection part coincides or substantially overlaps with the center of the central connection part 27121. At this time, the center of the central connection part may also be the projection of the center of the central area 2711A along the vibration direction of the elastic element 2711. Coincident or approximately coincident.
  • the central connecting portion of the reinforcing member 2712 please refer to the relevant description of the central connecting portion 123 of the reinforcing member 120.
  • the vibration component 2710 can receive the force and displacement transmitted by the vibration transmission unit 2724 to push the air to move and generate sound.
  • vibration assembly 2710 may have the same structure as vibration assembly 100 .
  • the ring area 2711B can be designed with a pattern of a characteristic shape, thereby destroying the vibration shape of the ring area 2711B of the elastic element 2711 in the corresponding frequency range, and avoiding the occurrence of sound cancellation caused by the partial division vibration of the elastic element 2711. , so that the vibration component 2710 has a flatter sound pressure level curve. At the same time, the local stiffness of the elastic element 2711 is increased through the pattern design.
  • the mode shape of the vibration assembly 2710 can be adjusted.
  • reinforcement 2712 includes one or more ring structures and one or more strip structures, each of the one or more strip structures being connected to at least one of the one or more ring structures; wherein , at least one of the one or more strip structures extends toward the center of the central region 2711A.
  • the area not covered by one or more annular structures and one or more strip structures constitutes a hollow portion.
  • the local stiffness of the central area 2711A of the elastic element 2711 can be controllably adjusted, thereby utilizing the elasticity of the elastic element 2711 of the vibration assembly 2710.
  • the divided mode shapes of each hollow area in the central area 2711A enable controllable adjustment of the resonance peak output by the vibration component 2710, so that the vibration component 2710 has a relatively flat sound pressure level curve.
  • the annular structure and the strip structure cooperate with each other so that the reinforcement 2712 has an appropriate proportion of reinforcement parts and hollow parts (ie, hollow parts), reducing the mass of the reinforcement 2712 and improving the overall vibration assembly 2710 sensitivity.
  • the position and bandwidth of the multiple resonance peaks (for example, the third resonance peak, the fourth resonance peak, etc.) of the vibration component 2710 can be adjusted, Thereby, the vibration output of the vibration component 2710 is controlled.
  • the mass of the reinforcement 2712, the mass of the elastic element 2711, the equivalent air mass, and the equivalent mass of the driving end are combined to form a total equivalent mass Mt, and the equivalent damping of each part forms a total equivalent damping Rt.
  • the elasticity Component 2711 provides stiffness Kt to the system, forming a mass Mt-spring Kt-damping Rt system.
  • a resonance peak appears in the frequency response curve of the vibration component 2710, that is, the vibration component The first resonance peak of 2710.
  • the frequency range of the first resonance peak includes 180 Hz-3000 Hz.
  • the frequency range of the first resonance peak includes 200 Hz-3000 Hz. In some embodiments, the frequency range of the first resonance peak includes 200 Hz-2500 Hz. In some embodiments, the frequency range of the first resonance peak includes 200 Hz-2000 Hz. In some embodiments, the frequency range of the first resonance peak includes 200 Hz-1000 Hz.
  • the suspended area 2711E between the ring area 2711B, the connection area 2711D, and the central area 2711A where the reinforcement 2712 is provided and the ring area 2711B form an equivalent mass Ms, an equivalent stiffness Ks, and an equivalent damping. Rs, forming a mass Ms-spring Ks-damping Rs system.
  • the excitation frequency of the driving component 2720 is close to the resonant frequency of the system, a resonance peak appears in the frequency response curve of the vibration component 2710, which is the second resonance peak of the vibration component 2710. .
  • the frequency range of the second resonance peak of the vibration component 2710 may include 3000 Hz-7000 Hz.
  • the frequency range of the second resonance peak of the vibration component 2710 may include 3000 Hz-6000 Hz. In some embodiments, the frequency range of the second resonance peak of the vibration component 2710 may include 4000 Hz-6000 Hz. In some embodiments, by setting the parameters of the elastic element 2711 (for example, the parameters of the ring area 2711B and the suspended area 2711E), the second resonance peak of the vibration component 2710 can be located in the above frequency range.
  • the effective mass combination forms the total equivalent mass Mt1
  • the equivalent damping of each part forms the total equivalent damping Rt1.
  • the reinforcement 2712 and the elastic element 2711 provide the stiffness Kt1 for the system, forming a mass Mt1-spring Kt1-damping Rt1 system.
  • the frequency range of the third resonance peak may include 5000 Hz-12000 Hz. In some embodiments, the frequency range of the third resonance peak may include 6000 Hz-12000 Hz. In some embodiments, the frequency range of the third resonance peak may include 6000 Hz-10000 Hz.
  • the reinforcement 2712 has no less than one hollow area corresponding to the central area 2711A, and each hollow area with different resonant frequencies vibrates, so that there is no less than 1 high value on the frequency response curve of the vibration component 2710. frequency resonance peak.
  • the resonant frequencies of each hollow area can be made equal or close (for example, the difference is less than 4000 Hz), so that there is an output sound pressure on the frequency response curve of the vibration component 2710
  • the higher frequency resonance peak is the fourth resonance peak of the vibration component 2710 .
  • the frequency range of the fourth resonance peak may include 8000 Hz-20000 Hz.
  • the frequency range of the fourth resonance peak may include 10000 Hz-18000 Hz. In some embodiments, the frequency range of the fourth resonance peak may include 12000 Hz-18000 Hz. In some embodiments, the frequency range of the fourth resonance peak may include 15000 Hz-18000 Hz. In other embodiments, the frequency range of the fourth resonance peak may also be greater than 20,000 Hz. In other embodiments, the resonant frequencies of each hollow area are different, and the vibration phases of different hollow areas in different frequency bands are different in the high frequency range (such as 8000Hz-20000Hz), forming a sound superposition and cancellation effect, which can prevent the vibration component 2710 from outputting The fourth resonance peak.
  • the speaker 2700 can exhibit 2, 3, or 4 resonance peaks within the audible range of the human ear (eg, 20 Hz-20 kHz).
  • the structure and size of the vibration component 2710 including the overall size of the reinforcement 2712, the number and size of the strip structures, the arrangement position of the strip structures, the area of the suspended area 2711E, and the structure of the ring area 2711B ( For example, the width of the ring, arch height, arch shape, pattern, etc.) and the area of the connection area 2711D can be used to design the frequency difference between the second resonance peak and the third resonance peak of the vibration component 2710.
  • the frequency difference between the second resonance peak and the third resonance peak of the vibration component 2710 is less than 2000 Hz, the second resonance peak and the third resonance peak tend to merge, that is, the second resonance peak and the third resonance peak appear.
  • the frequency range of the fourth resonance peak may be greater than 20,000 Hz, that is, there is no fourth resonance peak within the audible range of the human ear. In some embodiments, when the frequency difference between the second resonance peak and the third resonance peak is less than 2000 Hz and there is no fourth resonance peak within the audible range of the human ear, when the vibration component 2710 vibrates, there is a frequency difference within the audible range of the human ear.
  • the 3dB bandwidth of at least one of the resonant peaks is not less than 1000Hz.
  • the 3dB bandwidth refers to the width of the corresponding frequency band (such as the abscissa in Figure 7D) when the sound pressure level amplitude corresponding to the resonance peak (such as the ordinate in Figure 7D) is reduced by 3dB.
  • the 3dB bandwidth of at least one resonance peak within the audible range of the human ear is no less than 1500 Hz.
  • the 3dB bandwidth of at least one resonance peak within the audible range of the human ear is no less than 1000 Hz. In some embodiments, when the vibrating component 2710 vibrates, the 3dB bandwidth of at least one resonance peak within the audible range of the human ear is no less than 500 Hz.
  • the vibration component 2710 can make the required high-order mode appear in the audible sound range (20Hz-20000Hz), and appear on the frequency response curve of the vibration component 2710
  • the above-mentioned first resonant peak, second resonant peak, third resonant peak and fourth resonant peak, that is, the number of resonant peaks of the frequency response curve of the vibrating component 2710 in the frequency range of 20 Hz to 20000 Hz is 4.
  • the vibration component 2710 can have only three resonance peaks within the audible sound range of the human ear (20 Hz-20000 Hz). For example, when the frequency difference between the second resonance peak and the third resonance peak of the vibration component 2710 is less than 2000 Hz, on the frequency response sound pressure level curve of the vibration component 2710, the second resonance peak and the third resonance peak appear as one resonance peak, which is the same as the first resonance peak.
  • the first resonance peak and the fourth resonance peak together constitute three resonance peaks of the vibration component 2710 within the audible sound range of the human ear (20Hz-20000Hz).
  • the reinforcement 2712 has no less than one suspended area corresponding to the central area 2711A.
  • the resonant frequency of each hollow area is higher than the audible sound range, or the resonant frequency of each hollow area is different and in the high frequency range (10000Hz -18000Hz)
  • the vibration phases of different suspended areas in different frequency ranges are different, resulting in the effect of sound superposition and cancellation, a high-frequency roll-off effect can be obtained.
  • the fourth resonance peak is not reflected in the frequency response curve of the vibration component 2710 sound pressure level.
  • the first resonance peak, the second resonance peak and the third resonance peak constitute three resonance peaks of the vibration component 2710 within the audible sound range of the human ear (20 Hz-20000 Hz).
  • the structure of the stiffener 2712 or the elastic element 2711 by designing the structure of the stiffener 2712 or the elastic element 2711, not only the frequencies of the multiple resonant peaks, but also the 3dB bandwidth of the multiple resonant peaks (eg, the third resonant peak) and the Q of the speaker can be adjusted. value.
  • the angle ⁇ between two sides of the projected shape of the bar structure along the vibration direction by designing the angle ⁇ between two sides of the projected shape of the bar structure along the vibration direction, the 3dB bandwidth of the third resonance peak output by the speaker 2700 and the Q value of the speaker 2700 can be adjusted.
  • the angle ⁇ of the strip structure when the speaker 2700 is required to exhibit low-Q value and wide-bandwidth frequency response characteristics, the angle ⁇ of the strip structure may have a larger value.
  • the included angle ⁇ of the strip structure may range from -90° to 150°, so that the speaker 2700 has a lower Q value, and the 3dB bandwidth of the third resonant peak output by the speaker 2700 is not less than 1000 Hz.
  • the angle ⁇ of the strip structure may range from -0° to 60°, so that the speaker 2700 has a lower Q value, and the 3dB bandwidth of the third resonant peak output by the speaker 2700 is not less than 1000 Hz.
  • the included angle ⁇ of the strip structure may range from -150° to 90°, so that the speaker 2700 has a higher Q value, and the 3dB bandwidth of the third resonant peak output by the speaker 2700 is no greater than 1000 Hz. In some embodiments, the included angle ⁇ of the strip structure may range from -60° to 0°, so that the speaker 2700 has a higher Q value, and the 3dB bandwidth of the third resonant peak output by the speaker 2700 is no greater than 1000 Hz.
  • the area ratio between the inner and outer sides of the half-contour of the projected shape of the reinforcement 2712 along the vibration direction of the elastic element 2711 to be ⁇ , the 3dB bandwidth of the third resonant peak output by the speaker 2700 and the speaker 2700 can be adjusted Q value.
  • the speaker 2700 is required to exhibit low-Q value and wide-bandwidth frequency response characteristics, a larger mass can be designed to be concentrated in the center area of the reinforcement 2712 .
  • the area ratio ⁇ of the inside and outside of the half-profile of the projected shape of the reinforcement 2712 along the vibration direction of the elastic element 2711 may range from 0.3 to 2, so that the speaker 2700 has a lower Q value.
  • the 3dB bandwidth of the third resonance peak output by the speaker 2700 is not less than 1000Hz.
  • the area ratio ⁇ of the inside and outside of the half-profile of the projected shape of the reinforcement 2712 along the vibration direction of the elastic element 2711 may range from 0.5 to 1.2, so that the speaker 2700 has a lower Q value.
  • the 3dB bandwidth of the third resonance peak output by the speaker 2700 is not less than 1000Hz.
  • the area ratio ⁇ of the inside and outside of the half-profile of the projected shape of the reinforcement 2712 along the vibration direction of the elastic element 2711 may range from 1 to 3, so that the speaker 2700 has a higher Q value. And the 3dB bandwidth of the third resonance peak output by the speaker 2700 is not greater than 1000Hz. In some embodiments, the area ratio ⁇ of the inside and outside of the half-profile of the projected shape of the reinforcement 2712 along the vibration direction of the elastic element 2711 may range from 1.2 to 2.8, so that the speaker 2700 has a higher Q, and The 3dB bandwidth of the third resonant peak output by the speaker 2700 is not greater than 1000Hz.
  • At least one of the one or more strip-shaped structures has a plurality of steps with different thicknesses along the vibration direction of the elastic element 2711.
  • the steps include a first step located at the radially outermost side of the strip-shaped structure and a step located at the radially outermost side of the strip-shaped structure.
  • the thickness ratio ⁇ of the first step and the second step ranges from 0.1 to 1, so that the speaker 2700 has a lower Q value, and the 3dB bandwidth of the third resonant peak output by the speaker 2700 is not less than 1000Hz. In some embodiments, the thickness ratio ⁇ of the first step and the second step ranges from 0.2 to 0.8, so that the speaker 2700 has a lower Q value, and the 3dB bandwidth of the third resonant peak output by the speaker 2700 is not less than 1000Hz.
  • a larger mass can be designed to be concentrated in the edge area of the reinforcement 2712 .
  • the thickness ratio ⁇ of the first step and the second step ranges from 1 to 10, so that the speaker 2700 has a higher Q value, and the 3dB bandwidth of the third resonant peak output by the speaker 2700 is not greater than 1000Hz. In some embodiments, the thickness ratio ⁇ of the first step and the second step ranges from 1.2 to 6, so that the speaker 2700 has a higher Q value, and the 3dB bandwidth of the third resonant peak output by the speaker 2700 is not greater than 1000Hz.
  • the housing 2730 may be a regular or irregular three-dimensional structure with a hollow interior (ie, a cavity).
  • the housing 2730 may be a hollow frame structure, including but not limited to a rectangular frame, a circular frame, or a hollow frame structure.
  • Regular shapes such as square boxes, regular polygon boxes, and any irregular shapes.
  • the housing 2730 may be made of metal (eg, stainless steel, copper, etc.), plastic (eg, polyethylene (PE), polypropylene (PP), polyvinyl chloride (PVC), polystyrene (PS) and acrylonitrile-butadiene-styrene copolymer (ABS), etc.), composite materials (such as metal matrix composite materials or non-metal matrix composite materials), etc.
  • the driving assembly 2720 may be located within the acoustic cavity formed by the housing 2730 or at least partially suspended within the acoustic cavity of the housing 2730 .
  • the peripheral side of the elastic element 2711 may be connected to the inner wall of the housing 2730, thereby dividing the cavity formed by the housing 2730 into multiple cavities. Specifically, along the vibration direction of the elastic element 2711, with the elastic element 2711 as a boundary, the inner cavity of the housing 2730 is divided into a front cavity 2731 and a rear cavity 2733 respectively located on both sides 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 driving unit 2722.
  • the back cavity 2733 is located on a side of the elastic element 2711 close to the driving unit 2722, that is, the driving assembly 2720 can be disposed in the back cavity 2733.
  • one or more holes may be opened on the side walls of the housing 2730 corresponding to the front cavity 2731 and the rear cavity 2733.
  • a first hole 2732 is provided on the shell 2730 on the side of the front cavity 2731 away from the elastic element 2711.
  • the front cavity 2731 communicates with the outside world of the speaker 2700 through the first hole 2732; the rear cavity 2733 is away from the elastic element 2711.
  • the housing 2730 is provided with a second hole 2734, and the rear cavity 2733 communicates with the outside world of the speaker 2700 through the second hole 2734.
  • the sound generated by the vibration component 2710 may be radiated toward 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 .
  • a damping net or a dust-proof cloth may be disposed on one or more holes (eg, the second hole 2734).
  • the damping mesh may modulate (eg, reduce) the amplitude of sound waves leaking from the aperture, thereby improving the performance of speaker 2700.
  • the speaker 2700 may further include a support element 2740, which is connected to the housing 2730 and the fixing area 2711C respectively.
  • the fixing area 2711C of the elastic element 2711 of the vibration component 2710 is located at the periphery of the connection area 2711D and is connected around the circumference of the connection area 2711D.
  • the support element 2740 may be located on any surface of the fixed area 2711C along the vibration direction of the central area 2711A, and is connected to the connection area 2711D through the fixed area 2711C.
  • the support element 2740 can be embedded in the inner wall of the housing 2730 and connected with the housing 2730 to support the elastic element 2711.
  • a hole matching the support element 2740 can be provided on the inner wall of the housing 2730, so that the support element 2740 can be placed in the hole to realize the embedding of the support element 2740.
  • the support element 2740 can also be disposed in the cavity formed by the housing 2730.
  • the lower surface (the surface close to the driving unit 2722) or the peripheral surface of the support element 2740 along the vibration direction of the vibration assembly 2710 is in contact with Housing 2730 is connected to support elastic element 2711.
  • the inner wall of the housing 2730 can be configured to have a protruding structure that matches the supporting element 2740, so that the supporting element 2740 can be disposed along the protruding structure.
  • the vibration direction surface is used to realize the connection between the support element 2740 and the housing 2730 . In this arrangement, by disposing the support element 2740 in the cavity formed by the housing 2730, the support element 2740 can be prevented from being scratched and damaged during use of the speaker 2700, thereby preventing damage to the speaker 2700 (especially the vibration component 2710).
  • the support element 2740 can be a rigid structure that is not easily deformed, and only provides support for the elastic element 2711 during the vibration process of the vibration assembly 2710.
  • the support element 2740 in order to further reduce the system stiffness when the vibrating component 2710 vibrates and improve the compliance of the speaker 2700, can be configured as an easily deformable flexible structure to provide the vibrating component 2710 with additional displacement when vibrating.
  • the support element 2740 can deform in response to the vibration signal of the elastic element 2711 to provide the elastic element 2711 with a displacement along its vibration direction, thereby increasing the total displacement generated by the elastic element 2711 in its vibration direction. amount to further improve the low-frequency sensitivity of the vibration component 2710.
  • the material of the supporting element 2740 may include one or more of rigid materials, semiconductor materials, organic polymer materials, glue materials, and the like.
  • rigid materials may include, but are not limited to, metallic materials, alloy materials, and the like.
  • Semiconductor materials may include, but are not limited to, one or more of silicon, silicon dioxide, silicon nitride, silicon carbide, and the like.
  • Organic polymer materials may include, but are not limited to, one or more of polyimide (PI), parylene, polydimethylsiloxane (PDMS), hydrogel, and the like.
  • Glue materials may include, but are not limited to, one or more of gel, silicone, acrylic, polyurethane, rubber, epoxy, hot melt, light curing, etc.
  • the material of the support element 2740 in order to enhance the connection force between the support element 2740 and the elastic element 2711 and improve the reliability between the support element 2740 and the elastic element 2711, the material of the support element 2740 can be silicone adhesive glue, organic Silicone sealing glue, etc.
  • the cross-sectional shape of the support element 2740 on a cross-section parallel to the vibration direction of the enhancement region may be a rectangle, a circle, an ellipse, a pentagon, or other regular and/or irregular geometric shapes.
  • the support element 2740 by providing the support element 2740 with a flexible structure, not only the vibration characteristics of the vibration assembly 2710 can be changed, but also the elastic element 2711 can be prevented from directly contacting the shell 2730, and the stress concentration at the connection end between the elastic element 2711 and the shell 2730 can be reduced (shell The body is generally a rigid body), thereby further protecting the elastic element 2711.
  • Figure 28 is a schematic structural diagram of a speaker according to some embodiments of this specification. It should be noted that since the speaker 2800 shown in Figure 28 has a similar structure to the speaker 2700 shown in Figure 27, the speaker 2800 can be regarded as a modification based on the speaker 2700. Therefore, in this specification, Components in the speaker 2800 and the speaker 2700 that have the same structure or function are numbered the same, and components that are not labeled in FIG. 28 can be found in FIG. 27 .
  • the housing 2730 may include a front cavity plate 2735 , a rear cavity plate 2736 and a side plate 2737 .
  • the front cavity plate 2735 , the rear cavity plate 2736 and the side plates 2737 may enclose a cavity of the housing 2730 .
  • the cavity of the housing 2730 may include a front cavity 2731 on one side of the vibration assembly 2710 and one or more rear cavities 2733 on the other side of the vibration assembly 2710. At least one is surrounded by the driving assembly 2720, the vibration assembly 2710 and the rear cavity plate 2736.
  • the number of back chambers 2733 may be one.
  • the back cavity 2733 may only include the second back cavity 27332.
  • the number of back cavities 2733 may be two.
  • the two back cavities 2733 may be the first back cavity 27331 and the second back cavity 27332 respectively.
  • the number of back cavities 2733 may also be three, four, five, etc.
  • the driving assembly 2720, the vibration assembly 2710, the rear cavity plate 2736, and portions of the side plates 2737 can enclose the second rear cavity 27332.
  • the vibration assembly 2710 can separate the cavity of the housing 2730 into a front cavity 2731 corresponding to the front cavity plate 2735 and a rear cavity 2733 corresponding to the rear cavity plate 2736.
  • the driving assembly 2720 can be disposed in the rear cavity 2733.
  • the driving assembly 2720 is fixedly connected to the rear cavity plate 2736.
  • the back cavity plate 2736 may be a PCB board, a plastic plate, a metal plate, etc.
  • the housing 2730 may have an integrated structure, that is, the front cavity panel 2735, the rear cavity panel 2736, and the side panels 2737 are of an integrated design.
  • the front cavity plate 2735, the rear cavity plate 2736, and the side plates 2737 can be connected to form the housing 2730 by gluing, welding, snapping, etc.
  • the vibration component 2710, the driving component 2720, and the housing 2730 please refer to the description elsewhere in this specification (for example, FIG. 27), and will not be described again here.
  • Figure 29 is a schematic diagram of a speaker and its equivalent model according to some embodiments of this specification.
  • each part of the speaker 2800 can be equivalent to a mass-spring-damping system.
  • the vibrating surface of the drive assembly 2720 may form at least a portion of the sidewall of at least one of the one or more rear cavities 2733 .
  • the driving assembly 2720 can divide the back cavity 2733 into a first back cavity 27331 and a second back cavity 27332.
  • the vibration surface of the driving assembly 2720 facing the first back cavity 27331 and the vibration surface facing the second back cavity 27332 can respectively constitute a third back cavity.
  • the air in the first back cavity 27331 can be equivalent to a mass-spring-damping system with equivalent mass M 2 , equivalent stiffness K 2 and equivalent damping R 2 ;
  • the air in the second back cavity 27332 can be Equivalent to a mass-spring-damping system, with equivalent mass M 1 , equivalent stiffness K 1 and equivalent damping R 1 ;
  • the air in the front cavity 2731 can be equivalent to a mass-spring-damping system, with equivalent Effective mass M 3 , equivalent stiffness K 3 and equivalent damping R 3 ;
  • the vibration component 2710 can be equivalent to a mass-spring-damping system with equivalent mass Mv, equivalent stiffness Kv and equivalent damping Rv;
  • driving component 2720 can be equivalent to a mass-spring-damper system with equivalent mass Md, equivalent stiffness Kd and equivalent damping Rd.
  • the driving unit 2722 in the driving assembly 2720 may include a piezoelectric actuator as shown in FIG. 48 , one of a plurality of piezoelectric beams and elastic connectors of the piezoelectric actuator as described elsewhere in this specification.
  • the width of the gap between them is very small.
  • the air in the second rear chamber 27332 cannot flow quickly to the first rear chamber 27331 through the gap to balance the air pressure on both sides of the driving assembly 2720, so the first rear chamber 27331 and the first rear chamber 27331
  • the two back chambers 27332 are equivalent to being disconnected from each other, and the second back chamber 27332 is equivalent to a closed chamber.
  • FIG. 48 the driving unit 2722 in the driving assembly 2720 may include a piezoelectric actuator as shown in FIG. 48 , one of a plurality of piezoelectric beams and elastic connectors of the piezoelectric actuator as described elsewhere in this specification.
  • the width of the gap between them is very small.
  • the air in the second rear chamber 27332 cannot
  • the driving assembly 2720 may include multiple vibration units, the vibration units may include piezoelectric beams 27221 , and the piezoelectric beams 27221 in the multiple vibration units may be connected through elastic connectors 27222 .
  • the gaps formed between the multiple vibration units may be smaller.
  • the gaps formed between multiple vibration units may be no larger than 25 ⁇ m.
  • the gaps formed between multiple vibration units may be no larger than 20 ⁇ m.
  • the gaps formed between multiple vibration units may be no larger than 15 ⁇ m.
  • the gaps formed between multiple vibration units may be no larger than 10 ⁇ m.
  • the gaps formed between the multiple vibration units may refer to the gaps formed between the piezoelectric beams in the multiple vibration units. In some embodiments, the gaps formed between the multiple vibration units may be the gaps formed between the piezoelectric beams and the elastic connectors 27222 in the multiple vibration units.
  • the vibrating surface of the driving assembly 2720 may have a larger continuous surface area. In some embodiments, no less than 90% of the surface area of the vibrating surface of drive assembly 2720 is continuous. In some embodiments, no less than 95% of the surface area of the vibrating surface of drive assembly 2720 is continuous. In some embodiments, no less than 98% of the surface area of the vibrating surface of drive assembly 2720 is continuous. In some embodiments, the entire surface area of the vibrating surface of drive assembly 2720 is continuous.
  • drive component 2720 may include a piezoelectric membrane. In some embodiments, there may be no gap on the piezoelectric film, and the second back cavity 27332 is completely sealed in this case.
  • the equivalent mass-spring-damping system of the air in the first back cavity 27331 and the second back cavity 27332 can act on the driving assembly 2720 and the vibration assembly 2710. Due to the difference between the first back cavity 27331 and the second back cavity 27332 The volume is small, and the mass and damping of the internal air can be ignored, so that the mass-spring-damping system equivalent to the air in the first back cavity 27331 and the second back cavity 27332 can be equivalent to the air spring system, so the third The mass-spring-damping system equivalent to the air in the first rear chamber 27331 and the second rear chamber 27332 plays a major role in the vibration assembly 2710 and the driving assembly 2720. The stiffness of the air spring plays a major role.
  • an air spring system equivalent to the air in the first back cavity 27331 and the second back cavity 27332 can act on the driving assembly 2720 and the vibration assembly 2710 in the form of additional stiffness. Specifically, since the volumes of the first back cavity 27331 and the second back cavity 27332 are small, the degree of compressibility of the air in the first back cavity 27331 and the second back cavity 27332 is also small, resulting in the first back cavity 27331 and the second back cavity 27332 being compressible.
  • the air in the cavity 27332 adds greater stiffness to the vibration component 2710 and the driving component 2720, and the vibration displacement of the vibration component 2710 and the driving component 2720 is smaller, thereby reducing the output of the driving component 2720 and the vibration component 2710, for example, reducing the driving component 2720
  • the output to the vibration component 2710 and the reduction of the output of the vibration component 2710 to the air are not conducive to improving the sensitivity of the speaker.
  • the sensitivity of the speaker can be improved by adjusting the mass-spring-damping system equivalent to the air in the first back cavity 27331 and the second back cavity 27332 respectively.
  • the air spring system equivalent to the air in the first rear chamber 27331 and the second rear chamber 27332 has a greater impact on the vibration component 2710.
  • the impact on the driving component 2720 will be greater.
  • the vibration displacement of the vibration component 2710 will be reduced compared to the driving force. The reduction in vibration displacement of component 2720 is greater.
  • several through holes can be opened on the rear cavity plate 2736, and one or more rear cavities 2733 can be connected through several through holes, thereby improving the sensitivity of the speaker.
  • "several" may represent one or multiple, that is, the number of through holes opened on the rear cavity plate 2736 may be one or multiple.
  • the number of back cavities 2733 may include at least two, and at least two back cavities 2733 may be connected through a plurality of through holes.
  • the at least two back cavities 2733 may include a first back cavity 27331 and a second back cavity 27332.
  • the first back cavity 27331 and the second back cavity 27332 may be connected through a plurality of through holes, thereby allowing adjustment (minus The air in the rear cavity 2733 adds to the stiffness of the vibration component 2710 and the driving component 2720 to increase the vibration displacement of the vibration component 2710 and the driving component 2720, thereby improving the sensitivity of the speaker 2800.
  • the back cavity plate 2736 can be opened on the back cavity plate 2736 to connect the first back cavity 27331 and the second back cavity 27332, so that the back cavity 2733 (the first back cavity 27331 and the second back cavity 27332 are connected to form a The degree of air compressibility of the cavity) becomes larger, so that the air in the rear cavity 2733 adds to the stiffness of the vibration component 2710 and the driving component 2720 and decreases, as shown in Figure 30 for details.
  • Figure 30 is a schematic diagram of a speaker and its equivalent model according to some embodiments of this specification.
  • a number of through holes 27361 can be opened on the rear cavity plate 2736.
  • the first rear cavity 27331 and the second rear cavity 27332 can be connected through the plurality of through holes 27361, so that the rear cavity can be adjusted (i.e., reduced) overall.
  • the air in 2733 is added to the stiffness of the vibrating component 2710 and the driving component 2720 to increase the vibration displacement of the vibrating component 2710 and the driving component 2720 and improve the sensitivity of the speaker 2800.
  • the air in the back cavity 2733 can be equivalent to a mass-spring-damping system with equivalent mass M and equivalent stiffness K.
