WO2024020846A1 - 一种声学输出装置 - Google Patents

一种声学输出装置 Download PDF

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Publication number
WO2024020846A1
WO2024020846A1 PCT/CN2022/108205 CN2022108205W WO2024020846A1 WO 2024020846 A1 WO2024020846 A1 WO 2024020846A1 CN 2022108205 W CN2022108205 W CN 2022108205W WO 2024020846 A1 WO2024020846 A1 WO 2024020846A1
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WO
WIPO (PCT)
Prior art keywords
beam structure
output device
acoustic output
resonance peak
ratio
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PCT/CN2022/108205
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English (en)
French (fr)
Inventor
崔超杰
朱光远
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.)
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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 CN202280006774.8A priority Critical patent/CN117981358A/zh
Priority to PCT/CN2022/108205 priority patent/WO2024020846A1/zh
Priority to US18/165,348 priority patent/US20240040931A1/en
Publication of WO2024020846A1 publication Critical patent/WO2024020846A1/zh

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    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/02—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of electrical energy
    • B06B1/06—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of electrical energy operating with piezoelectric effect or with electrostriction
    • B06B1/0603—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of electrical energy operating with piezoelectric effect or with electrostriction using a piezoelectric bender, e.g. bimorph
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K9/00—Devices in which sound is produced by vibrating a diaphragm or analogous element, e.g. fog horns, vehicle hooters or buzzers
    • G10K9/12—Devices in which sound is produced by vibrating a diaphragm or analogous element, e.g. fog horns, vehicle hooters or buzzers electrically operated
    • G10K9/121—Flextensional transducers
    • 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
    • H04R17/00—Piezoelectric transducers; Electrostrictive transducers
    • H04R17/005—Piezoelectric transducers; Electrostrictive transducers using a piezoelectric polymer
    • 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