  • the air in the front cavity 2731 can be equivalent to a mass-spring-damping system, with equivalent mass M 3 , equivalent stiffness K 3 and equivalent damping R 3 ;
  • the vibration component 2710 can be equivalent to a mass-spring-damping system.
  • the system has equivalent mass Mv, equivalent stiffness Kv and equivalent damping Rv, and can form a mass-spring-damping system Mv-Kv-Rv;
  • the driving component 2720 can be equivalent to a mass-spring-damping system, with equivalent Mass Md, equivalent stiffness Kd and equivalent damping Rd.
  • the equivalent mass Ma is the equivalent mass of the air in the back cavity 2733 (the air in the first back cavity 27331 and the second back cavity 27332
  • the compressibility of the air in the rear chamber 2733 becomes greater, and the air is easily compressed, so that the air in the rear chamber 2733 is attached to the vibration assembly 2710 and the drive as a whole.
  • the stiffness on the component 2720 becomes smaller, thereby increasing the vibration displacement of the vibration component 2710 and the driving component 2720, thereby improving the sensitivity of the speaker 2800.
  • the back cavity 2733 can also include more back cavities (for example, a third back cavity, a fourth back cavity, etc.), and each two adjacent back cavities can be separated by a back cavity plate to separate adjacent ones.
  • a number of through holes can be provided on the back cavity plate to connect adjacent back cavities.
  • the housing 2730 may isolate at least two rear cavities to form an enclosed space. Further, the housing 2730 can isolate the first rear chamber 27331 and the second rear chamber 27332 from the outside world to form a closed space.
  • the speaker housing 2730 may also include a rear cavity.
  • the back cavity, the back cavity plate 2736 and the driving assembly 2720 can enclose a first back cavity 27331, and the driving assembly 2720, the vibration assembly 2710, the back cavity and the back cavity plate 2736 can enclose a second back cavity. 27332.
  • the rear cavity may include a closure panel 2738 and side panels 2737.
  • the sealing plate 2738 can be disposed on the side of the driving assembly 2720 opposite to the vibration assembly 2710.
  • the sealing plate 2738, the side plate 2737, the rear cavity plate 2736 and the driving assembly 2720 can enclose the first rear cavity 27331.
  • the driving assembly 2720, the vibration assembly 2710, the side plates 2737 and the rear cavity plate 2736 may enclose the second rear cavity 27332, so that the first rear cavity 27331 and the second rear cavity 27332 form a closed space.
  • several through holes can be opened in the sealing plate 2738 to further reduce the stiffness of the air in the rear cavity 2733 added to the vibration component 2710 and the driving component 2720, thereby making the speaker more sensitive.
  • At least two rear cavities 2733 may be connected to the outside world through one or more sound guide holes on the housing 2730 .
  • one or more sound guide holes may be opened in the sealing plate 2738 to connect the first back cavity 27331 and the second back cavity 27332 with the outside world.
  • several through holes opened on the sealing plate 2738 can be used as sound guide holes to connect the first back cavity 27331 and the second back cavity 27332 with the outside world.
  • one or more sound guide holes may also be opened on the side plate 2737 forming the first rear cavity 27331.
  • the sealing plate 2738 it is not necessary to provide a sealing plate 2738 at the opening of the first rear cavity 27331 away from the driving assembly 2720, so that the cavity space of the rear cavity 2733 is an open space.
  • the speaker 2800 in which the sealing plate 2738 is not provided at the cavity opening of the first rear cavity 27331 away from the driving assembly 2720 will be described in detail below.
  • Figure 31 is a 1/4 three-dimensional structural diagram of a speaker according to some embodiments of this specification.
  • 32 is a cross-sectional view parallel to the axis of the housing cavity of the speaker according to some embodiments of the present specification.
  • Figure 33 is a view perpendicular to the axis of the housing cavity of the speaker according to some embodiments of the present specification.
  • the back cavity plate 2736 is provided with a number of through holes 27361, which can reduce the stiffness of the vibration component 2710 and the drive component 2720 caused by the air in the back cavity 2733, thereby improving the vibration component 2810 and the drive component 2820. With the vibration displacement, the vibration component 2710 can push the air to vibrate at a greater amplitude, thereby increasing the output of the speaker 2800 and making the speaker 2800 have higher sensitivity.
  • the back cavity plate 2736 has solder points 27365 (for example, the solder points of the electrical connection lines of the drive assembly 2720 on the back cavity plate 2736), and a plurality of through holes 27361 on the back cavity plate.
  • the position on 2736 can be set according to the position of the solder point 27365.
  • the through hole 27361 can be set away from the solder point 27365.
  • Figure 49 is a frequency displacement graph of a driving unit according to some embodiments of this specification.
  • curve L491 is the frequency displacement curve of the drive unit 2720 when the rear cavity plate 2736 has a through hole 2736
  • curve L492 is the frequency displacement curve of the drive unit 2720 when the rear cavity plate 2736 does not have the through hole 27361.
  • Figure 34 is a frequency response curve diagram of a speaker according to some embodiments of the present specification.
  • curve L341 is the frequency response curve of the speaker 2800 when the rear cavity plate 2736 has a through hole
  • curve L342 is when the volume of the rear cavity 2733 approaches infinity (that is, the rear cavity 2733 is completely open. It can be seen that The frequency response curve of the speaker 2800 is formed by opening an infinitely large through hole in the rear cavity plate 2736 or canceling the setting of the rear cavity plate 2736).
  • Curve L343 is the frequency response curve of the speaker 2800 when the rear cavity plate 2636 does not have a through hole. . By comparing curves L341, L342 and L343, it can be found that curves L341 and L342 are smoother than curve L343 (curve L343 has a resonance valley 3431).
  • several through holes 27361 may all be circular holes.
  • the several through holes 27361 may all be holes of other regular or irregular shapes, for example, they may be regular hexagonal holes, other polygons, ellipses, irregular shapes, etc.
  • a plurality of through holes 27361 may be distributed annularly at equal intervals on the rear cavity plate 2736 .
  • several through holes may be distributed annularly at unequal intervals on the back cavity plate 2736 .
  • several through holes 27361 may be distributed in multiple (for example, two as shown in FIG. 35C ) annular shapes on the back cavity plate 2736 .
  • the centers of circles corresponding to multiple annular distributions may coincide.
  • the plurality of through holes may be non-circularly distributed or randomly distributed on the back cavity plate 2736.
  • circles corresponding to at least two of the plurality of annular distributions may be tangent.
  • the vias in each annular distribution may be equally or unequally spaced.
  • the through holes 27361 can be designed away from the solder points 27365 to ensure that the area on the back cavity plate 2736 close to the solder points 27365 has sufficient area design. Lay out the electrode leads and solder joints 27365.
  • the number of through holes 27361 may include a variety of differently shaped through holes.
  • the plurality of through holes 27361 may include a plurality of circular holes and a plurality of regular hexagonal holes. Multiple circular holes and multiple regular hexagonal holes may be distributed in the same annular shape on the back cavity plate 2736, or may be distributed in different annular shapes. In some embodiments, multiple circular holes and multiple regular hexagonal holes can be distributed in different annular shapes on the back cavity plate 2736, that is, multiple circular holes are distributed in an annular shape, and multiple regular hexagonal holes are distributed in an annular shape. Another circular distribution. In some embodiments, multiple circular holes and multiple regular hexagonal holes can also be mixed to form multiple annular arrays, that is, each annular array has both circular holes and regular hexagonal holes.
  • the plurality of through holes 27361 may all be fan-shaped holes, and the plurality of fan-shaped holes may be equally spaced annular distribution on the rear cavity plate 2736 , that is, the plurality of fan-shaped annular holes may be distributed on the rear cavity plate 2736 in an annular manner.
  • 2736 can be seen as discontinuous annular holes.
  • several fan-shaped annular holes can be distributed in multiple annular shapes on the back cavity plate 2736 , that is, several fan-shaped annular holes can be seen as multiple concentric discontinuities on the back cavity plate 2736 . annular hole.
  • the shapes, distribution patterns, etc. of several through holes 27361 shown in FIG. 33 and FIG. 35A-FIG. 35F are only examples and are not intended to be limiting.
  • the shape of the plurality of through holes 27361 can also be regular or irregular shapes such as triangles, rectangles, regular pentagons, etc.
  • a plurality of through holes 27361 may also be distributed in a rectangular or linear manner on the back cavity plate 2736.
  • a central through hole 27367 can also be opened in the center of the rear cavity plate 2736. The central through hole 27367 can leave a deformation space for the driving assembly 2720.
  • the positions of the several through holes 27361 on the rear cavity plate 2736 are different, which will have an impact on the performance of the speaker. Therefore, the positions of the several through holes 27361 on the rear cavity plate 2736 can be reasonably set to make the speaker Has better performance.
  • the following will take the structure of the speaker 2800 and the back cavity plate 2736 shown in FIGS. 32 and 33 as an example to specifically describe the impact of the positions of several through holes 27361 on the back cavity plate 2736 on the performance (eg, sensitivity) of the speaker.
  • the position of at least one through hole 2736 among the plurality of through holes 2736 can be based on the distance between the center line of the through hole 2736 and the center line of the cavity of the housing 2730, The equivalent radius of the drive assembly 2720 and the equivalent radius of the cavity of the housing 2730 are determined.
  • the center line of the through hole 2736 may be the axis of the circular hole; and when the through hole 2736 is a hole of other shapes, the center line of the through hole 27361 may be the through hole.
  • the geometric center of the cross section of the hole 2736 or the center of the equivalent circle and a line parallel to the axis of the cavity of the housing 2730 (eg, the centerline of the cavity).
  • the center line of the cavity of the housing 2730 is the axis of the cavity
  • the equivalent radius of the cavity of the housing 2730 is the circle. radius; and when the cross-sectional shape of the cavity of the housing 2730 is a non-circular shape, the center line of the cavity of the housing 2730 is the center of the equivalent circle passing through the non-circular shape and is connected with the vibration component 2710 or a line perpendicular to the surface of the drive assembly 2720.
  • the equivalent radius of the driving component 2720 is the radius of the circle; and when the cross-sectional shape of the driving component 2720 is non-circular
  • the equivalent radius of the driving assembly 2720 is the radius of the equivalent circle of the non-circular shape.
  • the cross section of the through hole 27361, the cavity of the housing 2730, and the driving assembly 2720 may refer to the cross section of the through hole 27361, the cavity of the housing 2730, and the driving assembly 2720 perpendicular to the center line of the cavity of the housing 2730.
  • the equivalent circle of a non-circular shape may refer to a circumscribed circle of the non-circular shape.
  • the position of the through hole 27361 on the back cavity plate 2736 may be represented by a first preset ratio ⁇ .
  • the first preset ratio ⁇ may be related to the performance of the speaker.
  • Figure 36 is a frequency response curve diagram of a speaker under different first preset ratios ⁇ according to some embodiments of this specification.
  • curve L361 is the frequency response curve of the speaker 2800 when the first preset ratio ⁇ is 0.23
  • curve L362 is the frequency response curve of the speaker 2800 when the first preset ratio ⁇ is 0.39
  • curve L363 is the frequency response curve of the speaker 2800 when the first preset ratio ⁇ is 0.39.
  • the frequency response curve of the loudspeaker 2800 when the first preset ratio ⁇ is 0.55
  • the curve L364 is the frequency response curve of the speaker 2800 when the first preset ratio ⁇ is 0.71.
  • the output sound pressure level of the speaker in the mid-frequency band increases first and then decreases as the first preset ratio ⁇ increases.
  • the output sound pressure level in the mid-to-high frequency band for example, 4kHz-8kHz
  • the output sound pressure level at high frequencies for example, above 10kHz
  • the first preset ratio ⁇ can be 0.3 to 0.9. In some embodiments, in order to ensure that the frequency response curve of the speaker in the full frequency range has a higher output sound pressure level output, so that the speaker has higher sensitivity in the full frequency range and has better sound quality, the first preset The ratio ⁇ can be 0.4 to 0.75.
  • the areas of the several through holes 27361 on the rear cavity plate 2736 are different, which will have an impact on the performance of the speaker. Therefore, the area of the several through holes 27361 on the rear cavity plate 2736 can be reasonably set to make the speaker Has better performance. Specifically, the sum of the projected areas of several through holes 2736 in a plane perpendicular to the center line of the cavity and the projected area of the cavity in a plane perpendicular to the center line of the cavity can be calculated by calculating The ratio between the difference between the projected area in the plane of the center line is designed to give the speaker better performance.
  • 37 and 38 are views perpendicular to the axis of the housing cavity of the speaker according to some embodiments of the present specification.
  • Figure 39 is a frequency response curve diagram of the speaker under different second preset ratios ⁇ when the through hole is a circular hole according to some embodiments of this specification.
  • curve L391 is the frequency response curve of the speaker 2800 when the second preset ratio ⁇ is 0.012
  • curve L392 is the frequency response curve of the speaker 2800 when the second preset ratio ⁇ is 0.036
  • curve L393 is the frequency response curve of the speaker 2800 when the second preset ratio ⁇ is 0.036.
  • the frequency response curve of the speaker 2800 when the second preset ratio ⁇ is 0.06.
  • the curve L394 is the frequency response curve of the speaker 2800 when the second preset ratio ⁇ is 0.11.
  • the curve L395 is the frequency response curve of the speaker 2800 when the second preset ratio ⁇ is 0.14. frequency response curve.
  • the sensitivity of the speaker when the second preset ratio ⁇ is 0.06 is higher than the sensitivity when the second preset ratio ⁇ is 0.012.
  • the frequency response curve of the speaker when the second preset ratio ⁇ is 0.012 has an obvious resonance valley relative to the frequency response curve when the second preset ratio ⁇ is 0.06.
  • the frequency response curve of the speaker when the second preset ratio ⁇ is 0.06 The frequency response curve when the second preset ratio ⁇ is 0.06 is smoother than the frequency response curve when the second preset ratio ⁇ is 0.012, that is, it has a flatter sound pressure level output.
  • the second preset ratio ⁇ when the through hole is a round hole, in order to ensure that the frequency response curve of the speaker has a higher output sound pressure level and the speaker has higher sensitivity, the second preset ratio ⁇ may be 0.02 to 1. In some embodiments, when the through hole is a round hole, in order to ensure that the frequency response curve of the speaker has a higher output sound pressure level and a relatively flat sound pressure level output, the second preset ratio ⁇ may be 0.06 to 0.5. .
  • the second preset ratio ⁇ may be 0.1 to 0.4.
  • Figure 40 is a frequency response curve diagram of the speaker under different second preset ratios ⁇ when the through hole shown in some embodiments of this specification is a fan-shaped hole (for example, the fan-shaped hole shown in Figure 35E).
  • curve L401 is the frequency response curve of the speaker 2800 when the second preset ratio ⁇ is 0 (that is, there is no through hole on the rear cavity plate 2736)
  • curve L402 is the frequency response curve of the speaker 2800 when the second preset ratio ⁇ is 0 (that is, there is no through hole on the rear cavity plate 2736).
  • the curve L403 is the frequency response curve of the speaker 2800 when the second preset ratio ⁇ is 0.25
  • the curve L404 is the frequency response curve of the speaker 2800 when the second preset ratio ⁇ is 1.
  • the second preset ratio ⁇ can be designed, the more beneficial it is for the speaker to improve the sensitivity of the speaker.
  • the second preset ratio ⁇ can be 0.1 to 1 .
  • the second preset ratio ⁇ when the through hole is a fan-shaped hole, in order to ensure that the frequency response curve of the speaker has a higher output sound pressure level and a relatively flat sound pressure level output, the second preset ratio ⁇ can be 0.1 ⁇ 0.5. In some embodiments, when the through holes are fan-shaped holes, in order to ensure that the frequency response curve of the speaker has a higher output sound pressure level and a relatively flat sound pressure level output, and to avoid the area of several through holes being too large. To affect the structural strength of the rear cavity plate 2736, the second preset ratio ⁇ may be 0.1 ⁇ 0.4.
  • the second preset ratio ⁇ corresponding to the through hole is a round hole and the second preset ratio ⁇ corresponding to the through hole is a fan-shaped hole.
  • the ratio ⁇ has the same value range, it can be concluded that when the speaker performance is improved by opening a number of through holes on the rear cavity plate 2736, the speaker performance mainly depends on the size of the second preset ratio ⁇ , and with The shape of the via is not very relevant.
  • the value range of the second preset ratio ⁇ corresponding to the through hole being a circular hole or a fan-shaped hole is when the through hole is a regular or irregular shape such as a triangle, a rectangle, a regular hexagon, etc. Can also be applied.
  • the sum of the projected areas of the several through holes in a plane perpendicular to the center line of the cavity Sh n ( ⁇ (D/2) 2 ), where n is the number of through holes 27361, and D is the diameter of the through holes 27361.
  • n the number of through holes 27361
  • D the diameter of the through holes 27361.
  • the diameter D of the through hole 27361 may be 0.2 mm to 2 mm, which can ensure that the speaker has better performance (for example, higher sensitivity) and the rear cavity plate can also have sufficient strength.
  • the aperture D of the through hole 27361 may be 0.4 mm to 1 mm, which can ensure that the speaker has better performance (for example, higher sensitivity) and the back cavity plate has sufficient strength.
  • the back cavity plate 2736 Has good dustproof and waterproof performance.
  • 41-43 are cross-sectional views parallel to the axis of the housing cavity of the speaker according to some embodiments of this specification.
  • 44 is a cross-sectional view perpendicular to the axis of the housing cavity of the speaker according to some embodiments of the present specification.
  • At least one of the plurality of through holes 27361 may be provided with a damping mesh 27362.
  • the damping net 27362 By setting the damping net 27362, the Q value of the resonance peak of the speaker in different frequency bands can be reduced, making the resonance peak less steep, thereby making the frequency response curve of the speaker smoother and making the speaker have better sound quality.
  • the damping net 27362 may be disposed at the opening of the side of the through hole 27361 away from the driving assembly 2720 .
  • the damping net 27362 may be disposed at the opening of the through hole 27361 close to one side of the driving assembly 2720 .
  • the damping net 27362 can be disposed in the through hole 27361.
  • the edge of the damping net 27362 can be connected with the inner wall of the through hole 27361 to be fixed in the through hole 27361.
  • Figure 45 is a frequency response graph of a speaker according to some embodiments of the present specification.
  • curve L451 is the frequency response curve of the speaker when the through hole 27361 is correspondingly provided with the damping net 27362
  • curve L452 is the frequency response curve of the speaker when the through hole 27361 is not provided with the damping net 27362.
  • the resonance peak 4511 in the curve L451 is gentler than the resonance peak 4521 in the curve L452, with a smaller Q value
  • the curve L451 is smoother than the curve L452. It can be concluded that by arranging the damping net 27362 corresponding to the through hole 27361, the speaker can have a relatively flat sound pressure level output, thereby ensuring that the speaker has better sound quality.
  • the resonance peak Q value in the frequency response curve of the speaker is related to the acoustic resistance of the damping network 27362.
  • the acoustic resistance of the damping network 27362 may be 3 to 10000 MKS rayls.
  • Figure 46 is a cross-sectional view parallel to the axis of the housing cavity of the speaker according to some embodiments of the present specification.
  • the damping net 27362 in addition to providing the damping net 27362 at the corresponding position of the through hole 27361 , can also be provided on the front cavity plate 2735 , for example, the damping net 27362 can be provided correspondingly on the first cavity plate 2735 .
  • a hole (the first hole 2732 shown in Figure 27) is used to further reduce the Q value of the resonance peak in the frequency response curve of the speaker, thereby further enabling the speaker to have better sound quality.
  • Figure 47 is a schematic structural diagram of a damping net according to some embodiments of this specification.
  • the damping net 27362 may be woven from a plurality of gauze lines 27363 , and pores 27364 of the damping net 27362 are formed between the gauze lines 27363 .
  • the acoustic resistance of damping mesh 27362 is related to its porosity.
  • the porosity of the damping mesh 27362 may be the ratio between the area S1 of the pores 27364 and the area S2 of the area enclosed along the center line of the gauze mesh line 27366. In some embodiments, the smaller the porosity of the damping mesh 27362, the greater the acoustic resistance of the damping mesh 27362.
  • the porosity of the damping net in order to make the damping net 27362 have a larger acoustic resistance to reduce the resonance peak Q value in the frequency response curve of the speaker and ensure that the speaker has better sound quality, the porosity of the damping net can be 13% ⁇ 44%.
  • the acoustic resistance of damping mesh 27362 is related to the size of pores 27364. In some embodiments, the smaller the size of the pores 27364, the greater the acoustic resistance of the damping mesh 27362.
  • the size of the pore 27364 may refer to the diameter of the circle; when the shape of the pore 27364 is a rectangle, the size of the pore 27364 may refer to the length or width of the rectangle.
  • the size of the pore 27364 in order to make the damping net 27362 have a larger acoustic resistance to reduce the resonance peak Q value in the frequency response curve of the speaker and ensure that the speaker has better sound quality, the size of the pore 27364 may be 18 to 285 ⁇ m.
  • the possible beneficial effects may be any one or a combination of the above, or any other possible beneficial effects.
  • numbers are used to describe the quantities of components and properties. It should be understood that such numbers used to describe the embodiments are modified by the modifiers "about”, “approximately” or “substantially” in some examples. Grooming. Unless otherwise stated, “about,” “approximately,” or “substantially” means that the stated number is allowed to vary by ⁇ 20%. Accordingly, in some embodiments, the numerical parameters used in the specification and claims are approximations that may vary depending on the desired features of the individual embodiment. In some embodiments, numerical parameters should account for the specified number of significant digits and use general digit preservation methods. Although the numerical ranges and parameters used to identify the breadth of ranges in some embodiments of this specification are approximations, in specific embodiments, such numerical values are set as accurately as is feasible.

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Abstract

本说明书实施例提供一种扬声器，包括：驱动组件，所述驱动组件基于电信号产生振动；振动组件，所述振动组件接收所述驱动组件的振动而发生振动；壳体，所述驱动组件和所述振动组件设置于所述壳体形成的腔体内；其中，所述腔体包括位于所述振动组件一侧的前腔以及一个或多个位于所述振动组件另一侧的后腔，所述壳体包括后腔板，所述一个或多个后腔中的至少一个至少由所述驱动组件、所述振动组件以及所述后腔板围合而成，所述后腔板上开设有通孔。

Description

一种扬声器
交叉引用
本申请要求2022年6月21日提交的申请号为202210707415.7的中国申请的优先权，其全部内容通过引用并入本文。
技术领域
本申请涉及声学技术领域，特别涉及一种扬声器。
背景技术
扬声器是一种常用的电声换能器件，主要包括壳体以及位于壳体内的振动组件以及驱动组件。其中，振动组件一般将壳体内部分隔为两个腔体，例如，前腔和背腔，而驱动组件则位于背腔内，而由于背腔内的空气作用于振动组件和驱动组件上，会对扬声器的性能有所影响。因此，希望提供一种扬声器，能够改善背腔内的空气对扬声器性能的影响。
发明内容
本说明书实施例提供一种扬声器，包括：驱动组件，所述驱动组件基于电信号产生振动；振动组件，所述振动组件接收所述驱动组件的振动而发生振动；壳体，所述驱动组件和所述振动组件设置于所述壳体形成的腔体内；其中，所述腔体包括位于所述振动组件一侧的前腔以及一个或多个位于所述振动组件另一侧的后腔，所述壳体包括后腔板，所述一个或多个后腔中的至少一个至少由所述驱动组件、所述振动组件以及所述后腔板围合而成，所述后腔板上开设有通孔。
在一些实施例中，所述驱动组件的振动表面构成所述一个或多个后腔中的至少一个的侧壁的至少一部分。
在一些实施例中，所述驱动组件包括压电式声学驱动器。
在一些实施例中，所述压电式声学驱动器包括悬臂梁。
在一些实施例中，相邻的所述悬臂梁之间的缝隙不大于25μm。
在一些实施例中，所述驱动组件的振动表面上不小于90％的表面区域连续。
在一些实施例中，所述驱动组件包括压电膜。
在一些实施例中，所述后腔的数量包括至少两个，至少两个所述后腔通过所述通孔相互连通。
在一些实施例中，所述壳体包括后腔部，所述后腔部、所述后腔板以及所述驱动组件围合成第一后腔；所述驱动组件、所述振动组件、所述后腔部以及所述后腔板围合成第二后腔。
在一些实施例中，所述后腔部包括侧板和封板。
在一些实施例中，至少两个所述后腔通过所述后腔部上一个或多个导声孔与外界连通。
在一些实施例中，所述通孔中的至少一个的中心线与所述腔体的中心线之间的距离与所述驱动组件的等效半径之间的差值和所述腔体的等效半径与所述驱动组件的等效半径之间的差值之间具有第一预设比值；其中，所述第一预设比值为0.3～0.9。
在一些实施例中，在垂直于所述腔体中心线的平面内，所述通孔在所述平面内的投影面积的总和与所述腔体在所述平面内的投影面积与所述驱动组件在所述平面内的投影面积之间的差值之间具有第二预设比值；其中，所述第二预设比值为0.02～1。
在一些实施例中，所述通孔中的至少一个的孔径为0.2～2mm。
在一些实施例中，所述通孔中的至少一个对应设置有阻尼网。
在一些实施例中，所述阻尼网的声阻为3～10000MKS rayls。
在一些实施例中，所述阻尼网的孔隙尺寸为18～285um。
在一些实施例中，所述阻尼网的孔隙率为13％～44％。
附图说明
本说明书将以示例性实施例的方式进一步说明，这些示例性实施例将通过附图进行详细描述。这些实施例并非限制性的，在这些实施例中，相同的编号表示相同的结构，其中：
图1是根据本说明书一些实施例所示的振动组件及其等效振动模型示意图；
图2是根据本说明书一些实施例所示的振动组件在第一谐振峰时的变形示意图；
图3是根据本说明书一些实施例所示的振动组件在第二谐振峰时的变形示意图；
图4是根据本说明书一些实施例所示的振动组件在第三谐振峰时的变形示意图；
图5是根据本说明书一些实施例所示的振动组件在第四谐振峰时的变形示意图；
图6是根据本说明书一些实施例所示的具有不同第三、四谐振频率差值的振动组件的频响曲线示意图；
图7A是根据本说明书一些实施例所示的振动组件的频响曲线示意图；
图7B是根据本说明书另一些实施例所示的振动组件的频响曲线示意图；
图7C是根据本说明书另一些实施例所示的振动组件的频响曲线示意图；
图7D是根据本说明书另一些实施例所示的振动组件的频响曲线示意图；
图8A是根据本说明书一些实施例所示的振动组件的结构示意图；
图8B是根据本说明书另一些实施例所示的振动组件的频响曲线示意图；
图9A是根据本说明书一些实施例所示的振动组件的局部结构示意图；
图9B是根据本说明书另一些实施例所示的振动组件的频响曲线示意图；
图9C是根据本说明书另一些实施例所示的振动组件的频响曲线示意图；
图10A是根据本说明书另一些实施例所示的振动组件在第四谐振峰时的变形示意图；
图10B是根据本说明书另一些实施例所示的振动组件的频响曲线示意图；
图10C是根据本说明书另一些实施例所示的振动组件的频响曲线示意图；
图11是根据本说明书另一些实施例所示的振动组件在第四谐振峰时的变形示意图；
图12A是图11所示的振动组件的频响曲线示意图；
图12B是根据本说明书另一些实施例所示的振动组件的频响曲线示意图；
图13A是根据本说明书另一些实施例所示的振动组件的结构示意图；
图13B是根据本说明书另一些实施例所示的振动组件的结构示意图；
图14A是根据本说明书另一些实施例所示的振动组件的结构示意图；
图14B是根据本说明书另一些实施例所示的振动组件的结构示意图；
图14C是根据本说明书另一些实施例所示的振动组件的结构示意图；
图14D是根据本说明书另一些实施例所示的振动组件的结构示意图；
图15A是根据本说明书另一些实施例所示的振动组件的结构示意图；
图15B是根据本说明书另一些实施例所示的振动组件的结构示意图；
图16A是根据本说明书另一些实施例所示的振动组件的结构示意图；
图16B是根据本说明书另一些实施例所示的振动组件的结构示意图；
图16C是根据本说明书另一些实施例所示的振动组件的结构示意图；
图16D是根据本说明书另一些实施例所示的振动组件的结构示意图；
图16E是根据本说明书另一些实施例所示的振动组件的结构示意图；
图16F是根据本说明书另一些实施例所示的振动组件的频响曲线示意图；
图17A是根据本说明书另一些实施例所示的振动组件的结构示意图；
图17B是根据本说明书另一些实施例所示的振动组件的结构示意图；
图17C是根据本说明书另一些实施例所示的振动组件的频响曲线示意图；
图18A是根据本说明书另一些实施例所示的振动组件的结构示意图；
图18B是根据本说明书另一些实施例所示的振动组件的结构示意图；
图18C是根据本说明书另一些实施例所示的振动组件的结构示意图；
图19是根据本说明书另一些实施例所示的振动组件的结构示意图；
图20A是根据本说明书另一些实施例所示的振动组件的结构示意图；
图20B是根据本说明书另一些实施例所示的振动组件的频响曲线示意图；
图21A是根据本说明书另一些实施例所示的振动组件的结构示意图；
图21B是根据本说明书另一些实施例所示的振动组件的结构示意图；
图21C是根据本说明书另一些实施例所示的振动组件的结构示意图；
图21D是根据本说明书另一些实施例所示的振动组件的结构示意图；
图21E是根据本说明书另一些实施例所示的振动组件的结构示意图；
图22是根据本说明书另一些实施例所示的振动组件的结构示意图；
图23是根据本说明书另一些实施例所示的振动组件的结构示意图；
图24A是根据本说明书另一些实施例所示的振动组件的结构示意图；
图24B是根据本说明书另一些实施例所示的振动组件的结构示意图；
图24C是是根据本说明书另一些实施例所示的振动组件的频响曲线示意图；
图25A是根据本说明书另一些实施例所示的振动组件的结构示意图；
图25B是根据本说明书另一些实施例所示的振动组件的结构示意图；
图25C是根据本说明书另一些实施例所示的振动组件的结构示意图；
图26A是根据本说明书另一些实施例所示的振动组件的结构示意图；
图26B是根据本说明书另一些实施例所示的振动组件的结构示意图；
图26C是根据本说明书另一些实施例所示的振动组件的结构示意图；
图26D是根据本说明书另一些实施例所示的振动组件的结构示意图；
图26E是根据本说明书一些实施例所示的加强件的剖面结构示意图；
图27是根据本说明书的一些实施例所示的扬声器示例性结构图；
图28是根据本说明书一些实施例所示的扬声器的结构示意图；
图29是根据本说明书一些实施例所示的扬声器及其等效模型示意图；
图30是根据本说明书一些实施例所示的扬声器及其等效模型示意图；
图31是根据本说明书一些实施例所示的扬声器的部分立体结构示意图；
图32是根据本说明书一些实施例所示的扬声器平行于壳体腔体的轴线方向的截面图；
图33是根据本说明书一些实施例所示的扬声器垂直于壳体腔体的轴线方向的视图；
图34是根据本说明书一些实施例所示的扬声器的频响曲线图；
图35A是根据本说明书一些实施例所示的若干通孔在后腔板上的分布示意图；
图35B是根据本说明书一些实施例所示的若干通孔在后腔板上的分布示意图；
图35C是根据本说明书一些实施例所示的若干通孔在后腔板上的分布示意图；
图35D是根据本说明书一些实施例所示的若干通孔在后腔板上的分布示意图；
图35E是根据本说明书一些实施例所示的若干通孔在后腔板上的分布示意图；
图35F是根据本说明书一些实施例所示的若干通孔在后腔板上的分布示意图；
图36是根据本说明书一些实施例所示的扬声器在不同第一预设比值α下的频响曲线图；
图37是根据本说明书一些实施例所示的扬声器垂直于壳体腔体的轴线方向的视图；
图38是根据本说明书一些实施例所示的扬声器垂直于壳体腔体的轴线方向的视图；
图39是根据本说明书一些实施例所示的通孔为圆孔时扬声器在不同第二预设比值β下的频响曲线图；
图40是根据本说明书一些实施例所示的通孔为扇环形孔时扬声器在不同第二预设比值β下的频响曲线图；
图41是根据本说明书一些实施例所示的扬声器平行于壳体腔体的轴线方向的截面图；
图42是根据本说明书一些实施例所示的扬声器平行于壳体腔体的轴线方向的截面图；
图43是根据本说明书一些实施例所示的扬声器平行于壳体腔体的轴线方向的截面图；
图44是根据本说明书一些实施例所示的扬声器垂直于壳体腔体的轴线方向的视图；
图45是根据本说明书一些实施例所示的扬声器的频率响应曲线图；
图46是根据本说明书一些实施例所示的扬声器平行于壳体腔体的轴线方向的截面图；
图47是根据本说明书一些实施例所示的阻尼网的结构示意图；
图48是根据本说明书一些实施例所示的驱动单元的结构示意图；
图49是根据本说明书一些实施例所示的驱动单元的频率位移曲线图。
附图标记说明：振动组件：100，2710；弹性元件：110，2711；112，中心区域：2711A；悬空区域：1121，2711E；折环区域：114，2711B；连接区域：115，2711D；固定区域：116，2711C；加强件：120，2712；环形结构：122；第一环形结构：1221；第二环形结构：1222；第三环形结构：1223；中心连接部：123；条形结构：124；第一条形结构：1241；第二条形结构：1242；第三条形结构：1243；加强部分：125；局部质量结构：126；镂空部分：127；第一谐振峰：210；第二谐振峰：220；第三谐振峰：230；第四谐振峰：240；频响曲线：710；频响曲线：720；频响曲线：810，820，830，910，920，940，950，1010，1020，1030，1040，1050，1060，1210，1220，1230；扬声器：2700，2800；驱动组件：2720；驱动单元：2722；压电梁：27221；弹性连接件：27222；缝隙宽度：27223；振动传递单元：2724；壳体：2730；前腔：2731；第一孔部：2732；后腔：2733；第一后腔：27331；第二后腔：27332；第二孔部：2734；前腔板：2735；后腔板：2736；侧板：2737；封板：2738；阻尼网：27362；纱网线：27363；孔隙：27364；焊点：27365；支撑元件：2740；通孔：27361；27367：中心通孔；曲线：L341，L342，L343，L361，L362，L363，L364，L391，L392，L393，L394，L395，L401，L402，L403，L404，L451，L452，L491，L492；谐振峰：4511，4521；谐振谷：3431。
具体实施方式
为了更清楚地说明本说明书实施例的技术方案，下面将对实施例描述中所需要使用的附图作简单的介绍。显而易见地，下面描述中的附图仅仅是本说明书的一些示例或实施例，对于本领域的普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图将本说明书应用于其它类似情景。除非从语言环境中显而易见或另做说明，图中相同标号代表相同结构或操作。
本说明书实施例中提供了一种振动组件，可以应用于各种声学输出装置。声学输出装置包括但不限于扬声器、助听器等。本说明书实施例中提供的振动组件主要包括弹性元件与加强件，其中弹性元件或加强件可以与扬声器的驱动部分连接，弹性元件的边缘固定(例如，与扬声器的壳体连接)。在扬声器中，扬声器的驱动部分作为电能-机械能转换单元，通过将电能转换为机械能，为扬声器提供驱动力。振动组件可以接收驱动部分传递的力或者位移而产生相应振动输出，从而推动空气运动产生声压。弹性元件可视为通过弹簧、阻尼与空气惯性负载部分连接，通过推动空气运动实现声压的辐射。
弹性元件主要包括中心区域、设置于中心区域外围的折环区域，以及设置于折环区域外围的固定区域。在一些实施例中，为了使扬声器在较大范围内(例如20Hz-20kHz)具有较为平坦的声压级输出，可以在弹性元件的折环区域设计预设的花纹，从而达到破坏弹性元件折环区域在相应频率段的振型，避免弹性元件局部分割振动导致的声相消的发生，同时通过花纹设计使得弹性元件的局部刚度增加。进一步，通过在弹性元件的中心区域设计一层加厚的结构，使得弹性元件的中心区域的刚度增加，避免扬声器弹性元件中心区域在20Hz-20kHz范围形成分割振型导致声相消的状态。但是直接在弹性元件的中心区域设计加厚层，会使得振动组件整体质量增加，使得扬声器负载增加，驱动端与负载端阻抗失配，使得扬声器输出的声压级降低。而本说明书实施例所提供的振动组件，对弹性元件与加强件进行结构设计，其中，加强件包括一个或多个环形结构以及一个或多个条形结构，一个或多个条形结构中的每一个与一个或多个环形结构中的至少一个连接，使得振动组件可以在中高频(3kHz以上)出现所需的高阶模态，在振动组件频响曲线上出现多个谐振峰，进而使得振动组件在较宽的频带范围具有较高的灵敏度；同时通过加强件的结构设计，使得振动组件的质量较小，使得振动组件整体灵敏度提升，并且通过合理的设置加强件，在弹性元件的中心区域中设置多个镂空区域使弹性元件的中心区域的局部刚度实现可控调节，从而利用中心区域的各镂空区域的分割振型实现对振动组件输出的谐振峰的可控调节，使振动组件具有较平坦的声压级曲线。有关振动组件、弹性元件及加强件的具体内容请参照后续相关描述。
参见图1，图1是根据本说明书一些实施例所示的振动组件及其等效振动模型示意图。
在一些实施例中，振动组件100主要包括弹性元件110，弹性元件110包括中心区域112、设置于中心区域112外围的折环区域114，以及设置于折环区域114外围的固定区域116。弹性元件110被配置为沿垂直于中心区域112的方向振动，以传递振动组件100接收到的力与位移从而推动空气运动。加强件120与中心区域112连接，加强件120包括一个或多个环形结构122以及一个或多个条形结构124，一个或多个条形结构124中的每一个与一个或多个环形结构122中的至少一个连接；其中，一个或多个条形结构124中的至少一个朝向中心区域112的中心延伸。通过合理的设置加强件120，在弹性元件110的中心区域112中设置多个镂空区域使弹性元件110的中心区域112的局部刚度实现可控调节，从而利用中心区域112的各镂空区域的分割振型实现对振动组件输出的谐振峰的可控调节，使振动组件100具有较平坦的声压级曲线。同时，环形结构122与条形结构124相互配合，使得加强件120具有合适比例的加强部分和镂空部分(即镂空部)，减小了加强件120的质量，提升了振动组件100的整体灵敏度，同时通过设计环形结构122与条形结构124的形状、尺寸和数量，可以调节振动组件100的多个谐振峰的位置，从而控制振动组件100的振动输出。
弹性元件110可以是在外部载荷的作用下能够发生弹性形变的元件。在一些实施例中，弹性元件110可以为耐高温的材料，使得弹性元件110在振动组件100应用于扬声器时的加工制造过程中保持性能。在一些实施例中，弹性元件110处于200℃～300℃的环境中时，其杨氏模量和剪切模量无变化或变化很小(如变化量在5％以内)，其中，杨氏模量可以用于表征弹性元件110受拉伸或压缩时的变形能力，剪切模量可以用于表征弹性元件110受剪切时的变形能力。在一些实施例中，弹性元件110可以为具有良好弹性(即易发生弹性形变)的材料，使得振动组件100具有良好的振动响应能力。在一些实施例中，弹性元件110的材质可以是有机高分子材料、胶类材料等中的一种或多种。在一些实施例中，有机高分子材料可以为聚碳酸酯(Polycarbonate，PC)、聚酰胺(Polyamides，PA)、丙烯腈-丁二烯-苯乙烯共聚物(Acrylonitrile Butadiene Styrene，ABS)、聚苯乙烯(Polystyrene，PS)、高冲击聚苯乙烯(High Impact Polystyrene，HIPS)、聚丙烯(Polypropylene，PP)、聚对苯二甲酸乙二酯(Polyethylene Terephthalate，PET)、聚氯乙烯(Polyvinyl Chloride，PVC)、聚氨酯(Polyurethanes，PU)、聚乙烯(Polyethylene，PE)、酚醛树脂(Phenol Formaldehyde，PF)、尿素-甲醛树脂(Urea-Formaldehyde，UF)、三聚氰胺-甲醛树脂(Melamine-Formaldehyde，MF)、 聚芳酯(Polyarylate，PAR)、聚醚酰亚胺(Polyetherimide，PEI)、聚酰亚胺(Polyimide，PI)、聚萘二甲酸乙二醇酯(Polyethylene Naphthalate two formic acid glycol ester，PEN)、聚醚醚酮(Polyetheretherketone，PEEK)、碳纤维、石墨烯、硅胶等中的任意一种或其组合。在一些实施例中，有机高分子材料也可以是各种胶，包括但不限于凝胶类、有机硅胶、丙烯酸类、聚氨酯类、橡胶类、环氧类、热熔类、光固化类等等，优选地可为有机硅粘接类胶水、有机硅密封类胶水。
在一些实施例中，弹性元件110的邵氏硬度可以为1-50HA。在一些实施例中，弹性元件110的邵氏硬度可以为1-15HA。在一些实施例中，弹性元件110的邵氏硬度可以为14.9-15.1HA。
在一些实施例中，弹性元件110的杨氏模量范围为5E8Pa-1E10Pa。在一些实施例中，弹性元件110的杨氏模量范围为1E9Pa-5E9Pa。在一些实施例中，弹性元件110的杨氏模量范围为1E9Pa-4E9Pa。在一些实施例中，弹性元件110的杨氏模量范围为2E9Pa-5E9Pa。
在一些实施例中，弹性元件110的密度范围为1E3kg/m 3-4E3kg/m 3。在一些实施例中，弹性元件110的密度范围为1E3kg/m 3-2E3kg/m 3。在一些实施例中，弹性元件110的密度范围为1E3kg/m 3-3E3kg/m 3。在一些实施例中，弹性元件110的密度范围为1E3kg/m 3-1.5E3kg/m 3。在一些实施例中，弹性元件110的密度范围为1.5E3kg/m 3-2E3kg/m 3。
在一些实施例中，当振动组件应用于扬声器时，弹性元件110的中心区域112可以直接与扬声器的驱动部分相连。在另一些实施例中，设置于弹性元件110的中心区域112的加强件120可以直接与扬声器的驱动部分相连。弹性元件110的中心区域112与加强件120可以传递驱动部分的力与位移从而推动空气运动，输出声压。
中心区域112是指弹性元件110上由中心(例如，形心)向周侧延伸一定面积的区域，加强件120与中心区域112相连。弹性元件110被配置为沿垂直于中心区域112的方向振动。中心区域112作为弹性元件110的主要振动区域，可以传递力与位移并输出振动响应。
折环区域114位于中心区域112外侧。在一些实施例中，折环区域114可以设计有特性形状的花纹，从而破坏弹性元件110的折环区域114在相应频率段的振型，避免弹性元件110局部分割振动导致的声相消的发生，同时通过花纹设计使得弹性元件110的局部刚度增加。
在一些实施例中，折环区域114可以包括折环结构。在一些实施例中，通过调节折环结构的折环宽度、拱高等参数，可以使折环结构所对应的折环区域114的刚度不同，对应的高频局部分割振型的频率段也不同。折环宽度可以是折环区域114沿弹性元件110的振动方向的投影的径向宽度。拱高是指折环区域114沿弹性元件110的振动方向凸出于中心区域112或固定区域116的高度。
在一些实施例中，加强件120的一个或多个环形结构122沿弹性元件110的振动方向投影的最大面积小于中心区域112的面积。即加强件120的投影最外侧与折环区域114之间存在未被加强件120支撑的区域，本说明书将折环区域114与加强件120之间的中心区域112的部分区域称为悬空区域1121。在一些实施例中，通过调节加强件120的最大轮廓，可以调节悬空区域1121的面积，从而调节振动组件的模态振型。
固定区域116设置于折环区域114的外围。弹性元件110可以通过固定区域116实现连接固定。例如，弹性元件110可以通过固定区域116连接固定至扬声器的壳体等。在一些实施例中，固定区域116被安装固定于扬声器的壳体中，可以视为不参与弹性元件110的振动。在一些实施例中，弹性元件110的固定区域116可以通过支撑元件与扬声器的壳体实现连接。在一些实施例中，支撑元件可以包括易于变形的软性材料，使得支撑元件在振动组件100振动时也可以发生变形，从而为振动组件100的振动提供更大的位移量。在另一些实施例中，支撑元件也可以包括不易变形的硬性材料。
在一些实施例中，弹性元件110还可以包括设置于折环区域114与固定区域116之间的连接区域115。在一些实施例中，连接区域115可以为弹性元件110的振动提供额外的刚度和阻尼，从而调整振动组件100的模态振型。
为了使弹性元件110能够提供合适的刚度，弹性元件110的厚度和弹性系数可以设置在合理的范围内。在一些实施例中，弹性元件110的厚度范围可以为3um-100um。在一些实施例中，弹性元件110的厚度范围可以为3um-50um。在一些实施例中，弹性元件110的厚度范围可以为3um-30um。
加强件120可以是用于提升弹性元件110刚度的元件。在一些实施例中，加强件120与中心区域112连接，加强件120和/或中心区域112与扬声器的驱动部分相连，以传递力和/或位移，从而使振动组件100推动空气运动，输出声压。加强件120可以包括一个或多个环形结构122以及一个或多个条形结构124，一个或多个条形结构124中的每一个与一个或多个环形结构122中的至少一个连接，以在弹性元件110的中心区域112形成交错支撑。其中，一个或多个条形结构124中的至少一个朝向中心区域112的中心延伸。在一些实施例中，一个或多个条形结构124可以经过中心区域112的中心，从而对中心区域112的中心提供支撑。在一些实施例中，加强件120还可以包括中心连接部123，一个或多个条形结构124也可以不经 过中心区域112的中心，而是由中心连接部123覆盖中心区域112的中心，一个或多个条形结构124与中心连接部123连接。
环形结构122可以是围绕特定中心延伸的结构。在一些实施例中，环形结构122所围绕的中心可以是中心区域112的中心。在另一些实施例中，环形结构122所围绕的中心也可以是中心区域112上偏离中心的其它位置。在一些实施例中，环形结构122可以是外形线条闭合的结构。在一些实施例中，环形结构122沿弹性元件110的振动方向的投影形状可以包括但不限于圆环形、多边环形、曲线环形或椭圆环形中的一种或多种的组合。在另一些实施例中，环形结构122也可以是外形线条不闭合的结构。例如，环形结构122可以是具有缺口的圆环形、多边环形、曲线环形或椭圆环形等。在一些实施例中，环形结构122的数量可以是1个。在一些实施例中，环形结构122的数量也可以是多个，多个环形结构可以具有相同的形心。在一些实施例中，环形结构122的数量范围可以为1-10。在一些实施例中，环形结构122的数量范围可以为1-5。在一些实施例中，环形结构122的数量范围可以为1-3。若环形结构122的数量过多，可能会导致加强件120质量过大，进而导致振动组件100的整体灵敏度降低。在一些实施例中，通过设计环形结构122的数量可实现对加强件120的质量、刚度的调节。在一些实施例中，位于加强件120的最外围的环形结构122的尺寸可以视为加强件的最大尺寸。在一些实施例中，通过设置最外围的环形结构122的尺寸可以调节折环区域114和加强件120之间的悬空区域1121的尺寸(或面积)，从而改变振动组件100的模态振型。
在一些实施例中，一个或多个环形结构122可以包括第一环形结构和第二环形结构，第一环形结构的径向尺寸小于第二环形结构的径向尺寸。在一些实施例中，第一环形结构设置于第二环形结构的内侧。在一些实施例中，第一环形结构和第二环形结构的形心可以重合。在另一些实施例中，第一环形结构和第二环形结构的形心也可以不重合。在一些实施例中，第一环形结构和第二环形结构可以通过一个或多个条形结构124连接。在一些实施例中，第一环形结构和第二环形结构可以是相邻的环形结构。在一些实施例中，第一环形结构和第二环形结构也可以是不相邻的环形结构，第一环形结构和第二环形结构之间可以设置有一个或多个环形结构。
条形结构124可以是具有一定延伸规律的结构。在一些实施例中，条形结构124可以沿直线延伸。在一些实施例中，条形结构124也可以沿曲线延伸。在一些实施例中，曲线延伸可以包括但不限于弧线形延伸、螺旋延伸、样条曲线形延伸、圆弧形延伸、S形延伸等。在一些实施例中，条形结构124与环形结构122连接而将加强件120分割为多个镂空部。在一些实施例中，中心区域112上与镂空部对应的区域可以称为镂空区域。在一些实施例中，条形结构124的数量可以是1个。例如，1个条形结构124可以沿环形结构122(例如，任意一个环形结构)的任意一个直径方向设置。在一些实施例中，该条形结构124可以同时连接中心区域的中心(即环形结构122的形心)和环形结构122。在一些实施例中，条形结构124的数量也可以是多个。在一些实施例中，多个条形结构124可以沿环形结构122的多个直径方向设置。在一些实施例中，多个条形结构124中的至少一部分可以朝向中心区域112的中心位置延伸，该中心位置可以是弹性元件110的形心。在一些实施例中，多个条形结构124可以包括朝向其它方向延伸的另一部分。在一些实施例中，多个条形结构124中的至少一部分可以连接于中心区域的中心位置，并在中心位置形成中心连接部123。在一些实施例中，中心连接部123也可以是单独的结构，多个条形结构124中的至少一部分可以与中心连接部123连接。在一些实施例中，中心连接部123的形状可以包括但不限于圆形、方形、多边形或椭圆形等。在一些实施例中，中心连接部123的形状也可以任意设置。在一些实施例中，当环形结构122的数量为多个时，相邻环形结构122可以通过一个或多个条形结构124连接。在一些实施例中，连接于相邻环形结构122之间的条形结构124可以朝向中心区域112的中心位置延伸，或者，也可以不朝向中心区域112的中心位置延伸。
在一些实施例中，条形结构124的数量范围可以为1-100。在一些实施例中，条形结构124的数量范围可以为1-50。在一些实施例中，条形结构124的数量范围可以为1-50。在一些实施例中，条形结构124的数量范围可以为1-30。通过设置条形结构124的数量，可以调节振动组件100的整体质量、加强件120的刚度以及弹性元件110的镂空区域的面积大小，从而改变振动组件的模态振型。
在一些实施例中，条形结构124沿弹性元件110的振动方向的投影形状包括矩形、梯形、曲线型、沙漏形、花瓣形中的至少一种。通过设计不同形状的条形结构124，可以调节加强件120的质量分布(如质心位置)、加强件120的刚度、调节镂空区域的面积大小，从而改变振动组件的模态振型。
需要说明的是，本说明书实施例对环形结构122和条形结构124的结构描述只是为了便于合理的设置加强件120的结构而选择的可选结构，不应理解为对加强件120及其各部分的形状的限制。事实上，本说明书实施例中的加强件120可以通过环形结构122和条形结构124构成加强部分以及位于环形结构122和条形结构124之间的镂空部分(即镂空部，对应于中心区域112的镂空区域)。一个或多个环形结构122所在区域以及一个或多个条形结构124所在的区域共同构成加强部分。在加强件120的最大轮廓的 沿弹性元件110的振动方向的投影范围内，一个或多个环形结构122以及一个或多个条形结构124未覆盖的区域构成镂空部分。通过调控加强部分和镂空部分的参数(如面积、加强部分的厚度等)即可实现对振动组件100的振动特性(例如，谐振峰的数量及频率范围)的调控。换句话说，具有加强部分和镂空部分的任意形状的加强件，均可以使用本说明书提供的关于加强部分和镂空部分的参数设置方式进行设置，以达到调节振动组件的振动性能(例如，谐振峰的数量及位置、频响曲线的形态等)的目的，这些方案均应该包含在本申请的范围内。
在一些实施例中，参见图1，弹性元件110的固定区域116与折环区域114之间的连接区域115悬空设置，该部分区域等效质量Mm 1，并且由于弹性元件110可以提供弹性和阻尼，因此该区域可以等效为通过弹簧Km、阻尼Rm与壳体固定连接，同时该连接区域115通过弹簧Ka 1、阻尼Ra 1与弹性元件110的前端空气负载连接，传递力与位移从而推动空气运动。
在一些实施例中，弹性元件110的折环区域114具有局部等效质量Mm 2，并且该区域通过弹簧Ka 1’、阻尼Ra 1’与弹性元件110的连接区域115连接，同时折环区域114通过弹簧Ka 2、阻尼Ra 2与弹性元件110前端空气负载连接，传递力与位移从而推动空气运动。
在一些实施例中，弹性元件110的中心区域112设置有加强件120，加强件120与弹性元件110的中心区域112连接，加强件120与中心区域112的接触面积小于中心区域112的面积，使得弹性元件110的中心区域112受加强件120支撑的区域与折环区域114之间具有一部分悬空区域1121。该区域具有局部等效质量Mm 3，并且该区域通过弹簧Ka 2’、阻尼Ra 2’与折环区域114连接，同时加强件120所在区域通过弹簧Ka3、阻尼Ra3与弹性元件110前端空气负载连接，传递力与位移从而推动空气运动。
在一些实施例中，由于加强件120的设计，使得与加强件120对应的弹性元件110的中心区域112具有不少于一个的镂空区域，每个镂空区域均可以等效为一个质量-弹簧-阻尼系统，具有等效质量Mm i、等效刚度Ka i与Ka i’、等效阻尼Ra i与Ra i’，其中i为自然数。镂空区域通过弹簧Ka i’、阻尼Ra i’与相邻的镂空区域之间连接。该镂空区域还通过弹簧Ka i’、阻尼Ra i’与中心区域112内受加强件120支撑的区域和折环区域114之间的悬空区域1121连接，同时该悬空区域1121通过弹簧Ka i、阻尼Ra i与弹性元件110前端空气负载连接，传递力与位移从而推动空气运动。
在一些实施例中，加强件120本身具有等效质量Mm n，并且加强件120通过弹簧Ka n’、阻尼Ra n’与中心区域112连接，同时加强件120通过弹簧Ka n、阻尼Ra n与弹性元件110前端空气负载连接，当加强件120自身产生谐振时，通过带动中心区域112从而带动弹性元件110产生较大的运动速度与位移，从而产生较大的声压级。
根据质量-弹簧-阻尼系统的动力学特性，每一个质量-弹簧-阻尼系统均具有自身的谐振峰频率f0，并且在f0处可发生较大运动速度与位移，通过设计振动组件100的不同参数(例如，弹性元件110和/或加强件120的结构参数)，可使得振动组件100不同位置的结构形成的质量-弹簧-阻尼系统在所需的频率段发生谐振，进而使得振动组件100的频响曲线上具有多个谐振峰，使得振动组件100有效频段大大扩宽，同时通过设计加强件120，可以使得振动组件100具有更轻的质量，可使得振动组件100具有更高的声压级输出。
图2是根据本说明书一些实施例所示的振动组件第一谐振峰变形图，图3是根据本说明书一些实施例所示的振动组件第二谐振峰变形图，图4是根据本说明书一些实施例所示的振动组件第三谐振峰变形图，图5是根据本说明书一些实施例所示的振动组件第四谐振峰变形图。
根据图1所示的振动组件100的等效振动模型示意图，振动组件100的各个部分会在不同的频率段产生速度共振，并使得在对应频率段输出较大的速度值，从而使得振动组件100频响曲线在对应频率段输出较大的声压值，有相应的谐振峰；同时，通过多个谐振峰使得振动组件100的频响在可听声范围(例如，20Hz-20kHz)均具有较高的灵敏度。
请参照图1与图2。在一些实施例中，加强件120的质量、弹性元件110的质量、等效空气质量、驱动端等效质量组合形成总等效质量Mt，各部分等效阻尼形成总的等效阻尼Rt，弹性元件110(尤其是折环区域114、折环区域114与加强件120之间的悬空区域的弹性元件110)具有较大的顺性，为系统提供刚度Kt，故形成一个质量Mt-弹簧Kt-阻尼Rt系统，该系统具有谐振频率，当驱动端激励频率接近该系统的速度共振频率时，系统产生谐振(如图2所示)，并在该Mt-Kt-Rt系统的速度共振频率附近频段输出较大的速度值v a，由于振动组件100输出声压幅值与声速成正相关(p a∝v a)，因而会在频响曲线中出现一个谐振峰，本说明书中将其定义为振动组件100的第一谐振峰。在一些实施例中，参见图2，图2示出了振动组件100在A-A截面位置的振动情况，图2中白色结构表示加强件120变形前的形状及位置，黑色结构表示加强件120在第一谐振峰时的形状及位置。需要说明的是，图2仅示出了振动组件100在A-A截面上由加强件120的中心至弹性元件110的一侧边缘的结构情况，即A-A截面的一半，未示出的A-A截面的另一半与图2所示情况对称。由振动组件100在A-A截面位置的振动情况可知，在第一谐振峰的位置，振动组 件100的主要变形位置为弹性元件110上连接固定区域116的部分。在一些实施例中，振动组件100的第一谐振峰的频率(也称为第一谐振频率)可以与振动组件100的质量和弹性元件110的弹性系数的比值相关。在一些实施例中，第一谐振峰的频率范围包括180Hz-3000Hz。在一些实施例中，第一谐振峰的频率范围包括200Hz-3000Hz。在一些实施例中，第一谐振峰的频率范围包括200Hz-2500Hz。在一些实施例中，第一谐振峰的频率范围包括200Hz-2000Hz。在一些实施例中，第一谐振峰的频率范围包括200Hz-1000Hz。在一些实施例中，通过设置加强件120的结构，可以使振动组件100的第一谐振峰位于上述频率范围内。
请参照图1与图3。弹性元件110的固定区域116与折环区域114之间的连接区域115处于悬空状态，该部分区域等效质量Mm 1，并且该区域通过弹簧Km、阻尼Rm与壳体固定连接，同时连接区域115通过弹簧Ka 1、阻尼Ra 1与弹性元件110前端空气负载连接，传递力与位移从而推动空气运动。
折环区域114具有局部等效质量Mm 2，并且该区域通过弹簧Ka 1’、阻尼Ra 1’与连接区域115连接，同时折环区域114通过弹簧Ka 2、阻尼Ra 2与弹性元件110前端空气负载连接，传递力与位移从而推动空气运动。
中心区域112设置有加强件120的区域与折环区域114之间具有悬空区域1121。悬空区域1121具有局部等效质量Mm 3，并且该区域通过弹簧Ka 2’、阻尼Ra 2’与折环区域114连接，同时加强件120所在区域通过弹簧Ka 3、阻尼Ra 3与弹性元件110前端空气负载连接，传递力与位移从而推动空气运动。
如上3部分可形成等效质量Ms、等效刚度Ks、等效阻尼Rs，形成一个质量Ms-弹簧Ks-阻尼Rs系统，进一步的，该系统具有谐振频率，当驱动端激励频率接近该Ms-Ks-Rs系统的速度共振频率时，系统产生谐振，并在该Ms-Ks-Rs系统的速度共振频率附近频段输出较大的速度值v a，由于振动组件100输出声压幅值与声速成正相关(p a∝v a)，因而会在频响曲线中出现一个谐振峰，本说明书中将其定义为振动组件100的第二谐振峰。该谐振峰主要由连接区域115、折环区域114、中心区域112设置有加强件120的区域与折环区域114之间悬空区域的振动模态产生，参见图3，图3分别示出了第二谐振峰前(图3中位于上方的结构图示)和第二谐振峰后(图3中位于下方的结构图示)振动组件100的变形位置。在一些实施例中，参见图3，由振动组件100在A-A截面位置的振动情况可知，在第二谐振峰的频率前后，振动组件100的主要变形位置为折环区域114和悬空区域1121。在一些实施例中，振动组件100的第二谐振峰的频率(也称为第二谐振频率)可以与弹性元件110的质量与弹性元件110的弹性系数的比值相关。在一些实施例中，振动组件100的第二谐振峰的频率范围可以包括1000Hz-10000Hz。在一些实施例中，振动组件100的第二谐振峰的频率范围可以包括3000Hz-7000Hz。在一些实施例中，振动组件100的第二谐振峰的频率范围可以包括3000Hz-6000Hz。在一些实施例中，振动组件100的第二谐振峰的频率范围可以包括4000Hz-6000Hz。在一些实施例中，通过设置加强件120的结构，可以使振动组件100的第二谐振峰的范围在上述频率范围内。
请参照图1与图4。加强件120本身具有等效质量Mm n，并且加强件120通过弹簧Ka n’、阻尼Ra n’与中心区域112连接，同时加强件120通过弹簧Ka n、阻尼Ra n与弹性元件110前端空气负载连接，当加强件120自身产生谐振时，通过带动中心区域112从而带动弹性元件110产生较大的运动速度与位移，从而产生较大的声压级。
加强件120、连接区域115、折环区域114、中心区域112设置有加强件120的区域与折环区域114之间的悬空区域1121、等效空气质量、驱动端等效质量组合形成总等效质量Mt 1，各部分等效阻尼形成总的等效阻尼Rt 1，加强件120、弹性元件110(尤其是中心区域112被加强件120覆盖的区域)具有较大的刚度，为系统提供刚度Kt 1，故形成一个质量Mt 1-弹簧Kt 1-阻尼Rt 1系统，该系统具有一个以中心区域112直径方向某一环形区域为等效固定支点，环形区域内与环形区域外沿相反方向运动，从而形成翻转运动的振动振型，连接区域115、折环区域114、中心区域112设置有加强件120的区域与折环区域114之间的悬空区域1121在加强件120的带动下振动，实现一个以翻转运动为振型的谐振模态(如图4所示)，该谐振亦为该等效质量Mt 1-弹簧Kt 1-阻尼Rt 1系统的谐振频率点，当驱动端激励频率接近该系统的速度共振频率时，该Mt 1-Kt 1-Rt 1系统产生谐振，并在该Mt 1-Kt 1-Rt 1系统的速度共振频率附近频段输出较大的速度值v a，由于振动组件100输出声压幅值与声速成正相关(p a∝v a)，因而会在频响曲线中出现一个谐振峰，本说明书中将其定义为振动组件100的第三谐振峰。在一些实施例中，参见图4，图4分别示出了第三谐振峰前(图4中位于上方的结构图示)和第三谐振峰后(图4中位于下方的结构图示)振动组件100的变形位置，由振动组件100在A-A截面位置的振动情况可知，在第三谐振峰的频率(也称为第三谐振频率)前后，振动组件100的主要变形位置为加强件120的翻转变形。在一些实施例中，振动组件100的第三谐振峰可以与加强件120的刚度相关。在一些实施例中，第三谐振峰的频率范围可以包括5000Hz-12000Hz。在一些实施例中，第三谐振峰的频率范围可以包括6000Hz-12000Hz。在一些实施例中，第三谐振峰的频率范围可以包括6000Hz-10000Hz。在一些实施例中，通过设置加强件120的结构，可以使振动组件100的第三谐振峰的范围在上述频率范围内。
请参照图1与图5。加强件120对应中心区域112具有不少于一个的镂空区域，每个镂空区域均为一个质量-弹簧-阻尼系统，具有等效质量Mm i、等效刚度Ka i与Ka i’、等效阻尼Ra i与Ra i’。镂空区域通过弹簧Ka i’、阻尼Ra i’与相邻的镂空区域之间连接，且该镂空区域通过弹簧Ka i’、阻尼Ra i’与中心区域112内受加强件120支撑的区域和折环区域114之间的悬空区域1121连接以及同时该镂空区域通过弹簧Ka i、阻尼Ra i与弹性元件110前端空气负载连接，传递力与位移从而推动空气运动。
由于各个镂空区域之间通过加强件120的条形结构124隔开设置，因而各个镂空区域可形成各自不同的谐振频率，并单独推动与之相连的空气域运动，产生相应的声压；进一步地，通过设计加强件120的各个条形结构124的位置、尺寸、数量，从而可实现具有不同谐振频率的各个镂空区域，从而使得在振动组件100频响曲线上均有不少于1个的高频谐振峰(即第四谐振峰)。在一些实施例中，如上所述的不少于1个的高频谐振峰(即第四谐振峰)的范围可以包括10000Hz-18000Hz。
进一步地，为了提升振动组件100在高频(10000Hz-20000Hz)输出的声压级，通过设计各个条形结构124的位置、尺寸、数量，使得各个镂空区域的谐振频率相等或接近。在一些实施例中，各个镂空区域的谐振频率差值在4000Hz范围内，从而使得在振动组件100的频响曲线上具有一个输出声压级较大的高频谐振峰，本说明书中将其定义为振动组件100的第四谐振峰(如图5所示)。在一些实施例中，参见图5，由振动组件100在B-B截面位置的振动情况可知，在第四谐振峰的频率(也称为第四谐振频率)附近，振动组件100的主要变形位置为中心区域112的镂空区域产生的变形。在一些实施例中，第四谐振峰的频率范围可以包括8000Hz-20000Hz。在一些实施例中，第四谐振峰的频率范围可以包括10000Hz-18000Hz。在一些实施例中，第四谐振峰的频率范围可以包括12000Hz-18000Hz。在一些实施例中，第四谐振峰的频率范围可以包括15000Hz-18000Hz。在一些实施例中，通过设计一个或多个镂空区域的面积以及弹性元件110的厚度，可以调节各个镂空区域的谐振频率，从而使振动组件100的第四谐振峰位于上述频率范围内。在一些实施例中，为了使振动组件100的第四谐振峰的范围在上述频率范围内，各个镂空区域的面积与弹性元件110的厚度的比值范围为100mm-1000mm。在一些实施例中，为了使振动组件100的第四谐振峰的范围在上述频率范围内，各个镂空区域的面积与弹性元件110的厚度的比值范围为120mm-900mm。在一些实施例中，为了使振动组件100的第四谐振峰的范围在上述频率范围内，各个镂空区域的面积与弹性元件110的厚度的比值范围为150mm-800mm。在一些实施例中，为了使振动组件100的第四谐振峰的范围在上述频率范围内，各个镂空区域的面积与弹性元件110的厚度的比值范围为150mm-700mm。
请参照图6，图6是根据本说明书一些实施例所示的具有不同第三、四谐振频率差值的振动组件100的频响曲线，其中，横坐标表示频率(单位Hz)，纵坐标表示灵敏度(SPL)。通过设计加强件120与弹性元件110的结构，可以实现振动组件100在可听声范围具有多个谐振峰，进一步的，通过多个谐振峰等组合，使得振动组件100在整个可听声范围均有较高的灵敏度。通过设计加强件120的条形结构124与环形结构122，可实现振动组件100的第四谐振峰240位于不同的频率范围。通过设计第四谐振峰240与第三谐振峰230的频率差值△f大小，可实现第四谐振峰240与第三谐振峰230之间频率段输出较为平坦的频响曲线与较高的声压级，避免频响曲线出现低谷。如图6所示，第四谐振峰240与第三谐振峰230的频率差值△f过大(如图6所示△f2)会导致第四谐振峰240与第三谐振峰230之间频率段出现低谷、输出声压级降低，第四谐振峰240与第三谐振峰230的频率差值△f过小(如图6所示△f1)会导致第四谐振峰240的频率降低，导致高频频率段(例如：12kHz-20kHz)声压级降低，振动组件100频带变窄。通过调节加强件120和弹性元件110的结构，可以使得第三谐振峰230左移和/或第四谐振峰240右移，从而增大第四谐振峰240与第三谐振峰230的频率差值△f。在一些实施例中，第四谐振峰240与第三谐振峰230的频率差值△f的范围为80Hz-15000Hz。在一些实施例中，第四谐振峰240与第三谐振峰230的频率差值△f的范围为100Hz-13000Hz。在一些实施例中，第四谐振峰240与第三谐振峰230的频率差值△f的范围为200Hz-12000Hz。在一些实施例中，第四谐振峰240与第三谐振峰230的频率差值△f的范围为300Hz-11000Hz。在一些实施例中，第四谐振峰240与第三谐振峰230的频率差值△f的范围为400Hz-10000Hz。在一些实施例中，第四谐振峰240与第三谐振峰230的频率差值△f的范围为500Hz-9000Hz。在一些实施例中，第四谐振峰240与第三谐振峰230的频率差值△f的范围为200Hz-11000Hz。在一些实施例中，第四谐振峰240与第三谐振峰230的频率差值△f的范围为200Hz-10000Hz。在一些实施例中，第四谐振峰240与第三谐振峰230的频率差值△f的范围为2000Hz-15000Hz。在一些实施例中，第四谐振峰240与第三谐振峰230的频率差值△f的范围为3000Hz-14000Hz。在一些实施例中，第四谐振峰240与第三谐振峰230的频率差值△f的范围为4000Hz-13000Hz。
请参照图7A，通过加强件120与弹性元件110的设计，可以使得振动组件100在人耳可听声范围(20Hz-20000Hz)内出现所需的高阶模态，在振动组件100的频响曲线上出现上述第一谐振峰210、第二谐振峰220、第三谐振峰230和第四谐振峰240，即在20Hz-20000Hz的频率范围内振动组件100的频响曲线的谐振峰数量为4个，进而使得振动组件100在较宽的频带范围具有较高的灵敏度。
在一些实施例中，通过设计加强件120与弹性元件110的结构，振动组件100在可听声范围(20Hz-20000Hz)内可以仅具有3个谐振峰。例如，当振动组件100的第二谐振峰与第三谐振峰的频率差小于2000Hz时，振动组件100频响声压级曲线上，第二谐振峰与第三谐振峰体现为一个谐振峰。又例如，加强件120对应中心区域112具有不少于一个的悬空区域，当使得各个镂空区域的谐振频率高于可听声范围，或者各个镂空区域的谐振频率不同、并且在高频范围(10000Hz-18000Hz)不同频率段不同悬空区域振动相位不同、形成声音叠加抵消的效果时，可获得一个高频滚降的效果，在振动组件100声压级频响曲线中不体现第四个谐振峰。
请参照图7B，图7B是根据本说明书一些实施例所示的第二、三谐振峰重叠时的示意图。在一些实施例中，通过设计加强件120的结构与尺寸，包括加强件120的整体尺寸、条形结构124数量及尺寸、条形结构124布置位置、中心区域112设置有加强件120的区域与折环区域114之间悬空区域1121的面积、折环区域114的花纹设计(例如折环的宽度、拱高、拱形)、连接区域115面积，可以设计振动组件100第二谐振峰220与第三谐振峰230的频率差。在一些实施例中，当振动组件100第二谐振峰220与第三谐振峰230的频率差在2000Hz-3000Hz范围内时，振动组件100的频响声压级曲线(如频响曲线710)上，第二谐振峰220与第三谐振峰230之间不存在低谷，在频响曲线上仍可辨别第二谐振峰220与第三谐振峰230存在(对应图中虚线)。在一些实施例中，当振动组件100第二谐振峰220与第三谐振峰230的频率差进一步减小，例如小于2000Hz时，振动组件100的频响声压级曲线(如频响曲线720)上，第二谐振峰220与第三谐振峰230体现为一个谐振峰(对应图中实线)，可使得中高频率段(3000Hz-10000Hz)具有较高的灵敏度。
通过设计加强件120的环形结构122和条形结构124，使得加强件120对应中心区域112具有不少于一个的镂空区域，每个镂空区域均为一个质量-弹簧-阻尼系统，通过设计加强件120各个条形结构124的位置、尺寸、数量，使得各个镂空区域的谐振频率相等或接近。在一些实施例中，各个镂空区域的谐振频率差值在4000Hz范围内，可以使得在振动组件100的频响曲线上具有一个或多个输出声压级较大的高频谐振峰(即第四谐振峰)。
在一些实施例中，参见图7C，通过设计加强件120各个条形结构124的位置、尺寸、数量，使得各个镂空区域的谐振频率高于可听声范围，或者使得各个镂空区域的谐振频率不同、并且在高频范围(10000Hz-18000Hz)不同频率段不同镂空区域振动相位不同，形成声音叠加抵消的效果，可获得一个高频滚降的效果，在振动组件100的声压级频响曲线中不体现第四个谐振峰。
请参照图7D，图7D是根据本说明书一些实施例所示的振动组件100具有两个谐振峰时的频响曲线示意图。在一些实施例中，通过设计加强件120的结构，当振动组件100第二谐振峰220与第三谐振峰230的频率差小于2000Hz时，振动组件100的频响声压级曲线上，第二谐振峰220与第三谐振峰230体现为一个谐振峰。另一方面，通过设计加强件120各个条形结构124的位置、尺寸、数量，使得各个镂空区域的谐振频率高于可听声范围，或者使得各个镂空区域的谐振频率不同、并且在高频范围(10000Hz-18000Hz)不同频率段不同镂空区域振动相位不同，形成声音叠加抵消的效果，可获得一个高频滚降的效果，在振动组件100的声压级频响曲线中不体现第四个谐振峰。此时，振动组件100具有一定带宽、且中高频率段(3000Hz-10000Hz)具有较高的灵敏度的输出特征。
在一些实施例中，可以通过设计弹性元件110的悬空区域1121与折环区域114的面积和厚度，保证振动组件100第二谐振峰在所需的频率范围。在一些实施例中，振动组件100第二谐振峰的范围可以为1000Hz-10000Hz。在一些实施例中，振动组件100第二谐振峰的范围可以为3000Hz-7000Hz。在一些实施例中，在设计振动组件100第二谐振峰与第三谐振峰的频率差时，振动组件100第二谐振峰与第三谐振峰的频率差小于3000Hz。
请参照图8A，图8A是根据本说明书一些实施例所示的具有单环形结构的加强件的振动组件的结构示意图。在一些实施例中，定义悬空区域1121水平面投影面积(即悬空区域1121沿弹性元件110的振动方向的投影面积)为S v、折环区域114水平面投影面积(即折环区域114沿弹性元件110的振动方向的投影面积)为S e，悬空区域1121水平面投影面积S v与折环区域114水平面投影面积S e之和为S s。定义物理量α(单位为mm)为S s与弹性元件110(也称为振膜)的厚度Hi的比值：
Figure PCTCN2022108479-appb-000001
在一些实施例中，为了使振动组件100的第二谐振峰的频率范围为3000Hz-7000Hz，S s与振膜厚度H i的比值α取值范围可以为5000mm-12000mm。在一些实施例中，为了使振动组件100的第二谐振峰的频率范围为3000Hz-7000Hz，α取值范围为6000mm-10000mm。在一些实施例中，为了进一步调整振动组件100的第二谐振峰的频率范围向高频移动，α取值范围可以为6000mm-9000mm。在一些实施例中，为了进一步调整振动组件100的第二谐振峰的频率范围向高频移动，α取值范围可以为6000mm-8000mm。 在一些实施例中，为了进一步调整振动组件100的第二谐振峰的频率范围向高频移动，α取值范围可以为6000mm-7000mm。
在一些实施例中，悬空区域1121与折环区域114的面积与弹性元件110的厚度的关系会影响局部等效质量Mm 3与局部等效质量Mm 2、局部区域刚度Ka 2’与局部区域刚度Ka 1’，进而影响连接区域115、折环区域114、悬空区域1121三部分形成的等效质量Ms、等效刚度Ks、等效阻尼Rs，从而控制振动组件100第二谐振峰所在范围。在一些实施例中，还可以通过折环区域114的折环的拱高设计，实现对振动组件100第二谐振峰的控制。
图8B是根据本说明书另一些实施例所示的振动组件的频响曲线示意图。在一些实施例中，如图8B所示，图中频响曲线810表示当α＝8190mm时振动组件的频率响应曲线；频响曲线820表示当α＝7146mm时振动组件的频率响应曲线；频响曲线830表示当α＝12360mm时振动组件的频率响应曲线。由频响曲线820可知，α＝7146mm时，振动组件100的第二谐振峰220频率约为7000Hz。由频响曲线810可知，α＝8190mm时，振动组件100的第二谐振峰220频率约为5000Hz；且频响曲线810的第二谐振峰220的幅值与频响曲线820的第二谐振峰220的幅值相近。即，随着α的增大第二谐振峰220的谐振频率降低，幅值基本保持不变。由频响曲线820可知，α＝12360mm时，振动组件100无明显的第二谐振峰，此时振动组件100在3000Hz-7000Hz范围内的幅值相比于频响曲线810和频响曲线820降低，即α＝12360mm时振动组件100的输出声压级较低。因此，当α取值范围为6000mm-10000mm时，能够较好地控制振动组件100的第二谐振峰的频率范围为3000Hz-7000Hz，使振动组件100在3000Hz-7000Hz范围内具有较高的输出声压级。
请参照图9A，图9A是根据本说明书一些实施例所示的振动组件的局部结构示意图。在本说明书中，可以定义折环区域114的折环拱高Δh，定义物理量δ(单位为mm)为S s与振膜折环拱高为Δh的比值：
Figure PCTCN2022108479-appb-000002
在一些实施例中，δ取值范围可以为50mm-600mm。在一些实施例中，δ取值范围可以为100mm-500mm。在一些实施例中，为了使振动组件100的第二谐振峰的频率范围为3000Hz-7000Hz，δ取值范围可以为200mm-400mm。在一些实施例中，为了进一步使振动组件100的第二谐振峰的频率范围在3000Hz-7000Hz内向低频移动，δ取值范围可以为300mm-400mm。在一些实施例中，为了进一步使振动组件100的第二谐振峰的频率范围在3000Hz-7000Hz内向低频移动，δ取值范围可以为350mm-400mm。在一些实施例中，为了使振动组件100的第二谐振峰的频率范围在3000Hz-7000Hz内向高频移动，δ取值范围可以为200mm-300mm。在一些实施例中，为了进一步使振动组件100的第二谐振峰的频率范围在3000Hz-7000Hz内向高频移动，δ取值范围可以为200mm-250mm。
在一些实施例中，通过折环的拱高的设计，可以在折环区域114与悬空区域1121水平方向投影面积不变的情况下，改变折环区域114的三维尺寸，从而改变折环区域114的刚度Ka 1’，进而实现对扬声器的第二谐振峰的控制。在一些实施例中，还可以通过协调设计加强部的尺寸，对扬声器的输出声压级进行调控。
图9B是根据本说明书另一些实施例所示的振动组件的频响曲线示意图。在一些实施例中，如图9B所示，图中频响曲线910表示当δ＝262mm时振动组件的频率响应曲线；频响曲线920表示当δ＝197mm时振动组件的频率响应曲线。由频响曲线910可知，δ＝262mm时，振动组件100的第二谐振峰220频率约为5000Hz；由频响曲线920可知，δ＝197mm时，振动组件100的第二谐振峰220频率约为7000Hz。因此，随着δ的增大，第二谐振峰220的谐振频率降低，且当δ取值范围为200mm-400mm时，可以较好地控制振动组件100的第二谐振峰的频率范围为3000Hz-7000Hz。
在本说明书中，定义中心区域112的水平投影面积为S c，加强件120的最大轮廓水平投影面积S rm，悬空区域1121的水平面投影面积为S v，其中：S rm＝S c-S v。
在本说明书中，定义物理量
Figure PCTCN2022108479-appb-000003
(单位为1)为悬空区域1121的水平面投影面积S v与中心区域112的水平投影面积S c的比值：
Figure PCTCN2022108479-appb-000004
在一些实施例中，
Figure PCTCN2022108479-appb-000005
取值范围为0.05-0.7。在一些实施例中，
Figure PCTCN2022108479-appb-000006
取值范围为0.1-0.5。在一些实施例中，为了使振动组件100的第二谐振峰的频率范围为3000Hz-7000Hz，
Figure PCTCN2022108479-appb-000007
取值范围为0.15-0.35。在一些实施例中，为了进一步使振动组件100的第二谐振峰的在频率范围3000Hz-7000Hz内向高频移动，
Figure PCTCN2022108479-appb-000008
取值范围为0.15-0.25。在一些实施例中，
Figure PCTCN2022108479-appb-000009
取值范围为0.15-0.2。在一些实施例中，为了进一步使振动组件100的第二谐振峰的在频率范围3000Hz-7000Hz内向低频移动，
Figure PCTCN2022108479-appb-000010
取值范围为0.25-0.35。在一些实施例中，为了进一步使振动组件100的第二谐振峰的在频率范围3000Hz-7000Hz内向低频移动，
Figure PCTCN2022108479-appb-000011
取值范围为0.3-0.35。
在一些实施例中，由于振动组件在第二谐振峰对应的频率附近发生变形时，悬空区域1121、折环区域114会产生局部谐振，此时通过对加强件120的尺寸(即加强件120的最大轮廓尺寸)进行设计，可以使得加强件120在该频率段实现一定的弯曲变形，从而实现振膜的不同区域的声压叠加相增，从而实现振动组件或扬声器在第二谐振峰的最大的声压级输出。
图9C是根据本说明书另一些实施例所示的振动组件的频响曲线示意图。在一些实施例中，如图9C所示，图中频响曲线940表示当
Figure PCTCN2022108479-appb-000012
时振动组件的频率响应曲线；频响曲线950表示当
Figure PCTCN2022108479-appb-000013
时振动组件的频率响应曲线。由频响曲线940可知，
Figure PCTCN2022108479-appb-000014
时，振动组件100的第二谐振峰220频率为4000Hz；由频响曲线950可知，
Figure PCTCN2022108479-appb-000015
时，振动组件100的第二谐振峰220频率约为6000Hz。因此，随着
Figure PCTCN2022108479-appb-000016
的减小，第二谐振峰220的谐振频率升高，且当
Figure PCTCN2022108479-appb-000017
取值范围为0.15-0.35时，能够较好地控制振动组件100的第二谐振峰的频率范围为3000Hz-7000Hz。
在一些实施例中，条形结构124可以具有不同的宽度、形状及数量，以改变加强件120的镂空区域(对应中心区域112的悬空区域)，从而对扬声器的频响频率进行调整。具体内容请参照后续图13A-图18C及其相关描述。
在一些实施例中，可以通过设计镂空区域的面积(例如，设计加强件120的条形结构124的数量及位置、环形结构122的数量及位置等)，对振动组件100的谐振频率进行调控，以提升振动组件100的使用性能。在一些实施例中，振动组件100的第四谐振峰的范围可以为8000Hz-20000Hz。在一些实施例中，振动组件100的第四谐振峰的范围可以为10000Hz-18000Hz。
请参照图6与图10A，图10A是根据本说明书一些实施例所示的具有单环形结构的加强件的振动组件的C-C截面在第四谐振峰频率附近的变形图。由图6可知，第四谐振峰240与第三谐振峰230的频率差值△f对于振动组件100高频段频响曲线的平坦度具有较大的影响。在一些实施例中，参见图10A，由振动组件100在C-C截面位置的振动情况可知，在第四谐振峰的频率附近，振动组件100的主要变形位置为中心区域112的镂空区域产生的变形。在一些实施例中，可以通过控制加强件120对应中心区域112的各个镂空区域均为质量-弹簧-阻尼系统，对应等效质量Mm i、等效刚度Ka i来实现振动组件100第四谐振峰240的控制。例如，可以设计条形结构124数量及尺寸、环形结构122来设计中心区域112各个镂空区域的面积，定义各个镂空区域面积为S i。需要说明的是，虽然图10A示出的是具有单环形结构的加强件120的振动组件100第四谐振峰变形图，但是对于多环形结构的加强件120得振动组件，该结论仍然适用(如图5所示的振动组件100)。
为了使第四谐振峰在合适频率范围(10000Hz-18000Hz)，本说明书定义一个物理量：任意一个镂空区域面积(即镂空部分沿弹性元件110的振动方向的投影面积)S i与各个镂空区域部分振膜(如弹性元件110)厚度H i比值为面积厚度比μ(单位为mm)：
Figure PCTCN2022108479-appb-000018
在一些实施例中，当振膜(如弹性元件110)的杨氏模量和密度在预设范围内时，通过设计μ值的大小，即可调整振动组件的第四谐振峰的频率位置。在一些实施例中，振膜杨氏模量的预设范围为5*10^8Pa-1*10^10Pa。在一些实施例中，振膜杨氏模量的预设范围为1*10^9Pa-5*10^9Pa。在一些实施例中，振膜密度的预设范围为1*10^3kg/m3-4*10^3kg/m3。在一些实施例中，振膜密度的预设范围为1*10^3kg/m3-2*10^3kg/m3。
在一些实施例中，面积厚度比μ范围为1000mm-10000mm。在一些实施例中，面积厚度比μ范围为1500mm-9000mm。在一些实施例中，面积厚度比μ范围为2000mm-8000mm。在一些实施例中，面积厚度比μ范围为2500mm-7500mm。在一些实施例中，面积厚度比μ范围为3000mm-7000mm。在一些实施例中，面积厚度比μ范围为3500mm-6500mm。在一些实施例中，面积厚度比μ范围为4000mm-6000mm。
在一些实施例中，通过对各镂空区域的面积以及振膜厚度进行设计，可以控制个镂空区域的等效质量Mm i、等效刚度Ka i，进而实现扬声器第四谐振峰的控制。
图10B是根据本说明书另一些实施例所示的振动组件的频响曲线示意图。在一些实施例中，如图10B所示，图中频响曲线1010表示当μ＝5230mm时振动组件的频率响应曲线；频响曲线1020表示当μ＝4870mm时振动组件的频率响应曲线；频响曲线1030表示当μ＝5330mm时振动组件的频率响应曲线；频响曲线1040表示当μ＝5440mm时振动组件的频率响应曲线。如图10B所示，μ＝5230mm对应的频响曲线1010的第四谐振峰频率约为15000Hz，μ＝4870mm对应的频响曲线1020的第四谐振峰频率约为12000Hz，μ＝5330mm对应的频响曲线1030的第四谐振峰频率约为16000Hz，μ＝5440mm对应的频响曲线1040的第四谐振峰频率约为17000Hz。因此，当μ取值范围为4000mm-6000mm时，可以较好地控制振动组件100的第四谐振峰的频率范围为10000Hz-18000Hz。
如图11所示，在一些实施例中，加强件120具有多环形结构(例如，双环形结构)，即加强件 120包括多个沿径向相邻设置的环形结构(例如，第一环形结构、第二环形结构等)，各环形结构的直径不同，直径较小的环形结构设置于直径较大的环形结构的内侧。本说明书定义第一环形结构内部弹性元件110的各个镂空区域面积为S 1i，当第一环形结构与第二环形结构为相邻环形结构时，第一环形结构与第二环形结构之间弹性元件110的各个镂空区域面积为S 2i。在另一些实施例中，加强件120还可以有更多的环形结构122，往外依次定义第n-1环与第n环之间弹性元件110的各个镂空区域面积为S ni。位于不同直径的环形结构之间的镂空区域可以包括第一镂空区域和第二镂空区域，第一镂空区域的形心与中心区域的中心之间的距离和第二镂空区域的形心与中心区域的中心之间的距离不同。本说明书定义物理量弹性元件110的镂空区域面积比γ(单位为1)为第一镂空区域面积S ki与第二镂空区域面积S ji之比：
Figure PCTCN2022108479-appb-000019
其中，k＞j。通过设计γ值的大小，即可调整振动组件的第四谐振峰的频率位置以及输出声压级。
如图11与图12A所示，图12A是图11所对应的振动组件的频响曲线。结构一至结构四中，第一环形区域与第二环形区域之间的各个镂空区域面积为S 2i(即第一镂空区域)与第一环形区域内部各个镂空区域面积为S 1i(即第二镂空区域)面积比γ依次为5.9、4.7、3.9、3.2。由图11可知，在振动组件100第四谐振峰位置，结构一至结构四中，随着γ的减小，位于内侧的环形结构122以内的第一镂空区域的半径△R 1逐渐增大，位于内侧的环形结构122和外侧的环形结构122之间的第二镂空区域的半径△R 2逐渐减小。在一些实施例中，进一步参见图12A，结构一至结构四的振动组件的频响曲线在第四谐振峰位置的声压幅值输出逐渐增加。因此，中心区域112各个镂空区域面积比值会影响各个镂空区域谐振频率，最后获得在高频段声压叠加的效果，即通过设置γ的大小，即可调整振动组件100的高频灵敏度。
在一些实施例中，中心区域112的各个镂空区域面积比值尽量小，例如第一镂空区域和第二镂空区域面积S ki与S ji之比γ范围为0.1-10。在一些实施例中，第一镂空区域和第二镂空区域面积S ki与S ji之比γ范围为0.16-6。在一些实施例中，第一镂空区域和第二镂空区域面积S ki与S ji之比γ范围为0.2-5。在一些实施例中，第一镂空区域和第二镂空区域面积S ki与S ji之比γ范围为0.25-4。在一些实施例中，第一镂空区域和第二镂空区域面积S ki与S ji之比γ范围为0.25-1。在一些实施例中，第一镂空区域和第二镂空区域面积S ki与S ji之比γ范围为0.25-0.6。在一些实施例中，第一镂空区域和第二镂空区域面积S ki与S ji之比γ范围为0.1-4。在一些实施例中，第一镂空区域和第二镂空区域面积S ki与S ji之比γ范围为0.1-3。在一些实施例中，第一镂空区域和第二镂空区域面积S ki与S ji之比γ范围为0.1-2。在一些实施例中，第一镂空区域和第二镂空区域面积S ki与S ji之比γ范围为0.1-1。
在一些实施例中，弹性元件110的各个镂空区域面积的比值会影响各个镂空区域的谐振频率差，而各个镂空区域的谐振频率相等或接近，可以使各个镂空区域的声压叠加，从而增大扬声器在第四谐振峰位置的输出声压级。
图10C是根据本说明书另一些实施例所示的振动组件的频响曲线示意图。在一些实施例中，如图10C所示，图中频响曲线1050表示当γ＝0.6时振动组件的频率响应曲线；频响曲线1060表示当γ＝0.2时振动组件的频率响应曲线。如图10C所示，频响曲线1050在第四谐振峰处的输出声压级(幅值)较高，频响曲线1060在第四谐振峰处的输出声压级(幅值)相对较低。因此，当γ取值范围为0.25-4时，可以使振动组件100在高频范围内(如，10000Hz-18000Hz)具有较高的输出声压级。
在一些实施例中，通过设计加强件120沿振动方向的投影面积与加强件120最大轮廓沿振动方向在中心区域112的投影面积，可实现加强件120的质量、质心、刚度，以及中心区域112镂空区域的质量与刚度的调节，从而实现对振动组件100的第一谐振峰、第三谐振峰和第四谐振峰进行调节。
本说明书中，参见图11，定义加强件120的加强部分与加强件120横向面积比β(单位为1)为加强件120沿振动方向的投影形状中，加强部分投影面积S r与加强件120最大轮廓在中心区域112投影面积S t之比：
Figure PCTCN2022108479-appb-000020
在一些实施例中，加强件120的加强部分与加强件120横向面积比β为0.1-0.8。在一些实施例中，加强件120的加强部分与加强件120横向面积比β为0.2-0.7。在一些实施例中，加强件120的加强部分与加强件120横向面积比β为0.1-0.7。在一些实施例中，加强件120的加强部分与加强件120横向面积比β为0.2-0.6。在一些实施例中，加强件120的加强部分与加强件120横向面积比β为0.3-0.6。在一些实施例中，加强件120的加强部分与加强件120横向面积比β为0.4-0.5。在一些实施例中，加强件120的加强部分与加强件120横向面积比β为0.3-0.5。在一些实施例中，加强件120的加强部分与加强件120横向面积比β为0.2-0.5。在一些实施例中，加强件120的加强部分与加强件120横向面积比β为0.1-0.5。
在一些实施例中，通过设计加强件120沿振动方向的投影面积以及加强件120最大轮廓沿振动方向的投影面积，可实现对加强件120的质量、质心、刚度的控制以及对中心区域112镂空区域的质量与刚 度的调节，从而实现对加强件120的质量、弹性元件110的质量、等效空气质量、驱动端等效质量组合形成总等效质量Mt进行控制，进而对扬声器的第一谐振峰、第三谐振峰和第四谐振峰进行调节。
图12B是根据本说明书另一些实施例所示的振动组件的频响曲线示意图。在一些实施例中，如图12B所示，图中频响曲线1210表示当β＝0.16时振动组件的频率响应曲线；频响曲线1220表示当β＝0.17时振动组件的频率响应曲线；频响曲线1230表示当β＝0.26时振动组件的频率响应曲线。如图12B所示，频响曲线1210、频响曲线1220和频响曲线1230具有第一谐振峰210、第二谐振峰220、第三谐振峰230和第四谐振峰240，当β的取值发生变化时，第一谐振峰210、第三谐振峰230和第四谐振峰240的频率均产生较大的变化，而第二谐振峰220的频率变化较小。当β＝0.16时，频响曲线1210不体现第四谐振峰240。当β增大到0.17时，振动组件的第一谐振峰210和第二谐振峰220的变化较小，第三谐振峰230向高频移动，高频输出声压级提升，体现出明显的第四谐振峰240。当β增大到0.26时，第一谐振峰210向低频移动，第三谐振峰230向高频移动，第四谐振峰240向高频移动，并且振动组件的整体输出声压级降低。因此，当β取值改变时，可以对振动组件100的第一谐振峰、第三谐振峰和第四谐振峰进行调节，为了使振动组件100的第一谐振峰、第三谐振峰和第四谐振峰位于合适的范围(例如，本说明书实施例所示出的范围)内，并使振动组件具有较高的输出声压级，可以将β的取值范围设置为0.1-0.5。
请参照图13A与图13B，图13A与图13B是根据本说明书一些实施例所示的具有不同数量的条形结构的振动组件结构示意图。在一些实施例中，通过调节条形结构124的数量，可以调节振动组件100的整体质量，使得加强件120质量、弹性元件110质量、等效空气质量、驱动端等效质量组合形成总等效质量Mt发生改变，故形成质量Mt-弹簧Kt-阻尼Rt系统的谐振频率发生改变，进而使得振动组件100的一阶谐振频率发生变化，使得振动组件100第一谐振频率之前的低频段以及第一谐振频率之后的中频段灵敏度发生改变。在一些实施例中，可以设计较多的条形结构124的数量，使得总等效质量Mt增加，振动组件100第一谐振频率提前，使得振动组件100第一谐振频率之前的低频段灵敏度提升，例如3000Hz之前频率段、2000Hz之前频率段、1000Hz之前频率段、500Hz之前频率段、300Hz之前频率段。在一些实施例中，设计较少的条形结构124数量，使得总等效质量Mt降低，振动组件100第一谐振频率后移，使得振动组件100第一谐振频率之后的中频段灵敏度提升，例如，可以使3000Hz之后频率段灵敏度提升。又例如，可以使2000Hz之后频率段灵敏度提升。又例如，可以使1000Hz之后频率段灵敏度提升。又例如，可以使500Hz之后频率段灵敏度提升。又例如，可以使300Hz之后频率段灵敏度提升。
在一些实施例中，通过调节条形结构124的数量，还可以调节加强件120的刚度，使得加强件120、弹性元件110为系统提供刚度Kt 1发生改变，则加强件120、连接区域115、折环区域114、中心区域112被加强件120覆盖的区域与折环区域114之间悬空区域、等效空气质量、驱动端等效质量组合形成总等效质量Mt 1，各部分等效阻尼形成总的等效阻尼Rt1，形成的质量Mt 1-弹簧Kt 1-阻尼Rt 1系统，则以加强件120直径方向某一环形区域为等效固定支点，环形成翻转运动的谐振频率发生改变，从而使得振动组件100第三个谐振位置发生改变。
在一些实施例中，通过调节条形结构124的数量，还可以调节加强件120对应中心区域112具有不少于一个的悬空区域的面积大小，使得各个镂空区域的等效质量Mm i、等效刚度Ka i与Ka i’、等效阻尼Ra i与Ra i’发生改变，从而使得振动组件的第四谐振峰位置发生改变。在一些实施例中，通过调节条形结构124的数量，还可以调节振动组件的面积厚度比μ和加强件120的加强部分与加强件120横向面积比β，从而调节振动组件的第四谐振峰的位置。
在一些实施例中，加强件120的条形结构124的数量可调，可以根据实际应用需求，调整振动组件100第一谐振峰、第三谐振峰、第四谐振峰的位置，从而使得对振动组件100的频响实现可控的调节。
在一些实施例中，由于条形结构124在沿弹性元件110的振动方向的投影形状包括矩形、梯形、曲线型、沙漏形、花瓣形中的至少一种，因此可以通过调节条形结构124的形状，改变加强件120的镂空区域(对应加强件120投影范围内中心区域112的悬空区域)的面积，以调节镂空区域面积与弹性元件110厚度的关系(面积厚度比μ)，从而达到调整第四谐振峰的目的；也可以改变加强件120不同环形结构122之间的镂空区域面积的关系(镂空区域面积比γ)，从而达到调整第四谐振峰的目的；还可以改变加强件120的加强部分与加强件120横向面积的关系(加强件120的加强部分与加强件120横向面积比β)，达到调整第一谐振峰、第三谐振峰、第四谐振峰的目的。
请参照图14A-图14D，图14A-图14D是根据本说明书一些实施例所示的具有不同宽度的条形结构的振动组件结构示意图，其中图14A中的条形结构124为倒梯形(即梯形的短边靠近加强件120的中心)，图14B中的条形结构124为梯形(即梯形的短边远离加强件120的中心)，图14C中的条形结构124为外弧形，图14D中的条形结构124为内弧形。在一些实施例中，通过设计具有不同横向宽度的条形结构124，可有效调节加强件120的质心位置。在一些实施例中，还可以在不变化加强件120质量的同时改变加强件120的自身刚度，使得加强件120、弹性元件110(尤其是中心区域112被加强件120覆盖的区 域)为系统提供刚度Kt 1发生改变，进一步使得质量Mt 1-弹簧Kt 1-阻尼Rt 1系统翻转运动的谐振频率发生改变，从而使得振动组件100第三个谐振频率发生改变。
在一些实施例中，通过改变条形结构124的宽度设计，可以使得条形结构124从中心向四周延伸不同位置局部刚度不同。当驱动端频率接近Mt 1-弹簧Kt 1-阻尼Rt 1系统谐振频率时，固定区域116与折环区域114之间的连接区域115、折环区域114、中心区域112被加强件120覆盖区域与折环区域114之间的悬空区域在加强件120带动下振动，并实现一个3dB带宽可调的谐振峰。
如图14A-图14D所示。在一些实施例中，通过设计倒梯形条形结构124、外弧形(定义向外凸出为外弧形、向内凹陷为内弧形，外弧形可以是圆弧、椭圆、高次函数弧线、以及其它任意外弧线)条形结构124，可获得较大的3dB带宽的振动组件100第三谐振峰，可应用于要求低Q值，宽带宽的场景。在一些实施例中，通过设计梯形、矩形、内弧形(定义向外凸出为外弧形、向内凹陷为内弧形，内弧形可以是圆弧、椭圆、高次函数弧线、以及其它任意内弧线)的条形结构124，可获得灵敏度高、3dB带宽小的振动组件100第三谐振峰，可应用于要求高Q值，局部高灵敏度的场景。
通过设计具有不同横向宽度条形结构124，亦可以调节加强件120对应中心区域112具有不少于一个的悬空区域的面积大小，使得各个具有等效质量Mm i、等效刚度Ka i与Ka i’、等效阻尼Ra i与Ra i’发生改变。进一步的使得振动组件100的第四谐振峰位置发生改变。
因此，通过设计具有不同横向宽度条形结构124，可实现振动组件100第三谐振峰频率位置、谐振峰处3dB带宽、谐振峰处振动组件100灵敏度、振动组件100第四谐振峰位置。
请参照图15A与图15B，图15A与图15B是根据本说明书一些实施例所示的具有不同形状的条形结构的振动组件结构示意图，其中图15A中的条形结构124为旋转形，图15B中的条形结构124为S形。在一些实施例中，通过设计具有不同横向形状的条形结构124，可以调节加强件120的刚度，从而使得加强件120、弹性元件110(尤其是中心区域112被加强件120覆盖的区域)为系统提供刚度Kt 1发生改变，进一步使得质量Mt 1-弹簧Kt 1-阻尼Rt 1系统，翻转运动的谐振频率发生改变，从而使得振动组件100第三个谐振位置发生改变。在一些实施例中，还可以调节加强件对应中心区域112具有不少于一个的悬空区域的面积大小，使得各个具有等效质量Mm i、等效刚度Ka i与Ka i’、等效阻尼Ra i与Ra i’发生改变，从而使得振动组件100的第四谐振峰位置发生改变。在一些实施例中，通过设计具有不同横向形状的条形结构124，还可以调节加强件120内部的应力分布、控制加强件120的加工变形。
请参照图16A-图16E，图16A-图16E是根据本说明书一些实施例所示的具有不同形状的条形结构的加强件的结构示意图。在一些实施例中，为了准确调节不同形状的条形结构对振动组件的谐振峰(如第一谐振峰、第三谐振峰和第四谐振峰)的影响，对于由中心向边缘宽度逐渐减小的条形结构124，定义辐条夹角θ为条形结构在垂直于所述振动方向的投影平面上的投影形状的两个侧边之间的夹角，通过设置θ的大小即可调整振动组件的谐振峰。在一些实施例中，对于侧边为直边的条形结构124(如图16A-图16C所示)，夹角θ即为辐条两个侧边的夹角。在一些实施例中，对于侧边为弧边的条形结构124(如图16E所示)，夹角θ即为条形结构124的两个侧边切线的夹角。在一些实施例中，为了准确调节不同形状的条形结构对振动组件的谐振峰(如第一谐振峰、第三谐振峰和第四谐振峰)的影响，如图16D所示，对于由中心向边缘宽度逐渐增加的辐条结构，定义辐条夹角为θ i，通过设置θ i的大小即可调整振动组件的谐振峰。在一些实施例中，对于侧边为直边的条形结构124，夹角θ i即为辐条两个侧边的夹角。在一些实施例中，对于侧边为直边的条形结构124，夹角θ i即为辐条两个侧边切线的夹角。
在一些实施例中，可以通过设计条形结构124的夹角θ(或θ i)可以在不改变或者改变加强件120的质量的同时改变加强件120自身的刚度，使得加强件120、弹性元件110为系统提供刚度Kt 1发生改变，进一步使得质量Mt 1-弹簧Kt 1-阻尼Rt 1系统，翻转运动的谐振频率发生改变，从而使得振动组件100第三个谐振位置发生改变，同时还可以控制振动组件100第三谐振峰的3dB带宽。在一些实施例中，可以通过增大条形结构124的夹角θ(或θ i)，有效增加振动组件100第三谐振峰的3dB带宽。
对应于某些需要低Q值宽带宽的振动组件100频响，可设计较大的条形结构124的夹角θ(或θ i)。在一些实施例中，条形结构124的夹角为θ的范围可以为0至150°。在一些实施例中，条形结构124的夹角为θ的范围可以为0至120°。在一些实施例中，条形结构124的夹角为θ的范围可以为0至90°。在一些实施例中，条形结构124的夹角为θ的范围可以为0至80°。在一些实施例中，条形结构124的夹角为θ的范围可以为0°至60°。在一些实施例中，条形结构124的夹角为θ i的范围可以为0至90°。在一些实施例中，条形结构124的夹角为θ i的范围可以为0至80°。在一些实施例中，条形结构124的夹角为θ i的范围可以为0至70°。在一些实施例中，条形结构124的夹角为θ i的范围可以为0至60°。在一些实施例中，条形结构124的夹角为θ i的范围可以为0至45°。
对应于某些需要高Q值窄带宽的振动组件100频响，可设计较小的条形结构124的夹角θ(或θ i)。在一些实施例中，条形结构124的夹角为θ的范围可以为0至90°。在一些实施例中，条形结构124 的夹角为θ的范围可以为0至80°。在一些实施例中，条形结构124的夹角为θ的范围可以为0至70°。在一些实施例中，条形结构124的夹角为θ的范围可以为0至60°。在一些实施例中，条形结构124的夹角为θ的范围可以为0至45°。在一些实施例中，条形结构124的夹角为θ i的范围可以为0至60°。在一些实施例中，条形结构124的夹角为θ i的范围可以为0至80°。在一些实施例中，条形结构124的夹角为θ i的范围可以为0至90°。在一些实施例中，条形结构124的夹角为θ i的范围可以为0至120°。在一些实施例中，条形结构124的夹角为θ i的范围可以为0至150°。
在一些实施例中，定义θ与θi关系为：
θ＝-θ i。    (公式7)
对应于某些需要低Q值宽带宽的扬声器频响，可设计较大的条形结构124的夹角θ。在一些实施例中，条形结构124的夹角为θ的范围可以为-90°至150°。在一些实施例中，条形结构124的夹角为θ的范围可以为-45°至90°。在一些实施例中，条形结构124的夹角为θ的范围可以为0°至60°。
对应于某些需要高Q值窄带宽的扬声器频响，可设计较小的条形结构124的夹角θ在一些实施例中，条形结构124的夹角为θ的范围可以为-150°至90°。在一些实施例中，条形结构124的夹角为θ的范围可以为-90°至45°。在一些实施例中，条形结构124的夹角为θ的范围可以为-60°至0°。
在一些实施例中，对于一些不规则形状的条形结构124，无法对条形结构124夹角的方法进行设计，此时可采用面积的方法进行设计，可以不变化或者变化加强件120质量同时改变加强件120的自身刚度，使得加强件120、弹性元件110为系统提供刚度Kt 1发生改变，进一步使得质量Mt 1-弹簧Kt 1-阻尼Rt 1系统，翻转运动的谐振频率发生改变，从而使得振动组件100第三个谐振位置发生改变；进一步的，还可以控制振动组件100第三谐振峰的3dB带宽。
图16F是根据本说明书另一些实施例所示的振动组件的频响曲线示意图，通过对振动组件进行结构设计，可以使得振动组件的第二谐振峰220和第三谐振峰230合并，使得振动组件的频响曲线仅体现出两个谐振峰。图16F分别示出了条形结构124的夹角θ取值为20°、10°和1°时振动组件的频响曲线，如图16F所示，随着夹角θ取值增大，振动组件的中高频谐振峰(如，第二谐振峰220和第三谐振峰230合并后的谐振峰)的3dB带宽逐渐增大。因此，通过调整条形结构124的夹角θ的取值，即可调整振动组件的中高频谐振峰的3dB带宽。在一些实施例中，通过将条形结构124的夹角θ的取值范围设置为-60°至60°，可以使得振动组件的至少一个中高频谐振峰的3dB带宽不低于1000Hz。
请参照图17A-图17B，图17A-图17B是根据本说明书一些实施例所示的具有不规则条形结构的加强件的结构示意图。在一些实施例中，为了准确设计不规则条形结构以便达到调节振动组件谐振峰的目的，参见图17A，以加强件120最大轮廓定义半径为R的圆，同时最大轮廓定义的圆的半径R的1/2定义半径为R/2，定义半径为R/2范围内加强件120水平投影面积为S in，半径为R/2与半径为R圆之间范围内加强件120水平投影(即沿振动组件的振动方向的投影)面积为S out，定义物理量τ为加强件120水平投影面积为S out与加强件120水平投影面积为S in的比值：
Figure PCTCN2022108479-appb-000021
在一些实施例中，可以通过调节加强件120水平投影面积为S out与加强件120水平投影面积为S in的比值τ来控制加强件120的质量分布，从而实现对振动组件100第三谐振峰的带宽控制。对于其他类型规则的加强件120结构，参见图17B，例如椭圆形、长方形、正方形、其他多边形结构，以加强件120最大轮廓定义与加强件120类似的图形进行包络，并定义图形中心区域为参考点，参考点至轮廓包络线各个点距离为R(例如，R i、…、R i+3)，所有对应R/2(例如，R i/2、…、R i+3/2)点形成区域加强件120水平投影面积为S in，距离R/2与距离为R之间范围内加强件120水平投影面积为S out；对于其他不规则的加强件120结构，以其最大轮廓以相近结构的规则图形进行包络，并以如上相同的的方式定义S in、S out、比值τ。
对应于某些需要低Q值宽带宽的振动组件100频响，可设计较大质量集中于加强件120中心区域。在一些实施例中，水平投影面积为S out与水平投影面积为S in比值τ取值范围可以为0.3-2。在一些实施例中，水平投影面积为S out与水平投影面积为S in比值τ取值范围可以为0.5-1.5。在一些实施例中，水平投影面积为S out与水平投影面积为S in比值τ取值范围可以为0.5-1.2；在一些实施例中，水平投影面积为S out与水平投影面积为S in比值τ取值范围可以为0.5-1.3；在一些实施例中，水平投影面积为S out与水平投影面积为S in比值τ取值范围可以为0.5-1.4；在一些实施例中，水平投影面积为S out与水平投影面积为S in比值τ取值范围可以为0.3-1.2；在一些实施例中，水平投影面积为S out与水平投影面积为S in比值τ取值范围可以为0.3-1.6；在一些实施例中，水平投影面积为S out与水平投影面积为S in比值τ取值范围可以为0.5-2；在一些实施例中，水平投影面积为S out与水平投影面积为S in比值τ取值范围可以为0.5-2.2；在一些实施例中，水平投影面积为S out与水平投影面积为S in比值τ取值范围可以为0.3-2.2；在一些实施例中，水平投影面积为S out与水平投影面积为S in比值τ取值范围可以为0.3-2。
对应于某些需要高Q值窄带宽的振动组件100频响，可设计较大质量集中于加强件120边缘区域。在一些实施例中，水平投影面积为S out与水平投影面积为S in比值τ取值范围可以为1-3。在一些实施例中，水平投影面积为S out与水平投影面积为S in比值τ取值范围可以为1.2-2.8。在一些实施例中，水平投影面积为S out与水平投影面积为S in比值τ取值范围可以为1.4-2.6。在一些实施例中，水平投影面积为S out与水平投影面积为S in比值τ取值范围可以为1.6-2.4。在一些实施例中，水平投影面积为S out与水平投影面积为S in比值τ取值范围可以为1.8-2.2。在一些实施例中，水平投影面积为S out与水平投影面积为S in比值τ取值范围可以为1.2-2。在一些实施例中，水平投影面积为S out与水平投影面积为S in比值τ取值范围可以为1-2。在一些实施例中，水平投影面积为S out与水平投影面积为S in比值τ取值范围可以为2-2.8。在一些实施例中，水平投影面积为S out与水平投影面积为S in比值τ取值范围可以为2-2.5。
在一些实施例中，通过调节水平投影面积为S out与水平投影面积为S in比值τ的取值范围，还可以使振动组件在振动时的翻转运动的谐振频率发生改变，从而使得第三谐振峰的位置发生改变。图17C是根据本说明书另一些实施例所示的振动组件的频响曲线示意图。如图17C所示，图17C中分别为τ取值1.68、1.73时振动组件的频响曲线，且两条频响曲线的第三谐振峰230处的3dB带宽均较窄。并且，当τ的取值由1.68增大为1.73时，第三谐振峰230向低频移动。因此，随着τ的取值增大，第三谐振峰230对应的频率减小，通过调节振动组件的τ的取值，可以有效调节第三谐振峰的带宽和位置。
在一些实施例中，可以通过调节环形结构122的数量(例如，在1-10的范围内)，改变加强件120的镂空区域(对应加强件120投影范围内中心区域112的悬空区域)的面积，以调节镂空区域面积与弹性元件110厚度的关系(面积厚度比μ)，从而达到调整第四谐振峰的目的；也可以改变加强件120不同环形结构122之间的镂空区域面积的关系(镂空区域面积比γ)，从而达到调整第四谐振峰的目的；还可以改变加强件120的加强部分与加强件120横向面积的关系(加强件120的加强部分与加强件120横向面积比β)，调整第一谐振峰、第三谐振峰、第四谐振峰的目的。
在一些实施例中，环形结构122可以包括形心重合的第一环形结构和第二环形结构，此时第一环形结构的径向尺寸小于第二环形结构的径向尺寸。在一些实施例中，条形结构124还可以包括至少一个第一条形结构和至少一个第二条形结构，至少一个第一条形结构设置于第一环形结构内侧，并与第一环形结构连接，至少一个第二条形结构设置于第一环形结构和第二环形结构之间，并分别与第一环形结构和第二环形结构连接，以使加强件120形成多个不同的镂空区域。
请参照图18A-图18C，图18A-图18C是根据本说明书一些实施例所示的具有不同数量的环形结构的振动组件结构示意图，其中图18A的环形结构122是单环结构，图18B的环形结构122是双环结构，图18C的环形结构122是三环结构。通过设计环形结构122的数量可实现对加强件120质量、刚度的调节，同时可实现对中心区域112镂空区域面积大小的调节。在一些实施例中，环形结构122的数量范围可以为1到10。在一些实施例中，环形结构122的数量范围可以为1到5。在一些实施例中，环形结构122的数量范围可以为1到3。
在一些实施例中，通过环形结构122的数量调节，可以调节加强件120质量，使得加强件120质量、弹性元件110质量、等效空气质量、驱动端等效质量组合形成总等效质量Mt发生改变，故形成质量Mt-弹簧Kt-阻尼Rt系统的谐振频率发生改变，进而使得振动组件100的一阶谐振频率发生变化。
在一些实施例中，通过环形结构122的数量调节，还可以调节加强件120刚度，使得加强件120、弹性元件110(尤其是中心区域112被加强件120覆盖的区域)为系统提供刚度Kt 1发生改变，进一步使得质量Mt 1-弹簧Kt 1-阻尼Rt 1系统，翻转运动的谐振频率发生改变，从而使得振动组件100第三个谐振位置发生改变。在一些实施例中，通过环形结构122的数量调节，还可以使得条形结构124从中心向四周延伸不同位置刚度分布不同，当驱动端频率接近Mt 1-弹簧Kt 1-阻尼Rt 1系统谐振频率时，连接区域115、折环区域114、中心区域112被加强件120覆盖的区域与折环区域114之间的局部悬空区域的面积在加强件120带动下振动，并实现一个3dB带宽可调的谐振峰。
在一些实施例中，通过环形结构122的数量调节，还可以调节中心区域112镂空区域面积的大小，使得各个镂空区域具有的等效质量Mm i、等效刚度Ka i与Ka i’、等效阻尼Ra i与Ra i’发生改变，从而使得振动组件100的第四谐振峰位置发生改变。
在一些实施例中，通过环形结构122的数量调节，还可以调节最外侧环形结构122的尺寸，可调控中心区域112被加强件120覆盖的区域与折环区域114之间的局部镂空区域的面积，而该区域、连接区域115、折环区域114三部分可形成等效的质量Ms、等效刚度Ks、等效阻尼Rs。通过中心区域112被加强件120覆盖的区域与折环区域114之间的局部悬空区域的面积，使得质量Ms-弹簧Ks-阻尼Rs系统谐振频率改变，从而实现振动组件100第二谐振峰位置的调节。
在一些实施例中，通过调节环形结构122数量，可以使得振动组件100第四谐振峰位于10kHz-18kHz范围，各个镂空区域面积Si与各个镂空区域部分振膜厚度Hi比值为面积厚度比μ范围为150mm- 700mm；任意两个弹性元件110的镂空区域面积S ki与S ji之比γ范围为0.25-4；加强件120的加强部分与加强件120横向面积比β为0.2-0.7。在一些实施例中，通过调节环形结构122数量，可以使得振动组件100第四谐振峰位于10kHz-18kHz范围，各个镂空区域面积Si与各个镂空区域部分振膜厚度Hi比值为面积厚度比μ范围为100mm-1000mm；任意两个弹性元件110的镂空区域面积S ki与S ji之比γ范围为0.1-10；加强件120的加强部分与加强件120横向面积比β为0.1-0.8。
请参照图19，图19是根据本说明书一些实施例所示的内外环条形结构不连续的振动组件的结构示意图。在一些实施例中，当振动组件100包括至少2个环形结构时，环形结构122将条形结构沿124中心向四周延伸方向分为多个区域，各个区域中的条形结构124可以连续设置、也可以不连续设置。在一些实施例中，振动组件100的一个或多个环形结构122可以至少包括第一环形结构1221。例如，环形结构122可以包括形心重合的第一环形结构1221和第二环形结构1222，第一环形结构1221的径向尺寸小于第二环形结构1222的径向尺寸。在一些实施例中，条形结构124可以包括至少一个第一条形结构1241和至少一个第二条形结构1242，任意一个第一条形结构1241设置于第一环形结构1221内侧的一个第一位置，并与第一环形结构1221连接，任意一个第二条形结构1242与第一环形结构1221的外侧连接于一个第二位置。多个第一条形结构1241连接于多个第一位置，多个第二条形结构1242连接于多个第二位置，在一些实施例中，至少一个第一位置与第一环形结构1221的中心的连线不经过任意一个第二位置。在一些实施例中，至少一个第二位置与第一环形结构1221的中心的连线不经过任意一个第一位置。在一些实施例中，多个第一位置和多个第二位置均不相同即第一位置、第二位置和第一环形结构1221的中心均不共线，第一条形结构1241和第二条形结构1242在第一环形结构1221上的连接位置可以不同。在一些实施例中，第一条形结构1241和第二条形结构1242的数量可以相同，也可以不同。
通过环形结构122内外区域的条形结构124不连续的设置，可实现环形结构122内外区域的条形结构124数量不等，内外区域的条形结构124横向宽度不同，内外区域的条形结构124横向形状不同，从而可以在较大范围内调节加强件120的质量、刚度和质心分布，以及中心区域112的镂空区域数量以及面积大小。
在一些实施例中，通过调节加强件120的质量，可以调控总等效质量Mt发生改变，故形成质量Mt-弹簧Kt-阻尼Rt系统的谐振频率发生改变，进而使得振动组件100的一阶谐振频率发生变化。通过调节加强件120刚度，可调节Mt 1-弹簧Kt 1-阻尼Rt 1系统，翻转运动的谐振频率，从而使得振动组件100第三个谐振位置发生改变；使得条形结构124从中心向四周延伸不同位置刚度分布不同，实现一个3dB带宽可调的振动组件100第三谐振峰。通过调节中心区域112的镂空区域数量以及面积大小，可以使得振动组件100的第四谐振峰位置与灵敏度发生改变。
在一些实施例中，通过环形结构122内外区域的条形结构124不连续设置，使得振动组件100第四谐振峰位于10kHz-18kHz范围，各个镂空区域面积S i与各个镂空区域部分弹性元件110厚度H i比值为面积厚度比μ范围为150mm-700mm，任意两个弹性元件110镂空区域面积S ki与S ji之比γ范围为0.25-4，加强件120的加强部分与加强件120横向面积比β为0.2-0.7。在一些实施例中，通过环形结构122内外区域的条形结构124不连续设置，可以使得振动组件100第四谐振峰位于10kHz-18kHz范围，各个镂空区域面积S i与各个镂空区域部分振膜厚度H i比值为面积厚度比μ范围为100mm-1000mm；任意两个弹性元件110的镂空区域面积S ki与S ji之比γ范围为0.1-10；加强件120的加强部分与加强件120横向面积比β为0.1-0.8。
请参照图20A，图20A是根据本说明书一些实施例所示的具有多个环形结构的振动组件的结构示意图。在一些实施例中，可以通过设计多个环形结构122从而设计多个环形结构122的间隔区域，通过设计不同间隔区域的条形结构124的数量，从而实现加强件120的质量分布设计。需要说明的是，各个环形结构122的间隔区域设计的条形结构124的数量可以不等、形状可以不同、位置也可不用对应。
在一些实施例中，可以定义由中心往外的各个环形结构122依次为第一环形结构1221、第二环形结构1222、第三环形结构1223、……第n环形结构，第n环形结构与第n-1环形结构之间间隔区域的条形结构124为第n条形结构(如第一条形结构1241、第二条形结构1242、第三条形结构1243)，定义第n条形结构(即连接于第n环形结构内侧的条形结构)的数量为Q n，其中，n为自然数。定义物理量q为任意第i条形结构的数量Q i与第j条形结构的数量为Q j的比值：
Figure PCTCN2022108479-appb-000022
在一些实施例中，任意第i条形结构的数量Q i与第j条形结构的数量Q j比值q取值范围可以为0.05-20。在一些实施例中，任意第i条形结构的数量Q i与第j条形结构的数量Q j比值q取值范围可以为0.1-10。在一些实施例中，任意第i条形结构的数量Q i与第j条形结构的数量Q j比值q取值范围可以为0.1-8。在一些实施例中，任意第i条形结构的数量Q i与第j条形结构的数量Q j比值q取值范围可以为0.1-6。 在一些实施例中，任意第i条形结构的数量Q i与第j条形结构的数量Q j比值q取值范围可以为0.2-5。在一些实施例中，任意第i条形结构的数量Q i与第j条形结构的数量Q j比值q取值范围可以为0.3-4。在一些实施例中，任意第i条形结构的数量Q i与第j条形结构的数量Q j比值q取值范围可以为0.5-6。在一些实施例中，任意第i条形结构的数量Q i与第j条形结构的数量Q j比值q取值范围可以为1-4。在一些实施例中，任意第i条形结构的数量Q i与第j条形结构的数量Q j比值q取值范围可以为1-2。在一些实施例中，任意第i条形结构的数量Q i与第j条形结构的数量Q j比值q取值范围可以为0.5-2。
在一些实施例中，通过设计多个环形结构122从而设计多个环形结构122的间隔区域，通过设计不同间隔区域的条形结构124的数量，从而实现加强件120的质量分布设计，进而在加强件120的质量不变化或者变化的条件下，改变加强件120的刚度，使得加强件120、振膜的等效刚度Kt 1发生改变，进一步使得质量Mt 1-弹簧Kt 1-阻尼Rt 1系统的翻转运动的谐振频率发生改变，从而使得扬声器第三谐振峰位置发生改变。
图20B是根据本说明书一些实施例所示的振动组件的频响曲线示意图。如图20B所示的两条频响曲线分别是q＝0.67与q＝0.1时的振动组件的频响曲线，两条频响曲线的第三谐振峰230的频率接近，但q＝0.67对应的频响曲线的第三谐振峰230的幅值高于q＝0.1对应的频响曲线的第三谐振峰幅值。因此，由图20B可知，通过调整q的取值，可以控制第三谐振峰的幅值改变，从而调节振动组件的灵敏度。在一些实施例中，当q的取值范围为0.2-5时，振动组件具有较高的灵敏度。
在一些实施例中，环形结构122的形状可以包括圆环形、椭圆环形、多边环形和曲线环形中的至少一种。通过设计不同形状和/或不同尺寸大小的环形结构122，可以实现对加强件120质量、刚度的调节，同时可实现对中心区域112镂空区域面积大小的调节。
在一些实施例中，悬空区域1121的尺寸与形状可以通过中心区域112被加强件120覆盖的区域的尺寸与形状以及加强件120的尺寸与形状进行调控。在一些实施例中，还可以通过调控折环区域114的面积与形状，以调节悬空区域1121与折环区域114总的水平投影(即沿振动组件的振动方向的投影)面积，而通过控制悬空区域1121与折环区域114总的水平投影面积与弹性元件110厚度、折环拱高等数据，可精确地控制振动组件100的第二谐振峰位于所需的频率段。在一些实施例中，振动组件100的第二谐振峰可以位于3000Hz-7000Hz范围。在一些实施例中，通过控制悬空区域1121与折环区域114的面积比例，可以调节振动组件100在其第二谐振峰频率段该局部区域的振动位移，从而最大化振动组件100在第二谐振峰位置处的输出灵敏度。
在一些实施例中，通过振动组件100的折环区域114及悬空区域1121的尺寸与弹性元件110的厚度的关系设置，可以实现对局部等效质量Mm 3与局部等效质量Mm 2、局部区域刚度Ka 2’与局部区域刚度Ka 1’的控制，进而保证振动组件100第二谐振峰在所需的频率范围。在一些实施例中，通过改变环形结构122的形状，使S s与振膜厚度H i的比值α取值范围为5000mm-12000mm，可以使振动组件100的第二谐振峰可以位于3000Hz-7000Hz范围。在一些实施例中，通过改变环形结构122的形状，使S s与振膜厚度H i的比值α取值范围为6000mm-10000mm，可以使振动组件100的第二谐振峰可以位于3000Hz-7000Hz范围。
在一些实施例中，通过折环区域114及悬空区域1121的尺寸与折环区域114的折环拱高尺寸的关系，通过折环的拱高设计，可实现折环区域114与悬空区域1121水平方向投影面积不改变情况下改变弹性元件110的折环区域114的三维尺寸，从而改变折环区域114的刚度Ka 1’，进而实现对振动组件100第二谐振峰的控制。在一些实施例中，S s与折环拱高为Δh的比值δ取值范围可以为50mm-600mm。在一些实施例中，S s与折环拱高为Δh的比值δ取值范围可以为100mm-500mm。在一些实施例中，S s与折环拱高为Δh的比值δ取值范围可以为200mm-400mm。
在一些实施例中，通过悬空区域1121的尺寸与中心区域112的面积关系，使得加强件120在该频率段实现一定的弯曲变形，实现弹性元件110不同区域的声压叠加相增与相减，从而实现最大的声压级输出。在一些实施例中，悬空区域1121水平面投影面积为S v与振动组件100振膜中心部水平投影面积为S c的比值
Figure PCTCN2022108479-appb-000023
取值范围可以为0.05-0.7。在一些实施例中，悬空区域1121水平面投影面积为S v与振动组件100振膜中心部水平投影面积为S c的比值
Figure PCTCN2022108479-appb-000024
取值范围可以为0.1-0.5。在一些实施例中，悬空区域1121水平面投影面积为S v与振动组件100振膜中心部水平投影面积为S c的比值
Figure PCTCN2022108479-appb-000025
取值范围可以为0.15-0.35。
请参照图21A-图21E，图21A-图21E是根据本说明书一些实施例所示的具有不同结构的振动组件的结构示意图。在一些实施例中，加强件120的外轮廓可以是具有向外延伸辐条的结构(如图21A所示)，也可以是圆形环形结构、椭圆形环形结构或曲线环形结构(如图21B所示)、多边形、其他不规则的环形结构等，其中多边形可以包括三角形、四边形、五边形、六边形(如图21C-图21D所示)、七边形、八边形九边形、十边形等。在一些实施例中，弹性元件110也可以是多边形，例如：三角形、四边形(如图21D与图21E所示)、五边形、六边形、七边形、八边形、九边形、十边形等以及其他不规则的图 形，加强件120可对应设计为相似或不相似的结构，从而通过加强件120、中心区域112、折环区域114的折环的形状控制悬空区域1121的形状，从而实现对振动组件100性能的调节。
请参照图22，图22是根据本说明书一些实施例所示的变宽度的环形结构的振动组件的结构示意图。在一些实施例中，通过在任意一个环形结构122不同位置设计不等宽的局部结构，可以有效的调整调节加强件120的质量，可以调控总等效质量Mt发生改变，故形成质量Mt-弹簧Kt-阻尼Rt系统的谐振频率发生改变，进而使得振动组件100的一阶谐振频率发生变化。同时，通过在任意一个环形结构122不同位置(例如，相邻位置)设计不等宽的局部结构，可以调节加强件120的刚度以及质心分布，从而调节Mt1-弹簧Kt1-阻尼Rt1系统翻转运动的谐振频率，使得振动组件100第三个谐振位置发生改变。不等宽的环形结构122设计还可以使得条形结构124从中心向四周延伸不同位置刚度分布不同，实现一个3dB带宽可调的振动组件100第三谐振峰。而且不等宽的环形结构122设计还可以调节中心区域112的悬空区域数量以及面积大小，使得振动组件100的第四谐振峰位置与灵敏度发生改变。例如，一个或多个环形结构122中的至少一个在与一个或多个条形结构124中的任意一个的连接位置的两侧具有不同的径向宽度，如图22所示。又例如，一个或多个环形结构122中的至少一个在与一个或多个条形结构124中的任意两个的连接位置之间具有不同的周向宽度。
在一些实施例中，通过任意一个环形结构122任意位置(例如，相邻位置)设计不等宽的局部结构，使得振动组件100第四谐振峰位于15kHz-18kHz范围，各个镂空区域面积S i与各个镂空区域部分弹性元件110厚度H i比值为面积厚度比μ范围为150mm-700mm，任意两个弹性元件110镂空区域面积S ki与S ji之比γ范围为0.25-4，加强件120的加强部分与加强件120横向面积比β为0.2-0.7。在一些实施例中，通过任意一个环形结构122任意位置设计不等宽的局部结构，使得振动组件100第四谐振峰位于15kHz-18kHz范围，各个镂空区域面积S i与各个镂空区域部分振膜厚度Hi比值为面积厚度比μ范围为100mm-1000mm；任意两个弹性元件110的镂空区域面积S ki与S ji之比γ范围为0.1-10；加强件120的加强部分与加强件120横向面积比β为0.1-0.8。
请参照图23，图23是根据本说明书一些实施例所示的具有不规则环形结构的振动组件的结构示意图。在一些实施例中，通过设计不同环形结构122的不同位置的局部结构，例如圆形、长方形、正方形、三角形、六边形、八边形、其他多边形、椭圆形以及其他不规则环形结构122，可以更灵活的控制环形结构122局部区域的尺寸、位置、形状，可以有效的调整调节加强件120的质量，可以调控总等效质量Mt发生改变，故形成质量Mt-弹簧Kt-阻尼Rt系统的谐振频率发生改变，进而使得振动组件100的第一谐振频率发生变化。通过调节加强件120刚度、加强件120质心分布，可调节Mt1-弹簧Kt1-阻尼Rt1系统，翻转运动的谐振频率，从而使得振动组件100第三谐振峰位置发生改变；使得条形结构124从中心向四周延伸不同位置刚度分布不同，实现一个3dB带宽可调的振动组件100第三谐振峰。同时可以有效的调节中心区域112的悬空区域数量以及面积大小，使得振动组件100的第四谐振峰位置与灵敏度发生改变。此外，通过设计不规则的结构，可以有效的避免应力集中，使得加强件120的变形更小。
在一些实施例中，参见图23，加强件120包括双环形结构，双环形结构包括位于内侧的第一环形结构1221和位于外侧的第二环形结构1222。在一些实施例中，第一环形结构1221和第二环形结构1222的形状可以不同。在一些实施例中，第一环形结构1221可以是曲线环形，第二环形结构1222可以是圆环形。在一些实施例中，通过设计不规则环形结构122，可以使得振动组件100第四谐振峰位于10kHz-18kHz范围，各个镂空区域面积S i与各个镂空区域部分振膜厚度H i比值为面积厚度比μ范围为150mm-700mm，任意两个振膜镂空区域面积S ki与S ji之比γ范围为0.25-4，加强件120的加强部分与加强件120横向面积比β为0.2-0.7。在一些实施例中，通过设计不规则环形结构122，使得振动组件100第四谐振峰位于15kHz-18kHz范围，各个镂空区域面积S i与各个镂空区域部分振膜厚度H i比值为面积厚度比μ范围为100mm-1000mm；任意两个弹性元件110的镂空区域面积S ki与S ji之比γ范围为0.1-10；加强件120的加强部分与加强件120横向面积比β为0.1-0.8。
请参照图24A-图24B，图24A是根据本说明书一些实施例中所示的具有台阶结构的条形结构的振动组件的结构示意图。图24B是根据本说明书另一些实施例中所示的具有台阶结构的条形结构的振动组件的结构示意图。在一些实施例中，参见图24A，通过设计具有台阶结构的条形结构124的加强件120，可保证控制中心区域112的镂空区域(影响振动组件100的第四谐振峰)、悬空区域1121(影响振动组件100的第二谐振峰)不变的情况下，改变加强件120的刚度、质量、质心分布，从而实现不改变振动组件100的第二谐振峰、第四谐振峰情况下，对振动组件100的第一谐振峰位置、第三谐振峰位置与带宽进行有效调节，可根据实际应用需求调节不同的频响曲线。
在一些实施例中，通过从厚度方向(即沿振动组件100的振动方向)，设计加强件120不同区域的厚度，实现根据实际所需的质量分布，可以不变化或者变化加强件120质量同时改变加强件120自身刚度，使得加强件120、弹性元件110为系统提供的刚度Kt 1发生改变，进一步使得质量Mt 1-弹簧Kt 1-阻尼 Rt 1系统，翻转运动的谐振频率发生改变，从而使得振动组件100的第三个谐振位置发生改变；进一步的，可以控制振动组件100的第三谐振峰的3dB带宽。
在一些实施例中，条形结构124可以具有多个沿弹性元件110的振动方向厚度不同的台阶，即条形结构124具有阶梯形状。在一些实施例中，多个条形结构中的至少一个具有阶梯形状。在一些实施例中，多个条形结构中全部具有阶梯形状。如图24B所示为具有阶梯形状的条形结构124的加强件120的结构，及其D-D剖面的剖面结构。定义加强件120结构最边缘台阶(即位于条形结构124的径向最外侧的第一台阶)厚度为h 1、次边缘台阶厚度为h 2……，中心台阶(即位于条形结构124的径向最内侧的第二台阶)厚度为h n，定义物理量∈为任意两个台阶厚度h j与h k(k＞j)的比值：
Figure PCTCN2022108479-appb-000026
定义物理量φ为加强件120结构最边缘台阶(即位于条形结构124的径向最外侧的第一台阶)厚度为h 1与中心台阶(及位于条形结构124的径向最内侧的第二台阶)厚度为h n的比值：
Figure PCTCN2022108479-appb-000027
在一些实施例中，任意两个台阶厚度h j与h k的比值∈取值范围为0.1-10。在一些实施例中，任意两个台阶厚度h j与h k的比值∈取值范围为0.1-8。在一些实施例中，任意两个台阶厚度h j与h k的比值∈取值范围为0.2-8。在一些实施例中，任意两个台阶厚度h j与h k的比值∈取值范围为0.1-7。在一些实施例中，任意两个台阶厚度h j与h k的比值∈取值范围为0.1-6。在一些实施例中，任意两个台阶厚度h j与h k的比值∈取值范围为0.2-6。在一些实施例中，任意两个台阶厚度h j与h k的比值∈取值范围为0.2-5。在一些实施例中，任意两个台阶厚度h j与h k的比值∈取值范围为0.25-4。
在一些实施例中，通过设计加强件120不同区域的厚度，可以调节加强件120的质量分布，从而在不变化或者变化加强件120质量的情况下改变加强件120自身刚度，使得加强件120、弹性元件110为系统提供的刚度Kt 1发生改变，从而调节振动组件100的第三个谐振峰的位置，并对振动组件100的第三谐振峰的3dB带宽进行控制。
图24C是根据本说明书另一些实施例所示的振动组件的频响曲线，通过对振动组件进行结构设计，可以使得振动组件的第二谐振峰220和第三谐振峰230合并，使得振动组件的频响曲线仅体现出两个谐振峰。如图24C所示分别为∈＝1、∈＝0.68、∈＝0.5对应的振动组件的频响曲线。如图24C所示，∈＝1、∈＝0.68、∈＝0.5对应的频响曲线的中高频谐振峰(如，第二谐振峰220和第三谐振峰230合并后的谐振峰)的位置不同，在该谐振峰处的3dB带宽也不同，并且随着∈取值变小，振动组件的中高频谐振峰(如，第二谐振峰220和第三谐振峰230合并后的谐振峰)的谐振频率逐渐增加，3dB带宽逐渐增大。因此，通过调整∈的取值，即可调整振动组件的中高频谐振峰的频率位置以及3dB带宽。在一些实施例中，任意两个台阶厚度h j与h k的比值∈取值范围为0.25-4，可以使得振动组件的中高频谐振峰位于3000Hz-12000Hz范围内，并且该谐振峰具有较大的3dB带宽。
对应于某些需要低Q值宽带宽的振动组件100频响，可设计较大质量集中于加强件120的靠近中心的位置。在一些实施例中，加强件120结构最边缘台阶厚度为h 1与中心台阶厚度为h n的比值φ取值范围为0.1-1。在一些实施例中，加强件120结构最边缘台阶厚度为h 1与中心台阶厚度为h n的比值φ取值范围为0.2-0.8。在一些实施例中，加强件120结构最边缘台阶厚度为h 1与中心台阶厚度为h n的比值φ取值范围为0.2-0.6。在一些实施例中，加强件120结构最边缘台阶厚度为h 1与中心台阶厚度为h n的比值φ取值范围为0.2-0.4。
对应于某些需要高Q值窄带宽的振动组件100频响，可设计较大质量集中于加强件120的边缘区域。在一些实施例中，加强件120结构最边缘台阶厚度为h 1与中心台阶厚度为h n的比值φ取值范围为1-10。在一些实施例中，加强件120结构最边缘台阶厚度为h 1与中心台阶厚度为h n的比值φ取值范围为1.2-6。在一些实施例中，加强件120结构最边缘台阶厚度为h 1与中心台阶厚度为h n的比值φ取值范围为2-6。在一些实施例中，加强件120结构最边缘台阶厚度为h 1与中心台阶厚度为h n的比值φ取值范围为3-6。在一些实施例中，加强件120结构最边缘台阶厚度为h 1与中心台阶厚度为h n的比值φ取值范围为4-6。在一些实施例中，加强件120结构最边缘台阶厚度为h 1与中心台阶厚度为h n的比值φ取值范围为5-6。
请参照图25A-图25C，图25A-图25C是根据本说明书一些实施例所示的不同形状加强件的振动组件的结构示意图。其中图25A中的加强件120的形状为矩形，环形结构122为单环矩形结构，条形结构124为梯形结构；图21B中的加强件120的形状为矩形，环形结构122为双环矩形结构，条形结构124为梯形结构；图21C中的加强件120的形状为六边形形，环形结构122为单环六边形结构，条形结构124为梯形结构。在一些实施例中，振动组件100的加强件120的形状可以与弹性元件110的形状相匹配。弹性元件110的结构也可以有多种，例如圆形、方形、多边形等。对应的加强件120的形状也可以设计成不同的形状，包括但不限于圆形、方形(例如，长方形、正方形)、三角形、六边形、八边形、其他多边形、 椭圆形以及其他不规则的结构。
不同形状的加强件120与不同形状的弹性元件110可以灵活设计，以改变加强件120的质量及刚度、振动组件100的质量与刚度等，从而改变振动组件100的谐振频率。
在一些实施例中，加强件120的形状与弹性元件110的形状均可以包括多种不同的形状，此时对于中心区域112向四周延伸的条形结构124，可以针对其横向设计不同的宽度、不同的形状；也可以对环形结构122进行设计，设计不同形状、数量、尺寸的环形结构122，环形结构122可以设计为整个环形、也可设计为局部环形结构122；不同环形结构122将条形结构124划分成不同区域，在不同区域中，由中心向四周不同区域条形结构124可以是连续的、交错的，数量可以相等，也可以不相等。在一些实施例中，环形结构122也可以设计为圆形、方形(例如，长方形、正方形)、三角形、六边形、八边形、其他多边形、椭圆形以及其他不规则的结构。
在一些实施例中，可以通过设计包括不同形状的加强件120的振动组件100，使得振动组件100第四谐振峰位于10kHz-18kHz范围；各个镂空区域面积Si与各个镂空区域部分弹性元件110的厚度Hi比值为面积厚度比μ范围为150mm-700mm；任意两个弹性元件110的悬空区域面积S ki与S ji之比γ范围为0.25-4；镂空区域面积与加强件120的横向面积比β为0.2-0.7。在一些实施例中，可以通过设计包括不同形状的加强件120的振动组件100，使得振动组件100第四谐振峰位于10kHz-18kHz范围；各个镂空区域面积Si与各个镂空区域部分弹性元件110的厚度Hi比值为面积厚度比μ范围为100mm-1000mm；任意两个弹性元件110的悬空区域面积S ki与S ji之比γ范围为0.1-10；镂空区域面积与加强件120的横向面积比β为0.1-0.8。
请参照图26A-图26D，图26A-图26D是根据本说明书一些实施例所示的包括局部质量结构的振动组件100的结构示意图。其中图26A所示为双弹性连接的局部质量结构126，图26B所示为四弹性连接的局部质量结构126，图26C所示为S形四弹性连接的局部质量结构126，图26D所示为S形四弹性连接的不规则的局部质量结构126。在一些实施例中，可以通过在中心区域112的悬空区域设计局部质量结构126，从而灵活的调节各个镂空区域的等效质量Mm i、等效刚度Ka i与Ka i’、等效阻尼Ra i与Ra i’，从而使得振动组件100第四谐振峰得到有效的调节。同时通过设计局部质量结构126，还可以较大范围调节加强件120的质量、刚度，从而调节振动组件100的第一谐振峰和第三谐振峰。
在一些实施例中，局部质量结构126可以通过双弹性结构环向连接至相邻条形结构124上(如图26A所示)，也可通过双弹性结构环向连接至相邻环形结构122上。在另一些实施例中，各个局部质量结构126还可以与条形结构124或环形结构122均不连接，仅与弹性元件110连接。在一些实施例中，局部质量结构126还可以一部分与弹性元件110连接，另一部分与环形结构122和/或条形结构124连接。
在一些实施例中，局部质量结构126还可以通过四弹性结构同时连接于相邻条形结构124和环形结构122上(如图26B所示)。
在一些实施例中，弹性结构平面形状可以是规则的形状(如图26A与图26B所示)，也可以是不规则形状(如图26C所示)。
在一些实施例中，局部质量结构126可以是规则形状(如图26A-图26C所示)，也可以是任意不规则形状(如图26D所示)。
在一些实施例中，通过设计局部质量结构126的尺寸、位置、数量、形状，弹性连接结构尺寸、位置、数量、形状，可以使得振动组件100的第四谐振峰位于10kHz-18kHz范围；各个镂空区域面积S i与各个镂空区域部分弹性元件110的厚度H i比值为面积厚度比μ范围为150mm-700mm；任意两个弹性元件110的悬空区域面积S ki与S ji之比γ范围为0.25-4；镂空区域面积与加强件120的横向面积比β为0.2-0.7。在一些实施例中，通过设计局部质量结构126的尺寸、位置、数量、形状，弹性连接结构尺寸、位置、数量、形状，可以使得振动组件100的第四谐振峰位于10kHz-18kHz范围；各个镂空区域面积S i与各个镂空区域部分弹性元件110的厚度H i比值为面积厚度比μ范围为100mm-1000mm；任意两个弹性元件110的悬空区域面积S ki与S ji之比γ范围为0.1-10；镂空区域面积与加强件120的横向面积比β为0.1-0.8。
图26E是根据本说明书一些实施例所示的加强件的剖面结构示意图。如图26E所示，加强件120可以包括中心连接部123、加强部分125和镂空部分127。在一些实施例中，镂空部分127可以通过在加强件120上镂刻掉部分材料的方式获得，加强件120上未被镂刻掉的部分即构成加强部分125。在一些实施例中，镂空部分127可以被构造为圆形。在一些实施例中，镂空部分127也可以被构造为其它形状。在一些实施例中，中心连接部123与加强部分125沿弹性元件110的振动方向具有不同的厚度。在一些实施例中，中心连接部123沿弹性元件110的振动方向的厚度可以大于加强部分125沿弹性元件110的振动方向的厚度。
本说明书实施例还提供了一种扬声器，扬声器具有本说明书实施例提供的振动组件，通过合理设置振动组件(例如，弹性元件、加强件)的结构及参数，可以使得扬声器在人耳可听范围内(如，20kHz- 20kHz)具有多个谐振峰，从而提升扬声器的频带和灵敏度，并能提高扬声器输出的声压级。
图27是根据本说明书的一些实施例所示的扬声器示例性结构图。在一些实施例中，参见图27，扬声器2700可以包括壳体2730、驱动组件2720以及上述的振动组件2710。其中，驱动组件2720能够基于电信号产生振动，振动组件2710能够接收驱动组件2720的振动而发生振动。壳体2730形成腔体，驱动组件2720与振动组件2710设置于腔体内。其中，振动组件2710的结构可以与本说明书实施例中的任意一种振动组件相同。
在一些实施例中，振动组件2710主要包括弹性元件2711和加强件2712。其中，弹性元件2711主要包括中心区域2711A、设置于中心区域2711A外围的折环区域2711B，以及设置于折环区域2711B外围的固定区域2711C。弹性元件2711被配置为沿垂直于中心区域2711A的方向振动。加强件2712与中心区域2711A连接。加强件2712包括加强部分和多个镂空部分，加强件2712与弹性元件2711的振动在人耳可听范围(20Hz-20kHz)内产生至少两个谐振峰。
驱动组件2720可以是具有能量转换功能的声学器件。在一些实施例中，驱动组件2720可以与扬声器2700的其他组件(如，信号处理器)电连接以接收电信号，并将电信号转换为机械振动信号，该机械振动可以传递至振动组件2710，以使振动组件2710产生振动，从而推动腔体内的空气发生振动，产生声音。
在一些实施例中，驱动组件2720可以包括驱动单元2722与振动传递单元2724。其中，驱动单元2722可以与扬声器2700的其他组件(如，信号处理器)电连接以接收电信号，并将电信号转换为机械振动信号。振动传递单元2724连接于驱动单元2722与振动组件2710之间，用于将驱动单元2722产生的振动信号传递至振动组件2710。
在一些实施例中，驱动单元2722可以包括但不限于动圈式声学驱动器、动铁式声学驱动器、静电式声学驱动器或压电式声学驱动器。在一些实施例中，动圈式声学驱动器可以包括产生磁场的磁性件以及设置在磁场中的线圈，线圈通电后可以在磁场中产生振动从而将电能转换为机械能。在一些实施例中，动铁式声学驱动器可以包括产生交变磁场的线圈以及设置于交变磁场中的铁磁件，铁磁件在交变磁场的作用下产生振动从而将电能转换为机械能。在一些实施例中，静电式声学驱动器可以通过设置于其内部的静电场驱动膜片振动，从而将电能转换为机械能。在一些实施例中，压电式声学驱动器可以通过设置于其内部的压电材料在电致伸缩效应的作用下，将电能转换为机械能。在一些实施例中，驱动单元2722可以是如图48所示的压电式声学驱动器，压电式声学驱动器由多个压电梁27221组成，多个压电梁27221之间通过弹性连接件27222互相连接。在一些实施例中，为了最大限度地利用空间，提高驱动单元2722输出的驱动力，多个压电梁27221和/或弹性连接件应尽可能地铺满固定端所围成的平面，即多个压电梁和弹性连接件之间的缝隙宽度27223应尽可能小，如不大于25μm。
在一些实施例中，驱动单元2722和振动传递单元2724可以位于振动组件的振动方向的同一侧。在一些实施例中，振动传递单元2724沿中心区域2711A的振动方向的一端与驱动单元2722相连，振动传递单元2724远离驱动单元2722的另一端可以与振动组件2710的中心区域2711A相连。在另一些实施例中，加强件2712可以包括中心连接部27121，中心连接部27121覆盖中心区域2711A的中心。在一些实施例中，振动传递单元2724远离驱动单元2722的另一端可以与中心连接部27121直接相连，即振动传递单元2724通过中心连接部27121与中心区域2711A连接。在一些实施例中，振动传递单元2724远离驱动单元2722的另一端可以与中心连接部27121间接相连，即振动传递单元2724与中心区域2711A直接连接，并通过中心区域2711A与中心连接部27121连接。在一些实施例中，振动传递单元2724的尺寸可以与中心连接部27121的尺寸相同或大致相同(例如，尺寸差值在10％以内)。
在一些实施例中，振动传递单元2724与中心区域2711A相连的一端的中心与中心区域2711A的中心沿弹性元件2711的振动方向的投影重合或大致重合，通过这样的设置，一方面可以提升弹性元件2711振动的均匀性与稳定性，另一方面可以控制扬声器2700输出的第三谐振峰在本说明书实施例中所述的频率范围(例如，5000Hz-12000Hz)以内。本说明书实施例中，大致重合是指振动传递单元2724与中心区域2711A相连的一端的中心与中心区域2711A的中心之间的距离不超过中心区域2711A直径的5％。在另一些实施例中，当振动传递单元2724通过加强件2712的中心连接部与中心区域2711A连接时，由于振动传递单元2724的尺寸与中心连接部的尺寸相匹配(例如，尺寸相同)，因此振动传递单元2724与中心连接部相连的一端的中心与中心连接部27121的中心相重合或大致重合，此时中心连接部的中心也可以与中心区域2711A的中心沿弹性元件2711的振动方向的投影重合或大致重合。加强件2712的中心连接部的具体内容可以参照加强件120的中心连接部123的相关描述。
在一些实施例中，振动组件2710能够接收振动传递单元2724传递的力与位移从而推动空气运动，产生声音。在一些实施例中，振动组件2710的结构可以与振动组件100相同。
在一些实施例中，折环区域2711B可以设计有特性形状的花纹，从而破坏弹性元件2711的折环 区域2711B在相应频率段的振型，避免弹性元件2711局部分割振动导致的声相消的发生，使振动组件2710具有较平坦的声压级曲线。同时通过花纹设计使得弹性元件2711局部刚度增加。
在一些实施例中，通过调节加强件2712的结构，可以调节振动组件2710的模态振型。
在一些实施例中，加强件2712包括一个或多个环形结构以及一个或多个条形结构，一个或多个条形结构中的每一个与一个或多个环形结构中的至少一个连接；其中，一个或多个条形结构中的至少一个朝向中心区域2711A的中心延伸。一个或多个环形结构所在区域以及一个或多个条形结构所在的区域共同构成加强部分。在加强件2712的最大轮廓的沿弹性元件2711的振动方向的投影范围内，一个或多个环形结构以及一个或多个条形结构未覆盖的区域构成镂空部分。加强件2712的环形结构与条形结构的具体内容可以参照本说明书其它地方关于环形结构和条形结构的相关描述。
在一些实施例中，通过合理的设置加强件2712，在中心区域2711A中设置多个镂空区域使弹性元件2711的中心区域2711A的局部刚度实现可控调节，从而利用振动组件2710的弹性元件2711的中心区域2711A的各镂空区域的分割振型实现对振动组件2710输出的谐振峰的可控调节，使振动组件2710具有较平坦的声压级曲线。在一些实施例中，环形结构与条形结构相互配合，使得加强件2712具有合适比例的加强部分和镂空部分(即镂空部)，减小了加强件2712的质量，提升了振动组件2710的整体灵敏度。在一些实施例中，通过设计环形结构与条形结构的形状、尺寸和数量，可以调节振动组件2710的多个谐振峰(例如，第三谐振峰、第四谐振峰等)的位置及带宽，从而控制振动组件2710的振动输出。
在一些实施例中，加强件2712的质量、弹性元件2711的质量、等效空气质量、驱动端等效质量组合形成总等效质量Mt，各部分等效阻尼形成总的等效阻尼Rt，弹性元件2711为系统提供刚度Kt，形成一个质量Mt-弹簧Kt-阻尼Rt系统，当驱动组件2720的激励频率接近该系统的共振频率时，振动组件2710频响曲线中出现一个谐振峰，即振动组件2710的第一谐振峰。在一些实施例中，第一谐振峰的频率范围包括180Hz-3000Hz。在一些实施例中，第一谐振峰的频率范围包括200Hz-3000Hz。在一些实施例中，第一谐振峰的频率范围包括200Hz-2500Hz。在一些实施例中，第一谐振峰的频率范围包括200Hz-2000Hz。在一些实施例中，第一谐振峰的频率范围包括200Hz-1000Hz。
在一些实施例中，折环区域2711B、连接区域2711D以及中心区域2711A设置有加强件2712的区域与折环区域2711B之间的悬空区域2711E形成等效质量Ms、等效刚度Ks、等效阻尼Rs，形成一个质量Ms-弹簧Ks-阻尼Rs系统，当驱动组件2720的激励频率接近该系统的共振频率时，振动组件2710频响曲线中出现一个谐振峰，即振动组件2710的第二谐振峰。在一些实施例中，振动组件2710的第二谐振峰的频率范围可以包括3000Hz-7000Hz。在一些实施例中，振动组件2710的第二谐振峰的频率范围可以包括3000Hz-6000Hz。在一些实施例中，振动组件2710的第二谐振峰的频率范围可以包括4000Hz-6000Hz。在一些实施例中，通过设置弹性元件2711的参数(例如，折环区域2711B、悬空区域2711E的参数)即可使得振动组件2710的第二谐振峰位于上述频率范围内。
在一些实施例中，加强件2712、连接区域2711D、折环区域2711B、中心区域2711A设置有加强件2712的区域与折环区域2711B之间的悬空区域2711E、等效空气质量、驱动组件2720等效质量组合形成总等效质量Mt1，各部分等效阻尼形成总的等效阻尼Rt1，加强件2712、弹性元件2711为系统提供刚度Kt1，形成一个质量Mt1-弹簧Kt1-阻尼Rt1系统，当驱动组件2720的激励频率接近该系统的速度共振频率时，振动组件2710频响曲线中出现一个谐振峰，即振动组件2710的第三谐振峰。在一些实施例中，第三谐振峰的频率范围可以包括5000Hz-12000Hz。在一些实施例中，第三谐振峰的频率范围可以包括6000Hz-12000Hz。在一些实施例中，第三谐振峰的频率范围可以包括6000Hz-10000Hz。
在一些实施例中，加强件2712对应中心区域2711A具有不少于一个的镂空区域，具有不同谐振频率的各个镂空区域振动，从而使得在振动组件2710频响曲线上有不少于1个的高频谐振峰。在一些实施例中，通过设计加强件2712的结构，可以使得各个镂空区域的谐振频率相等或接近(例如，差值小于4000Hz)，从而使得在振动组件2710的频响曲线上具有一个输出声压级较大的高频谐振峰，即为振动组件2710的第四谐振峰。在一些实施例中，第四谐振峰的频率范围可以包括8000Hz-20000Hz。在一些实施例中，第四谐振峰的频率范围可以包括10000Hz-18000Hz。在一些实施例中，第四谐振峰的频率范围可以包括12000Hz-18000Hz。在一些实施例中，第四谐振峰的频率范围可以包括15000Hz-18000Hz。在另一些实施例中，第四谐振峰的频率范围也可以大于20000Hz。在另一些实施例中，各个镂空区域的谐振频率不同、并且在高频范围(如8000Hz-20000Hz)不同频率段不同镂空区域振动相位不同，形成声音叠加抵消的效果，可以使得振动组件2710不输出第四谐振峰。
在一些实施例中，通过设计振动组件2710的结构，可以使得扬声器2700在人耳可听范围(如，20Hz-20kHz)内体现出2个、3个或4个谐振峰。
在一些实施例中，通过设计振动组件2710的结构与尺寸，包括加强件2712的整体尺寸、条形结构数量及尺寸、条形结构布置位置、悬空区域2711E的面积、折环区域2711B的结构(例如折环的宽度、 拱高、拱形、花纹等)、连接区域2711D面积，可以设计振动组件2710第二谐振峰与第三谐振峰的频率差。在一些实施例中，当振动组件2710第二谐振峰与第三谐振峰的频率差小于2000Hz时，第二谐振峰和第三谐振峰趋于合并，即第二谐振峰与第三谐振峰体现为一个谐振峰，可使得中高频率段(3000Hz-10000Hz)具有较高的灵敏度，并能大大提高合并后的谐振峰的带宽。在一些实施例中，第四谐振峰的频率范围可以大于20000Hz，即在人耳可听范围内不具有第四谐振峰。在一些实施例中，第二谐振峰与第三谐振峰的频率差小于2000Hz且在人耳可听范围内不具有第四谐振峰时，振动组件2710振动时，在人耳可听范围内有且仅有2个谐振峰，且其中至少一个谐振峰的3dB带宽不低于1000Hz。其中，3dB带宽指的是谐振峰对应的声压级幅值(例如图7D中的纵坐标)降低3dB时对应的频带(例如图7D中的横坐标)宽度。在一些实施例中，振动组件2710振动时，在人耳可听范围内的至少一个谐振峰的3dB带宽不低于1500Hz。在一些实施例中，振动组件2710振动时，在人耳可听范围内的至少一个谐振峰的3dB带宽不低于1000Hz。在一些实施例中，振动组件2710振动时，在人耳可听范围内的至少一个谐振峰的3dB带宽不低于500Hz。
在一些实施例中，通过加强件2712与弹性元件2711的设计，可以使得振动组件2710在可听声范围(20Hz-20000Hz)内出现所需的高阶模态，在振动组件2710的频响曲线上出现上述第一谐振峰、第二谐振峰、第三谐振峰和第四谐振峰，即在20Hz-20000Hz的频率范围内振动组件2710的频响曲线的谐振峰数量为4个。
在一些实施例中，通过设计加强件2712与弹性元件2711的结构，振动组件2710在人耳可听声范围(20Hz-20000Hz)内也可以有且仅有3个谐振峰。例如，当振动组件2710的第二谐振峰与第三谐振峰的频率差小于2000Hz时，振动组件2710频响声压级曲线上，第二谐振峰与第三谐振峰体现为一个谐振峰，与第一谐振峰、第四谐振峰共同组成振动组件2710在人耳可听声范围(20Hz-20000Hz)内的3个谐振峰。又例如，加强件2712对应中心区域2711A具有不少于一个的悬空区域，当使得各个镂空区域的谐振频率高于可听声范围，或者各个镂空区域的谐振频率不同、并且在高频范围(10000Hz-18000Hz)不同频率段不同悬空区域振动相位不同、形成声音叠加抵消的效果时，可获得一个高频滚降的效果，在振动组件2710声压级频响曲线中不体现第四个谐振峰，此时，第一谐振峰、第二谐振峰和第三谐振峰组成振动组件2710在人耳可听声范围(20Hz-20000Hz)内的3个谐振峰。
在一些实施例中，通过设计加强件2712或弹性元件2711的结构，不仅可以调整多个谐振峰的频率，还可以调整多个谐振峰(例如，第三谐振峰)的3dB带宽以及扬声器的Q值。
在一些实施例中，通过设计条形结构沿振动方向的投影形状的两个侧边之间的夹角θ，可以调整扬声器2700输出的第三谐振峰的3dB带宽和扬声器2700的Q值。在一些实施例中，当需要扬声器2700表现出低Q值宽带宽的频响特性时，条形结构的夹角θ可以具有较大的取值。在一些实施例中，条形结构的夹角θ的范围可以为-90°至150°，使得扬声器2700具有较低的Q值，并且扬声器2700输出的第三谐振峰的3dB带宽不小于1000Hz。在一些实施例中，条形结构的夹角θ的范围可以为-0°至60°，使得扬声器2700具有较低的Q值，并且扬声器2700输出的第三谐振峰的3dB带宽不小于1000Hz。
在一些实施例中，当需要扬声器2700表现出高Q值窄带宽的频响特性时，可设计较小的条形结构的夹角θ。在一些实施例中，条形结构的夹角θ的范围可以为-150°至90°，使得扬声器2700具有较高的Q值，并且扬声器2700输出的第三谐振峰的3dB带宽不大于1000Hz。在一些实施例中，条形结构的夹角θ的范围可以为-60°至0°，使得扬声器2700具有较高的Q值，并且扬声器2700输出的第三谐振峰的3dB带宽不大于1000Hz。
在一些实施例中，通过设计加强件2712沿弹性元件2711的振动方向的投影形状的半轮廓的内侧和外侧的面积比值为τ，可以调整扬声器2700输出的第三谐振峰的3dB带宽和扬声器2700的Q值。当需要扬声器2700表现出低Q值宽带宽的频响特性时，可设计较大质量集中于加强件2712的中心区域。在一些实施例中，加强件2712沿弹性元件2711的振动方向的投影形状的半轮廓的内侧和外侧的面积比值τ的取值范围可以为0.3-2，使得扬声器2700具有较低的Q值，并且扬声器2700输出的第三谐振峰的3dB带宽不小于1000Hz。在一些实施例中，加强件2712沿弹性元件2711的振动方向的投影形状的半轮廓的内侧和外侧的面积比值τ的取值范围可以为0.5-1.2，使得扬声器2700具有较低的Q值，并且扬声器2700输出的第三谐振峰的3dB带宽不小于1000Hz。当需要扬声器2700表现出高Q值窄带宽的频响特性时，可设计较大质量集中于加强件2712边缘区域。在一些实施例中，加强件2712沿弹性元件2711的振动方向的投影形状的半轮廓的内侧和外侧的面积比值τ的取值范围可以为1-3，使得扬声器2700具有较高的Q值，并且扬声器2700输出的第三谐振峰的3dB带宽不大于1000Hz。在一些实施例中，加强件2712沿弹性元件2711的振动方向的投影形状的半轮廓的内侧和外侧的面积比值τ的取值范围可以为1.2-2.8，使得扬声器2700具有较高的Q，并且扬声器2700输出的第三谐振峰的3dB带宽不大于1000Hz。
在一些实施例中，一个或多个条形结构中的至少一个具有多个沿弹性元件2711的振动方向厚度不同的台阶，台阶包括位于条形结构的径向最外侧的第一台阶和位于条形结构的径向最内侧的第二台阶。 在一些实施例中，通过设计第一台阶和第二台阶的厚度比值φ，可以调整扬声器2700输出的第三谐振峰的3dB带宽和扬声器2700的Q值。当需要扬声器2700表现出低Q值宽带宽的频响特性时，可设计较大质量集中于加强件2712的靠近中心的位置。在一些实施例中，第一台阶和第二台阶的厚度比值φ的取值范围为0.1-1，使得扬声器2700具有较低的Q值，并且扬声器2700输出的第三谐振峰的3dB带宽不小于1000Hz。在一些实施例中，第一台阶和第二台阶的厚度比值φ的取值范围为0.2-0.8，使得扬声器2700具有较低的Q值，并且扬声器2700输出的第三谐振峰的3dB带宽不小于1000Hz。当需要扬声器2700表现出高Q值窄带宽的频响特性时，可设计较大质量集中于加强件2712的边缘区域。在一些实施例中，第一台阶和第二台阶的厚度比值φ的取值范围为1-10，使得扬声器2700具有较高的Q值，并且扬声器2700输出的第三谐振峰的3dB带宽不大于1000Hz。在一些实施例中，第一台阶和第二台阶的厚度比值φ的取值范围为1.2-6，使得扬声器2700具有较高的Q值，并且扬声器2700输出的第三谐振峰的3dB带宽不大于1000Hz。
在一些实施例中，壳体2730可以为内部中空(即设有腔体)的规则或不规则的立体结构，例如，壳体2730可以是中空的框架结构体，包括但不限于矩形框、圆形框、正多边形框等规则形状，以及任何不规则形状。在一些实施例中，壳体2730可以采用金属(例如，不锈钢、铜等)、塑料(例如，聚乙烯(PE)、聚丙烯(PP)、聚氯乙烯(PVC)、聚苯乙烯(PS)及丙烯腈─丁二烯─苯乙烯共聚合物(ABS)等)、复合材料(如金属基复合材料或非金属基复合材料)等。在一些实施例中，驱动组件2720可以位于壳体2730形成的声学腔内或者至少部分悬空设置于壳体2730的声学腔内。
在一些实施例中，弹性元件2711的周侧可以与壳体2730的内壁连接，从而将壳体2730形成的腔体分隔为多个腔体。具体地，弹性元件2711沿其振动方向，以弹性元件2711为界，将壳体2730的内腔分为分别位于弹性元件2711两侧的前腔2731与后腔2733。在一些实施例中，前腔2731位于弹性元件2711远离驱动单元2722的一侧。
在一些实施例中，后腔2733位于弹性元件2711靠近驱动单元2722的一侧，即驱动组件2720可以设置于后腔2733中。
在一些实施例中，前腔2731和后腔2733对应的壳体2730的侧壁上可以开设有一个或多个孔部。示例性的，前腔2731远离弹性元件2711的一侧的壳体2730上设置有第一孔部2732，前腔2731通过第一孔部2732与扬声器2700的外界连通；后腔2733远离弹性元件2711的壳体2730上设置有第二孔部2734，后腔2733通过第二孔部2734与扬声器2700的外界连通。振动组件2710产生的声音可以向前腔2731和/或后腔2733辐射，并通过壳体2730上的第一孔部2732和/或第二孔部2734传递至扬声器2700的外部。
在一些实施例中，一个或多个孔部(例如，第二孔部2734)上可以设置阻尼网或防尘布(例如，阻尼网，)。在一些实施例中，阻尼网可以调节(例如，降低)从孔部泄漏的声波的幅度，从而改善扬声器2700的性能。
在一些实施例中，扬声器2700还可以包括支撑元件2740，支撑元件2740分别与壳体2730、固定区域2711C连接。在一些实施例中，参见图27，振动组件2710的弹性元件2711的固定区域2711C位于连接区域2711D的外围，并环绕连接于连接区域2711D的周侧。支撑元件2740可以位于固定区域2711C沿中心区域2711A的振动方向的任一表面，并通过固定区域2711C与连接区域2711D连接。
在一些实施例中，支撑元件2740可以嵌设于壳体2730的内壁中，并与壳体2730连接以支撑弹性元件2711。当支撑元件2740嵌设于壳体2730内壁中时，壳体2730的内壁上可以设置有与支撑元件2740匹配的孔洞，使得支撑元件2740可以放置于该孔洞内，以实现支撑元件2740的嵌设。
在一些实施例中，参见图27，支撑元件2740也可以设置于壳体2730形成的腔体内，支撑元件2740沿振动组件2710的振动方向的下表面(靠近驱动单元2722的表面)或周侧面与壳体2730连接以支撑弹性元件2711。在一些实施例中，当支撑元件2740设置于壳体2730形成的腔体内时，壳体2730的内壁可以设置成具有与支撑元件2740匹配的突出结构，使得支撑元件2740可以设置于该突出结构沿振动方向的表面，以实现支撑元件2740与壳体2730的连接。这种设置方式下，通过将支撑元件2740设置于壳体2730形成的腔体内，可以防止扬声器2700使用过程中支撑元件2740被剐蹭损坏，进而防止扬声器2700(尤其是振动组件2710)的损坏。
在一些实施例中，支撑元件2740可以是不易变形的刚性结构，在振动组件2710振动过程中仅为弹性元件2711提供支撑作用。在一些实施例中，为了进一步降低振动组件2710振动时的系统刚度，提高扬声器2700的顺性，可以将支撑元件2740设置为易于变形的柔性结构，为振动组件2710提供振动时的额外位移量。
在一些实施例中，支撑元件2740在响应于弹性元件2711的振动信号时可以产生形变，为弹性元件2711提供沿其振动方向的位移量，从而提高弹性元件2711在其振动方向上产生的总位移量，进一步提高振动组件2710的低频灵敏度。在一些实施例中，支撑元件2740的材质可以包括刚性材料、半导体材料、 有机高分子材料、胶类材料等中的一种或多种。在一些实施例中，刚性材料可以包括但不限于金属材料、合金材料等。半导体材料可以包括但不限于硅、二氧化硅、氮化硅、碳化硅等中的一种或多种。有机高分子材料可以包括但不限于聚酰亚胺(PI)、派瑞林(Parylene)、聚二甲基硅氧烷(Polydimethylsiloxane，PDMS)、水凝胶等中的一种或多种。胶类材料可以包括但不限于凝胶类、有机硅胶、丙烯酸类、聚氨酯类、橡胶类、环氧类、热熔类、光固化类等中的一种或多种。在一些实施例中，为了增强支撑元件2740与弹性元件2711之间的连接力，提高支撑元件2740与弹性元件2711之间的可靠性，支撑元件2740的材质可以是有机硅粘接类胶水、有机硅密封类胶水等。在一些实施例中，支撑元件2740在平行于增强区域的振动方向的截面上的截面形状可以是长方形、圆形、椭圆形、五边形等规则和/或不规则几何形状。同时通过设置具有柔性结构的支撑元件2740，不仅可以改变振动组件2710的振动特性，还能避免弹性元件2711直接与壳体2730接触，减小弹性元件2711直接与壳体2730连接端应力集中(壳体一般为刚性体)，从而进一步保护弹性元件2711。
图28是根据本说明书一些实施例所示的扬声器的结构示意图。需要说明的是，由于图28所示的扬声器2800具有与图27所示的扬声器2700相似的结构，扬声器2800可以看成是在扬声器2700的基础上所进行的修改，因此，在本说明书中，扬声器2800和扬声器2700中结构或功能相同的部件采用了相同编号，图28中未进行标记的部件可以在图27中找到。
如图28所示，壳体2730可以包括前腔板2735、后腔板2736以及侧板2737，前腔板2735、后腔板2736以及侧板2737可以围成壳体2730的腔体。在一些实施例中，壳体2730的腔体可以包括位于振动组件2710一侧的前腔2731以及一个或多个位于振动组件2710另一侧的后腔2733，一个或多个后腔2733中的至少一个至少由驱动组件2720、振动组件2710以及后腔板2736围合而成。在一些实施例中，后腔2733的数量可以为一个。例如，后腔2733可以只包括第二后腔27332。在一些实施例中，后腔2733的数量可以为两个。例如，两个后腔2733可以分别是第一后腔27331和第二后腔27332。在一些实施例中，后腔2733的数量还可以是三个、四个、五个等。作为示例性说明，驱动组件2720、振动组件2710、后腔板2736以及侧板2737的部分能够围合形成第二后腔27332。具体而言，振动组件2710可以将壳体2730的腔体分隔成了与前腔板2735对应的前腔2731和以及与后腔板2736对应的后腔2733，驱动组件2720可以设置在后腔2733内，例如，驱动组件2720固定连接于后腔板2736上。在一些实施例中，后腔板2736可以是PCB板、塑料板、金属板等。在一些实施例中，壳体2730可以为一体式结构，即前腔板2735、后腔板2736以及侧板2737为一体式设计。在一些实施例中，前腔板2735、后腔板2736以及侧板2737可以通过胶接、焊接、卡接等方式连接形成壳体2730。关于振动组件2710和驱动组件2720以及壳体2730的更多描述可以参照本说明书其他地方(例如，图27)的描述，在此不再赘述。
图29是根据本说明书一些实施例所示的扬声器及其等效模型示意图。
如图29所示，扬声器2800各个部分均可等效为质量-弹簧-阻尼系统。在一些实施例中，驱动组件2720的振动表面可以构成一个或多个后腔2733中的至少一个的侧壁的至少一部分。具体地，驱动组件2720可以将后腔2733分成第一后腔27331和第二后腔27332，驱动组件2720朝向第一后腔27331的振动表面和朝向第二后腔27332的振动表面可以分别构成第一后腔27331和第二后腔27332的侧壁。其中，第一后腔27331内的空气可以等效为一个质量-弹簧-阻尼系统，具有等效质量M 2、等效刚度K 2和等效阻尼R 2；第二后腔27332内的空气可以等效为一个质量-弹簧-阻尼系统，具有等效质量M 1、等效刚度K 1和等效阻尼R 1；前腔2731内的空气可以等效为一个质量-弹簧-阻尼系统，具有等效质量M 3、等效刚度K 3和等效阻尼R 3；振动组件2710可以等效为一个质量-弹簧-阻尼系统，具有等效质量Mv、等效刚度Kv和等效阻尼Rv；驱动组件2720可以等效为一个质量-弹簧-阻尼系统，具有等效质量Md、等效刚度Kd和等效阻尼Rd。在一些实施例中，驱动组件2720中的驱动单元2722可以包括如图48所示的压电式驱动器，根据本说明书其他地方的描述，压电式驱动器的多个压电梁和弹性连接件之间的缝隙宽度很小，在振动过程中，第二后腔27332内的空气无法通过缝隙快速流动到第一后腔27331，以平衡驱动组件2720两侧的气压，所以第一后腔27331和第二后腔27332相当于互不连通，第二后腔27332相当于一个密闭腔室。在一些实施例中，如图48所示，驱动组件2720可以包括多个振动单元，振动单元可以包括压电梁27221，多个振动单元中的压电梁27221可以通过弹性连接件27222连接。在一些实施例中，为了提高驱动组件2720输出的驱动力，更大程度地利用空间，多个振动单元之间形成的缝隙可以较小。在一些实施例中，多个振动单元之间形成的缝隙可以不大于25μm。在一些实施例中，多个振动单元之间形成的缝隙可以不大于20μm。在一些实施例中，多个振动单元之间形成的缝隙可以不大于15μm。在一些实施例中，多个振动单元之间形成的缝隙可以不大于10μm。在一些实施例中，多个振动单元之间形成的缝隙可以是指多个振动单元中的压电梁之间形成的缝隙。在一些实施例中，多个振动单元之间形成的缝隙可以是多个振动单元中的压电梁与弹性连接件27222之间形成的缝隙。
在一些实施例中，为了提高驱动组件2720输出的驱动力，更大程度地利用空间，驱动组件2720 的振动表面上可以具有较大面积的连续表面区域。在一些实施例中，驱动组件2720的振动表面上不小于90％的表面区域连续。在一些实施例中，驱动组件2720的振动表面上不小于95％的表面区域连续。在一些实施例中，驱动组件2720的振动表面上不小于98％的表面区域连续。在一些实施例中，驱动组件2720的振动表面的表面区域全部连续。
在一些实施例中，驱动组件2720可以包括压电膜。在一些实施例中，压电膜上可以没有缝隙，此时第二后腔27332完全密封。
第一后腔27331和第二后腔27332内的空气分别所等效的质量-弹簧-阻尼系统能够作用于驱动组件2720和振动组件2710上，由于第一后腔27331和第二后腔27332的体积较小，其内部空气的质量和阻尼可以忽略，使得第一后腔27331和第二后腔27332内的空气分别所等效的质量-弹簧-阻尼系统可以等效于空气弹簧系统，因此第一后腔27331和第二后腔27332内的空气所等效的质量-弹簧-阻尼系统对振动组件2710和驱动组件2720起主要作用的是空气弹簧的刚度。进一步地，第一后腔27331和第二后腔27332内的空气所等效的空气弹簧系统可以以附加刚度的形式作用于驱动组件2720和振动组件2710上。具体地，由于第一后腔27331和第二后腔27332的体积较小，第一后腔27331和第二后腔27332内的空气可压缩程度也较小，导致第一后腔27331和第二空腔27332内的空气附加到振动组件2710和驱动组件2720刚度较大，振动组件2710和驱动组件2720的振动位移较小，从而降低驱动组件2720和振动组件2710的输出，例如，降低驱动组件2720向振动组件2710的输出以及降低振动组件2710向空气的输出，这并不有利于提高扬声器的灵敏度。为了提高扬声器的灵敏度，在一些实施例中，可以通过调节第一后腔27331和第二后腔27332内的空气分别所等效的质量-弹簧-阻尼系统，来提高扬声器的灵敏度。在一些实施例中，由于振动组件2710的刚度相较于驱动组件2720的刚度较小，使得第一后腔27331和第二后腔27332内的空气所等效的空气弹簧系统对振动组件2710的影响相较于第一后腔27331和第二后腔27332内的空气所等效的空气弹簧系统对驱动组件2720的影响会更大，例如，振动组件2710的振动位移的降低幅度相较于驱动组件2720的振动位移的降低幅度更大。
在一些实施例中，可以在后腔板2736上开设若干通孔，一个或多个后腔2733可以通过若干通孔连通，以此提高扬声器的灵敏度。在一些实施例中，若干可以表示一个，也可以表示多个，即后腔板2736上开设的通孔数量可以是一个，也可以是多个。在一些实施例中，后腔2733的数量可以包括至少两个，至少两个后腔2733可以通过若干通孔连通。在一些实施例中，至少两个后腔2733可以包括第一后腔27331和第二后腔27332，可以通过若干通孔将第一后腔27331和第二后腔27332连通，从而可以调节(减小)后腔2733内的空气附加到振动组件2710和驱动组件2720的刚度，以增大振动组件2710和驱动组件2720的振动位移，从而提高扬声器2800的灵敏度。具体而言，可在后腔板2736上开设若干通孔将第一后腔27331和第二后腔27332连通后，可以使得后腔2733(第一后腔27331和第二后腔27332连通后形成的腔体)的空气可压缩程度变大，以使后腔2733内的空气附加到振动组件2710和驱动组件2720的刚度减小，具体请参见图30所示。
图30是根据本说明书一些实施例所示的扬声器及其等效模型示意图。
如图30所示，后腔板2736上可以开设有若干通孔27361，通过若干通孔27361可以将第一后腔27331和第二后腔27332连通，从而可以总体调节(即减小)后腔2733内的空气附加到振动组件2710和驱动组件2720的刚度，以增大振动组件2710和驱动组件2720的振动位移，提高扬声器2800的灵敏度。进一步地，当第一后腔27331和第二后腔27332连通成为一个后腔2733后，后腔2733的空气可以等效为一个质量-弹簧-阻尼系统，具有等效质量M、等效刚度K 1与K 2、等效阻尼R 1与R 2。前腔2731内的空气可以等效为一个质量-弹簧-阻尼系统，具有等效质量M 3、等效刚度K 3和等效阻尼R 3；振动组件2710可以等效为一个质量-弹簧-阻尼系统，具有等效质量Mv、等效刚度Kv和等效阻尼Rv，能够形成质量-弹簧-阻尼系统Mv-Kv-Rv；驱动组件2720可以等效为一个质量-弹簧-阻尼系统，具有等效质量Md、等效刚度Kd和等效阻尼Rd。其中，在后腔2733的空气所等效的质量-弹簧-阻尼系统中，等效质量Ma为后腔2733内的空气的等效质量(第一后腔27331和第二后腔27332内的空气的等效质量之和)，等效刚度K 1与K 2分别为第一后腔27331和第二后腔27332内的空气的等效刚度，等效阻尼R 1与R 2分别为第一后腔27331和第二后腔27332内的空气的等效阻尼。具体地，当第一后腔27331和第二后腔27332连通后，后腔2733内的空气可压缩程度变大，空气容易被压缩，使得后腔2733内的空气总体附加到振动组件2710和驱动组件2720上的刚度变小，进而增大了振动组件2710和驱动组件2720的振动位移，从而可以提高扬声器2800的灵敏度。
需要说明的是，后腔2733还可以包括更多后腔(例如，第三后腔、第四后腔等)，每两个相邻后腔之间均可以通过后腔板分隔，分隔相邻后腔的后腔板上可以设置有若干通孔，以使得相邻后腔连通。
在一些实施例中，壳体2730可以隔绝至少两个后腔以形成封闭空间。进一步地，壳体2730可以将第一后腔27331和第二后腔27332与外界隔绝形成封闭空间。在一些实施例中，继续参见图30所示， 扬声器壳体2730还可以包括后腔部。在一些实施例中，后腔部、后腔板2736以及驱动组件2720可以围合成第一后腔27331，驱动组件2720、振动组件2710、后腔部以及后腔板2736可以围合成第二后腔27332。在一些实施例中，后腔部可以包括封板2738和侧板2737。在一些实施例中，封板2738可以设置在驱动组件2720的与振动组件2710相对的一侧，封板2738、侧板2737和后腔板2736以及驱动组件2720可以围合成第一后腔27331，驱动组件2720、振动组件2710、侧板2737以及后腔板2736可以围合成第二后腔27332，从而使得第一后腔27331和第二后腔27332形成封闭空间。在一些实施例中，封板2738上可以开设若干通孔，以进一步减小后腔2733的空气附加到振动组件2710和驱动组件2720上的刚度，从而使得扬声器的灵敏度更大。在一些实施例中，至少两个后腔2733可以通过壳体2730上的一个或多个导声孔与外界连通。在一些实施例中，可以在封板2738开设一个或多个导声孔，以将第一后腔27331和第二后腔27332与外界连通。在一些实施例中，开设在封板2738上的若干通孔可以作为导声孔，将第一后腔27331和第二后腔27332与外界连通。在一些实施例中，一个或多个导声孔也可以开设在构成第一后腔27331的侧板2737上。在一些实施例中，可以不用在第一后腔27331远离驱动组件2720的腔口处设置封板2738，而使得后腔2733的腔体空间为开放式空间。下面将以第一后腔27331远离驱动组件2720的腔口处未设置封板2738的扬声器2800进行详细说明。
图31是根据本说明书一些实施例所示的扬声器的1/4立体结构示意图。图32是根据本说明书一些实施例所示的扬声器平行于壳体腔体的轴线方向的截面图。图33是根据本说明书一些实施例所示的扬声器垂直于壳体腔体的轴线方向的视图。
结合图31-33所示，后腔板2736开设有若干通孔27361，可以减小后腔2733中的空气附加在振动组件2710和驱动组件2720的刚度，从而可以提高振动组件2810和驱动组件2820的振动位移，振动组件2710便可以推动空气进行更大幅度的振动，进而可以提升扬声器2800的输出，使扬声器2800具有较高的灵敏度。在一些实施例中，如图33所示，后腔板2736上具有焊点27365(例如，驱动组件2720在后腔板2736上的电连接线的焊点)，若干通孔27361在后腔板2736上的位置可以根据焊点27365的位置进行设置，例如，可以将通孔27361设置在远离焊点27365的位置。
下面将结合驱动单元的频率位移曲线图和扬声器2800的频率响应曲线图具体描述后腔板2736开设通孔27361对扬声器2800的输出的影响。
图49是根据本说明书一些实施例所示的驱动单元的频率位移曲线图。
如图49所示，曲线L491是后腔板2736开设通孔27361时驱动单元2720的频率位移曲线，曲线L492是后腔板2736不开设通孔27361时驱动单元2720的频率位移曲线。可见通过在后腔板2736设计通孔27361，对驱动单元2720输出位移具有显著的影响，特别是在小于2000Hz的频段，驱动单元2720的位移明显提高，进一步的说明通过在后腔板2736设计通孔27361，减小附加于驱动单元2720上的附加刚度，可以极大的提升驱动单元2720在相同激励电压下的位移输出，最终提升扬声器的整体输出。
图34是根据本说明书一些实施例所示的扬声器的频响曲线图。
如图34所示，曲线L341是后腔板2736开设通孔时扬声器2800的频率响应曲线，曲线L342是后腔2733的体积趋近于无限大时(即后腔2733呈完全开放状态，可以看成在后腔板2736上开设了无限大的通孔或取消了后腔板2736的设置)的扬声器2800的频率响应曲线，曲线L343是后腔板2636未开设通孔时扬声器2800的频率响应曲线。通过比较曲线L341、L342以及L343可以发现，曲线L341、L342相较于曲线L343(曲线L343存在谐振谷3431)更为平滑，由此可以得出，当后腔板2736开设通孔或者后腔2733的体积趋近于无限大时扬声器2800能够具有较为平坦的声压级输出，从而使得扬声器2800具有较好的音质。另外，曲线L341、L342相较于曲线L343具有较大的输出声压级(即幅值)，由此可以得出，当后腔板2736开设通孔或者后腔2733的体积趋近于无限大时扬声器2800可以具有更高的灵敏度。通过使后腔板2736上开设无限大的通孔来使后腔2733的体积趋近于无限大较为理想化，而取消后腔板2736的设置则会影响扬声器2800的结构强度，因此，在扬声器的实际设计中，通过在后腔板2736开设通孔，并合理设计通孔的参数(例如，通孔的数量、形状、尺寸、分布方式等)可以有效提高扬声器的音质和灵敏度。
在一些实施例中，如图32所示，若干通孔27361可以均是圆孔。在一些实施例中，如图34A所示，若干通孔27361可以均是其它规则或不规则形状的孔，例如，均为正六边形孔、其他多边形、椭圆形、不规则图形等。
在一些实施例中，如图33和35A所示，若干通孔27361可以在后腔板2736上呈等间距的环形分布。在一些实施例中，如图35B所示，若干通孔可以在后腔板2736上呈不等间距的环形分布。
在一些实施例中，如图35C所示，若干通孔27361可以在后腔板2736上呈多个(例如，图35C所示的两个)环形分布。在一些实施例中，多个环形分布所对应的圆的圆心可以重合。在一些实施例中，多个通孔可以非环形分布，或者无规律分布于后腔板2736上。在一些实施例中，多个环形分布中的至少 两个所对应的圆可以相切。在一些实施例中，每个环形分布中的通孔可以是等间距或不等间距。在一些实施例中，当环形分布中的通孔呈不等间距分布时，可以将通孔27361远离焊点27365的位置设计，确保后腔板2736上靠近焊点27365的区域有足够的面积设计布置电极引线以及焊点27365。
在一些实施例中，若干通孔27361可以包括多种不同形状的通孔。在一些实施例中，如图35D所示，若干通孔27361可以包括多个圆形孔和多个正六边形孔。多个圆形孔和多个正六边形孔可以在后腔板2736上呈同一环形分布，也可以呈不同的环形分布。在一些实施例中，多个圆形孔和多个正六边形孔可以分别在后腔板2736上呈不同的环形分布，即多个圆形孔呈一环形分布，多个正六边形孔呈另一环形分布。在一些实施例中，多个圆形孔和多个正六边形孔也可以混合形成多个环形阵列，即每个环形阵列里既有圆形孔也有正六边形孔。
在一些实施例中，如图35E所示，若干通孔27361可以均是扇环形孔，若干扇环形孔可以在后腔板2736上呈等间距的环形分布，即若干扇环形孔在后腔板2736上可以看成是不连续的环形孔。在一些实施例中，如图35F所示，若干扇环形孔可以在后腔板2736上呈多个环形分布，即若干扇环形孔在后腔板2736上可以看成是多个同心的不连续的环形孔。
需要说明的是，图33以及图35A-图35F所示的若干通孔27361的形状、分布方式等仅作为示例，并无意于对其进行限制。例如，若干通孔27361的形状还可以三角形、矩形、正五边形等规则或不规则形状。又例如，若干通孔27361在后腔板2736上还可以呈矩形分布、线性分布等。在一些实施例中，如图33以及图35A-图35F所示，还可以在后腔板2736的中心开设中心通孔27367，中心通孔27367可以为驱动组件2720留出变形空间。
在一些实施例中，若干通孔27361在后腔板2736上的位置不同，对扬声器性能会有所影响，因此，可以通过合理设置若干通孔27361在后腔板2736上的位置，来使得扬声器具有较好的性能。
下面将以图32-图33所示的扬声器2800以及后腔板2736的结构为例，具体说明若干通孔27361在后腔板2736上的位置对扬声器的性能(例如，灵敏度)的影响。
在一些实施例中，如图32和图33所示，若干通孔2736中的至少一个通孔2736的位置可以根据通孔2736的中心线到壳体2730腔体的中心线之间的距离、驱动组件2720的等效半径以及壳体2730的腔体的等效半径确定。在一些实施例中，当通孔2736为圆孔时，通孔2736的中心线可以是圆孔的轴线；而当通孔2736为其他形状的孔时，通孔27361的中心线可以为过通孔2736的横截面的几何中心或等效圆的圆心且与壳体2730腔体的轴线(例如，腔体的中心线)平行的线。在一些实施例中，当壳体2730腔体的横截面的形状为圆形时，壳体2730腔体的中心线则为腔体的轴线，壳体2730腔体的等效半径则为该圆的半径；而当壳体2730腔体的横截面的形状为非圆形的形状时，壳体2730腔体的中心线则为过该非圆形的形状的等效圆的圆心且与振动组件2710或驱动组件2720的表面垂直的线。在一些实施例中，当驱动组件2720的横截面的形状为圆形时，驱动组件2720的等效半径则为该圆形的半径；而当驱动组件2720的横截面的形状为非圆形的形状时，驱动组件2720的等效半径则为该非圆形的形状的等效圆的半径。可以理解的是，通孔27361、壳体2730腔体以及驱动组件2720的横截面可以是指通孔27361、壳体2730腔体以及驱动组件2720与壳体2730腔体的中心线垂直的截面。非圆形的形状的等效圆可以是指该非圆形的形状的外接圆。
进一步地，通孔27361的中心线与腔体的中心线之间的距离RK与驱动组件2720的等效半径RN之间的差值和腔体的等效半径R与驱动组件2720的等效半径RN之间的差值具有第一预设比值α，其中，α＝(RK-RN)/(R-RN)。在一些实施例中，通孔27361在后腔板2736上的位置可以用第一预设比值α表示。具体地，第一预设比值α可以与扬声器的性能相关。
下面将结合不同第一预设比值α下的扬声器的频率响应曲线进行具体说明。
图36是根据本说明书一些实施例所示的扬声器在不同第一预设比值α下的频响曲线图。
如图36所示，曲线L361是扬声器2800在第一预设比值α为0.23时的频响曲线，曲线L362是扬声器2800在第一预设比值α为0.39时的频响曲线，曲线L363是扬声器2800在第一预设比值α为0.55时的频响曲线，曲线L364是扬声器2800在第一预设比值α为0.71时的频响曲线。由曲线L361、L362、L363以及L364可知，扬声器的频响曲线随第一预设比值α的增加在中频段(例如，1kHz-4kHz)的输出声压级先增加后降低，随第一预设比值α的增加在中高频段(例如，4kHz-8kHz)的输出声压级先增加后降低，随第一预设比值α的逐渐增加在高频(例如，10kHz以上)的输出声压级先增加后降低。因此可以得出，第一预设比值α过大或过小均不利于提高扬声器的灵敏度。
在一些实施例中，为了保证扬声器全频段范围(例如，人耳可听域内的20Hz-20kHz)内的频响曲线具有较高的输出声压级，使得扬声器在全频段范围内具有较高的灵敏度，第一预设比值α可以为0.3～0.9。在一些实施例中，为了保证扬声器全频段范围内的频响曲线具有较高的输出声压级输出，使得扬声器在全频段范围内具有较高的灵敏度并且具有较好的音质，第一预设比值α可以为0.4～0.75。
在一些实施例中，若干通孔27361在后腔板2736上的面积不同，对扬声器性能会有所影响，因此，可以通过合理设置若干通孔27361在后腔板2736上的面积，来使得扬声器具有较好的性能。具体地，可以通过对若干通孔2736在垂直于腔体中心线的平面内的投影面积的总和与腔体在垂直于腔体中心线的平面内的投影面积与驱动组件2720在垂直于腔体中心线的平面内的投影面积之间的差值之间的比值进行设计，来使扬声器具有较好的性能。
图37和图38是根据本说明书一些实施例所示的扬声器垂直于壳体腔体的轴线方向的视图。
如图37和图38所示，在垂直于腔体中心线的平面内，若干通孔在该平面内的投影面积的总和Sh与腔体在该平面内的投影面积与驱动组件2720在该平面内的投影面积之间的差值S之间存在第二预设比值β。在一些实施例中，当腔体和驱动组件2720的横截面为圆形时，S＝πR 2-πRN 2。因此，β＝Sh/(πR 2-πRN 2)。具体地，第二预设比值β与扬声器的性能相关。
下面将结合不同第二预设比值β下的扬声器的频率响应曲线进行具体说明。
图39是根据本说明书一些实施例所示的通孔为圆孔时扬声器在不同第二预设比值β下的频响曲线图。
如图39所示，曲线L391是扬声器2800在第二预设比值β为0.012时的频响曲线，曲线L392是扬声器2800在第二预设比值β为0.036时的频响曲线，曲线L393是扬声器2800在第二预设比值β为0.06时的频响曲线，曲线L394是扬声器2800在第二预设比值β为0.11时的频响曲线，曲线L395是扬声器2800在第二预设比值β为0.14时的频响曲线。由曲线L391、L392、L393、L394以及曲线L395可知，当通孔为圆孔时，随第二预设比值β的增加，扬声器的频响曲线的输出声压级也在增加。因此可以得出，可以将第二预设比值β设计得越大，越有利于扬声器提高扬声器的灵敏度。例如，根据曲线L391和L393可知，在相同频段内，扬声器在第二预设比值β为0.06时的频响曲线的输出声压级是高于第二预设比值β为0.012时的频响曲线的输出声压级的，因此，在相同频段内，扬声器在第二预设比值β为0.06时的灵敏度高于第二预设比值β为0.012时的灵敏度的。另外，扬声器在第二预设比值β为0.012的频响曲线相对于第二预设比值β为0.06时的频响曲线具有明显的谐振谷，也即是说，扬声器在第二预设比值β为0.06时的频响曲线相对于第二预设比值β为0.012时的频响曲线更为平滑，即具有更为平坦的声压级输出。在一些实施例中，当通孔为圆孔时，为了保证扬声器的频响曲线具有较高的输出声压级，保证扬声器具有较高的灵敏度，第二预设比值β可以为0.02～1。在一些实施例中，当通孔为圆孔时，为了保证扬声器的频响曲线具有较高的输出声压级且具有较为平坦的声压级输出，第二预设比值β可以为0.06～0.5。在一些实施例中，当通孔为圆孔时，为了保证扬声器的频响曲线具有较高的输出声压级且具有较为平坦的声压级输出，并且避免若干通孔的面积过大而影响后腔板2736的结构强度，第二预设比值β可以为0.1～0.4。
图40是根据本说明书一些实施例所示的通孔为扇环形孔(例如，图35E所示的扇环形孔)时扬声器在不同第二预设比值β下的频响曲线图。
如图40所示，曲线L401是扬声器2800在第二预设比值β为0(即后腔板2736上未开设有通孔)时的频响曲线，曲线L402是扬声器2800在第二预设比值β为0.12时的频响曲线，曲线L403是扬声器2800在第二预设比值β为0.25时的频响曲线，曲线L404是扬声器2800在第二预设比值β为1时的频响曲线。结合曲线L401、L402、L403以及L404可知，当通孔的为扇环孔时，随第二预设比值β的增加，扬声器的频响曲线的输出声压级也在增加。因此可以得出，可以将第二预设比值β设计得越大，越有利于扬声器提高扬声器的灵敏度。在一些实施例中，当通孔为扇环形孔时，为了保证扬声器的频响曲线具有较高的输出声压级，保证扬声器具有较高的灵敏度，第二预设比值β可以为0.1～1。在一些实施例中，当通孔为扇环形孔时，为了保证扬声器的频响曲线具有较高的输出声压级且具有较为平坦的声压级输出，第二预设比值β可以为0.1～0.5。在一些实施例中，当通孔为扇环形孔时，为了保证扬声器的频响曲线具有较高的输出声压级且具有较为平坦的声压级输出，并且避免若干通孔的面积过大而影响后腔板2736的结构强度，第二预设比值β可以为0.1～0.4。
在一些实施例中，结合图39和图40可知，为了保证扬声器具有较好的性能，通孔为圆孔时对应的第二预设比值β和通孔为扇环形孔时对应的第二预设比值β具有相同的取值范围，由此可以得出，当通过在后腔板2736上开设若干通孔来改善扬声器性能时，扬声器性能主要取决于第二预设比值β的大小，而与通孔的形状并不大相关。因此，在一些实施例中，通孔为圆孔或扇环形孔对应的第二预设比值β的取值范围在通孔为三角形、矩形、正六边形等规则或不规则的形状的情况下也能适用。
在一些实施例中，结合图32和图33所示，当若干通孔27361均为相同大小的圆孔时，若干通孔在垂直于腔体中心线的平面内的投影面积的总和Sh＝n(π(D/2) 2)，其中，n为通孔27361的数量，D为通孔27361的孔径。在一些实施例中，结合上述可知，通孔27361的孔径D越大，若干通孔在垂直于腔体中心线的平面内的投影面积的总和Sh就越大，第二预设比值β也就越大，就越有利于提高扬声器的灵敏度。但由于通孔27361的孔径D过大会导致后腔板2736的强度不足，并且会增加后腔板2736的防尘防 水难度。因此，在一些实施例中，通孔27361的孔径D可以为0.2mm～2mm，这样可以保证扬声器具有较好性能(例如，较高的灵敏度)的同时，后腔板也能具有足够的强度。在一些实施例中，通孔27361的孔径D可以为0.4mm～1mm，这样可以保证扬声器具有较好性能(例如，较高的灵敏度)且后腔板有足够的强度的同时，后腔板2736具有较好的防尘防水性能。
图41-图43是根据本说明书一些实施例所示的扬声器平行于壳体腔体的轴线方向的截面图。图44是根据本说明书一些实施例所示的扬声器垂直于壳体腔体的轴线方向的截面图。
在一些实施例中，如图41-图44所示，若干通孔27361中的至少一个可以设置有阻尼网27362。通过设置阻尼网27362，可以降低扬声器在不同频段内的谐振峰的Q值，使得谐振峰的陡峭程度较低，从而使得扬声器的频响曲线更好平滑，使得扬声器具有较好的音质。在一些实施例中，如图41所示，阻尼网27362可以设置于通孔27361远离驱动组件2720的一侧的孔口处。在一些实施例中，如图42所示，阻尼网27362可以设置于通孔27361靠近驱动组件2720的一侧的孔口处。在一些实施例中，如图43所示，阻尼网27362可以设置于通孔27361内，例如，阻尼网27362的边缘可以与通孔27361的内壁连接以固定于通孔27361内。
下面将结合图45具体说明通孔27361对应设置有阻尼网对扬声器2800的频响曲线的影响。
图45是根据本说明书一些实施例所示的扬声器的频率响应曲线图。
如图45所示，曲线L451为通孔27361对应设置有阻尼网27362时扬声器的频响曲线，曲线L452通孔27361未对应设置有阻尼网27362时扬声器的频响曲线。结合曲线L451和曲线L452可知，曲线L451中的谐振峰4511相较于曲线L452中的谐振峰4521较为平缓，Q值较小，曲线L451相对于曲线L452更为平滑。由此可以得出，通过在通孔27361对应设置阻尼网27362，可以使得扬声器具有较为平坦的声压级输出，从而保证扬声器具有较好的音质。
在一些实施例中，扬声器的频响曲线中的谐振峰Q值与阻尼网27362的声阻相关，阻尼网27362的声阻越大，谐振峰Q值就越小。在一些实施例中，为了使得扬声器的频响曲线中的谐振峰具有较小的Q值，以保证扬声器具有较好的音质，阻尼网27362的声阻可以为3～10000MKS rayls。
图46是根据本说明书一些实施例所示的扬声器平行于壳体腔体的轴线方向的截面图。
在一些实施例中，如图46所示，除了在通孔27361的对应位置处设置阻尼网27362，还可以将阻尼网27362设置在前腔板2735上，例如，将阻尼网27362对应设置于第一孔部(图27示出的第一孔部2732)，以进一步降低扬声器的频响曲线中的谐振峰的Q值，从而进一步使扬声器具有较好的音质。
图47是根据本说明书一些实施例所示的阻尼网的结构示意图。
在一些实施例中，如图47所示，阻尼网27362可以由多条纱网线27363编织而成，纱网线27363之间形成有阻尼网27362的孔隙27364。在一些实施例中，阻尼网27362的声阻与其孔隙率相关。其中，阻尼网27362的孔隙率可以是孔隙27364的面积S1与指沿纱网线27366中心线围成的区域面积S2之间的比值。在一些实施例中，阻尼网27362的孔隙率越小，阻尼网27362的声阻就越大。在一些实施例中，为了使得阻尼网27362具有较大的声阻，以降低扬声器的频响曲线中的谐振峰Q值，保证扬声器具有较好的音质，阻尼网的孔隙率可以为13％～44％。在一些实施例中，阻尼网27362的声阻与孔隙27364的尺寸相关。在一些实施例中，孔隙27364的尺寸越小，阻尼网27362的声阻就越大。可以理解的是，当孔隙27364的形状为圆形时，孔隙27364的尺寸可以是指该圆形的直径；当孔隙的形状为矩形时，孔隙27364的尺寸可以是指该矩形的长度或宽度。在一些实施例中，为了使得阻尼网27362具有较大的声阻，以降低扬声器的频响曲线中的谐振峰Q值，保证扬声器具有较好的音质，孔隙27364的尺寸可以为18～285um。
需要说明的是，不同实施例可能产生的有益效果不同，在不同的实施例里，可能产生的有益效果可以是以上任意一种或几种的组合，也可以是其他任何可能获得的有益效果。
上文已对基本概念做了描述，显然，对于本领域技术人员来说，上述详细披露仅仅作为示例，而并不构成对本说明书的限定。虽然此处并没有明确说明，本领域技术人员可能会对本说明书进行各种修改、改进和修正。该类修改、改进和修正在本说明书中被建议，所以该类修改、改进、修正仍属于本说明书示范实施例的精神和范围。
同时，本说明书使用了特定词语来描述本说明书的实施例。如“一个实施例”、“一实施例”、和/或“一些实施例”意指与本说明书至少一个实施例相关的某一特征、结构或特点。因此，应强调并注意的是，本说明书中在不同位置两次或多次提及的“一实施例”或“一个实施例”或“一个替代性实施例”并不一定是指同一实施例。此外，本说明书的一个或多个实施例中的某些特征、结构或特点可以进行适当的组合。
同理，应当注意的是，为了简化本说明书披露的表述，从而帮助对一个或多个发明实施例的理解，前文对本说明书实施例的描述中，有时会将多种特征归并至一个实施例、附图或对其的描述中。但是，这种披露方法并不意味着本说明书对象所需要的特征比权利要求中提及的特征多。实际上，实施例的特征要少于上述披露的单个实施例的全部特征。
一些实施例中使用了描述成分、属性数量的数字，应当理解的是，此类用于实施例描述的数字，在一些示例中使用了修饰词“大约”、“近似”或“大体上”来修饰。除非另外说明，“大约”、“近似”或“大体上”表明所述数字允许有±20％的变化。相应地，在一些实施例中，说明书和权利要求中使用的数值参数均为近似值，该近似值根据个别实施例所需特点可以发生改变。在一些实施例中，数值参数应考虑规定的有效数位并采用一般位数保留的方法。尽管本说明书一些实施例中用于确认其范围广度的数值域和参数为近似值，在具体实施例中，此类数值的设定在可行范围内尽可能精确。
最后，应当理解的是，本说明书中所述实施例仅用以说明本说明书实施例的原则。其他的变形也可能属于本说明书的范围。因此，作为示例而非限制，本说明书实施例的替代配置可视为与本说明书的教导一致。相应地，本说明书的实施例不仅限于本说明书明确介绍和描述的实施例。

Claims (18)

  1. 一种扬声器，包括：
    驱动组件，所述驱动组件基于电信号产生振动；
    振动组件，所述振动组件接收所述驱动组件的振动而发生振动；
    壳体，所述驱动组件和所述振动组件设置于所述壳体形成的腔体内；
    其中，所述腔体包括位于所述振动组件一侧的前腔以及一个或多个位于所述振动组件另一侧的后腔，所述壳体包括后腔板，所述一个或多个后腔中的至少一个至少由所述驱动组件、所述振动组件以及所述后腔板围合而成，所述后腔板上开设有通孔。
  2. 根据权利要求1所述的扬声器，其中，所述驱动组件的振动表面构成所述一个或多个后腔中的至少一个的侧壁的至少一部分。
  3. 根据权利要求2所述的扬声器，其中，所述驱动组件包括压电式声学驱动器。
  4. 根据权利要求3所述的扬声器，其中，所述压电式声学驱动器包括悬臂梁。
  5. 根据权利要求4所述的扬声器，其中，相邻的所述悬臂梁之间的缝隙不大于25μm。
  6. 根据权利要求2所述的扬声器，其中，所述驱动组件的振动表面上不小于90％的表面区域连续。
  7. 根据权利要求6所述的扬声器，其中，所述驱动组件包括压电膜。
  8. 根据权利要求1所述的扬声器，其中，所述后腔的数量包括至少两个，至少两个所述后腔通过所述通孔相互连通。
  9. 根据权利要求8所述的扬声器，其中，所述壳体包括后腔部，所述后腔部、所述后腔板以及所述驱动组件围合成第一后腔；所述驱动组件、所述振动组件、所述后腔部以及所述后腔板围合成第二后腔。
  10. 根据权利要求9所述的扬声器，其中，所述后腔部包括侧板和封板。
  11. 根据权利要求9所述的扬声器，其中，至少两个所述后腔通过所述后腔部上一个或多个导声孔与外界连通。
  12. 根据权利要求1所述的扬声器，其中，所述通孔中的至少一个的中心线与所述腔体的中心线之间的距离与所述驱动组件的等效半径之间的差值和所述腔体的等效半径与所述驱动组件的等效半径之间的差值之间具有第一预设比值；其中，所述第一预设比值为0.3～0.9。
  13. 根据权利要求1所述的扬声器，其中，在垂直于所述腔体中心线的平面内，所述通孔在所述平面内的投影面积的总和与所述腔体在所述平面内的投影面积与所述驱动组件在所述平面内的投影面积之间的差值之间具有第二预设比值；其中，所述第二预设比值为0.02～1。
  14. 根据权利要求1所述的扬声器，其中，所述通孔中的至少一个的孔径为0.2mm～2mm。
  15. 根据权利要求1所述的扬声器，其中，所述通孔中的至少一个对应设置有阻尼网。
  16. 根据权利要求15所述的扬声器，其中，所述阻尼网的声阻为3MKS rayls～10000MKS rayls。
  17. 根据权利要求15所述的扬声器，其中，所述阻尼网的孔隙尺寸为18μm～285μm。
  18. 根据权利要求15所述的扬声器，其中，所述阻尼网的孔隙率为13％～44％。
PCT/CN2022/108479 2022-06-21 2022-07-28 一种扬声器 WO2023245807A1 (zh)

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TW112101228A TWI835518B (zh) 2022-06-21 2023-01-11 一種揚聲器
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CN206181371U (zh) * 2016-10-31 2017-05-17 常州阿木奇声学科技有限公司 一种具有陶瓷压电单元的动圈扬声器
CN207124746U (zh) * 2017-07-24 2018-03-20 歌尔科技有限公司 扬声器单体以及电子设备
US20200177996A1 (en) * 2018-11-30 2020-06-04 Merry Electronics (Shenzhen) Co., Ltd. Speaker
CN113079441A (zh) * 2020-01-06 2021-07-06 北京小米移动软件有限公司 扬声器及终端设备

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US20110085684A1 (en) * 2009-10-12 2011-04-14 Samsung Electronics Co., Ltd. Piezoelectric micro speaker
CN206181371U (zh) * 2016-10-31 2017-05-17 常州阿木奇声学科技有限公司 一种具有陶瓷压电单元的动圈扬声器
CN207124746U (zh) * 2017-07-24 2018-03-20 歌尔科技有限公司 扬声器单体以及电子设备
US20200177996A1 (en) * 2018-11-30 2020-06-04 Merry Electronics (Shenzhen) Co., Ltd. Speaker
CN113079441A (zh) * 2020-01-06 2021-07-06 北京小米移动软件有限公司 扬声器及终端设备

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