Definitions

  • This specification relates to the field of acoustics, and in particular to an acoustic output device.
  • Acoustic output devices driven by piezoelectric materials utilize the inverse piezoelectric effect of piezoelectric materials to generate vibrations to radiate sound waves outward. Compared with traditional electromagnetic acoustic output devices, acoustic output devices driven by piezoelectric materials have the advantages of high electromechanical conversion efficiency, low energy consumption, small size, and high integration.
  • acoustic output devices driven by piezoelectric materials have poorer sound quality.
  • the reasons include: there are many vibration modes in the target frequency range and it is impossible to form a smoother frequency response curve.
  • an acoustic output device that can form a smoother frequency response curve within a target frequency range.
  • the vibration element includes a beam structure extending along the length direction.
  • the beam structure includes: a piezoelectric layer for deforming in response to an electrical signal, the deformation driving the vibrating element to vibrate; and a mass element connected to a first position of the beam structure, the The vibration of the vibrating element drives the mass element to vibrate in a direction perpendicular to the length direction, wherein, along the length direction of the beam structure, the distance from the first position to one end of the beam structure is equal to the distance between the first position and one end of the beam structure.
  • the ratio between the lengths of the beam structures can be in the range of 0.3 to 0.95.
  • the vibration of the mass element may have a first resonance peak and a second resonance peak in the range of 50 Hz-10000 Hz.
  • the amplitude difference between the lowest point of the frequency response between the first resonance peak and the second resonance peak and the first resonance peak or the second resonance peak may be less than 40 dB.
  • the beam structure may include a fixed end and a free end.
  • the acoustic output device may further include a second mass element, which may be connected to the free end.
  • the ratio between the second mass element and the mass of the beam structure may be in the range of 0-1.2.
  • the ratio between the distance from the first position to the fixed end and the length of the beam structure may be in the range of 0.7-0.95.
  • the ratio of the frequency range of the second resonance peak to the frequency range of the first resonance peak may be greater than 17.
  • the vibration of the mass element may have a third resonance peak, and the lowest point of the frequency response between the second resonance peak and the third resonance peak is consistent with the second resonance peak or the third resonance peak.
  • the amplitude difference between resonant peaks can be less than 30dB.
  • the ratio of the frequency range of the third resonance peak to the frequency range of the second resonance peak may be greater than 4.
  • the ratio between the distance from the first position to the fixed end and the length of the beam structure may be in the range of 0.45-0.6.
  • the beam structure may include two fixed ends.
  • the ratio between the distance from the first position to one of the two fixed ends and the length of the beam structure may be in the range of 0.3-0.4.
  • the ratio of the frequency range of the second resonance peak to the frequency range of the first resonance peak may be greater than 13.
  • the vibration of the mass element may have a third resonance peak, and the lowest point of the frequency response between the second resonance peak and the third resonance peak is consistent with the second resonance peak or the third resonance peak.
  • the amplitude difference between resonant peaks can be less than 40dB.
  • the ratio of the frequency range of the third resonance peak to the frequency range of the second resonance peak may be greater than 2.
  • the ratio between the distance from the first position to one of the two fixed ends and the length of the beam structure may be in the range of 0.45-0.5.
  • the ratio between the distance from the first position to one side of the beam structure and the width of the beam structure may be in the range of 0.15-0.3.
  • the beam structure may include a fixed end and a hinged end.
  • the hinged end may rotate along an axis perpendicular to the length direction and vibration direction of the beam structure. .
  • the ratio between the distance from the first position to the fixed end and the length of the beam structure may be in the range of 0.5-0.6.
  • the ratio of the frequency range of the second resonance peak to the frequency range of the first resonance peak may be greater than 6.
  • the beam structure may include two hinged ends. During the vibration process of the vibrating element, the two hinged ends may be aligned along directions perpendicular to the length direction and the vibration direction of the beam structure. The shaft rotates.
  • the ratio between the distance from the first position to one of the two hinge ends and the length of the beam structure may be in the range of 0.3-0.4.
  • the ratio of the frequency range of the second resonance peak to the frequency range of the first resonance peak may be greater than 10.
  • the beam structure may include two elastic ends, and the two elastic ends may be elastically connected to the fixed support of the acoustic output device through elastic members respectively.
  • the beam structure may be a two-end symmetrical structure, and the elastic members corresponding to the two elastic ends may be symmetrically arranged along the length direction or width direction of the beam structure.
  • the frequency range of the first resonance peak may be 300 Hz-700 Hz.
  • the ratio between the distance from the first position to one of the two elastic ends and the length of the beam structure may be in the range of 0.1-0.25.
  • the acoustic output device may further include a third vibration element, and the third vibration element may include a third beam structure, wherein one end of the beam structure and the third beam structure is a fixed end. , the other end of the beam structure and the third beam structure may be connected through an elastic connector.
  • the number of the vibration elements may be two or more, wherein the beam structure of each of the two or more vibration elements may include a fixed end and a free end.
  • the mass element may be respectively connected to a first position of the beam structure of each of the two or more vibration elements, and the first position of each beam structure is connected to a fixed position of the beam structure.
  • the ratio between the distance between the ends and the length of the beam structure may be in the range 0.7-0.95.
  • FIG. 1 is a block diagram of an exemplary acoustic output device according to some embodiments of the present specification
  • Figure 2 is a schematic diagram of an exemplary beam structure shown in accordance with some embodiments of the present specification
  • Figure 3 is a frequency response curve diagram of different positions on the beam structure according to some embodiments of this specification.
  • Figure 4 is a structural schematic diagram of an exemplary beam structure according to some embodiments of the present specification.
  • Figure 5 is a frequency response curve diagram of different positions along the length of the beam structure under no-load and loaded conditions according to some embodiments of this specification;
  • Figure 6 is a diagram showing the relationship between the mass ratio of the second mass element and the beam structure and the distance from the first position to the fixed end and the length ratio of the beam structure according to some embodiments of this specification;
  • Figure 7 is a structural schematic diagram of an exemplary beam structure according to some embodiments of the present specification.
  • Figure 8 is a schematic structural diagram of a hinge end according to some embodiments of this specification.
  • Figure 9 is a structural schematic diagram of an exemplary beam structure according to some embodiments of the present specification.
  • Figure 10 is a structural schematic diagram of an exemplary beam structure according to some embodiments of the present specification.
  • Figure 11A is a structural schematic diagram of an exemplary beam structure according to some embodiments of the present specification.
  • Figure 11B is a schematic diagram of the vibration modes of the beam structure shown in Figure 11A;
  • Figure 12 is a frequency response curve diagram of different position points in the length direction of the beam structure according to some embodiments of this specification.
  • Figure 13 is a frequency response curve diagram of different position points in the width direction of the beam structure according to some embodiments of this specification.
  • Figure 14A is a structural schematic diagram of a beam structure according to some embodiments of this specification.
  • Figure 14B is a schematic diagram of the vibration mode of the beam structure shown in Figure 14A;
  • Figure 15 is a frequency response curve diagram of different positions on the beam structure according to some embodiments of this specification.
  • Figure 16A is a structural schematic diagram of a beam structure according to some embodiments of this specification.
  • Figure 16B is a schematic diagram of the vibration mode of the beam structure shown in Figure 16A;
  • Figure 17 is a frequency response curve diagram of different positions on the beam structure according to some embodiments of this specification.
  • Figure 18 is a partial schematic diagram of an acoustic output device according to some embodiments of the present specification.
  • Figure 19 is a schematic diagram of an acoustic output device according to some embodiments of the present specification.
  • system means of distinguishing between different components, elements, parts, portions or assemblies at different levels.
  • words may be substituted by other expressions if they serve the same purpose.
  • an acoustic output device which may include a vibrating element, and the vibrating element includes a beam structure extending along a length direction.
  • the beam structure may include a piezoelectric layer. Due to its inverse piezoelectric effect, the piezoelectric layer may deform in response to an electrical signal, and the deformation drives the vibrating element to vibrate.
  • the acoustic output device may further include a mass element connected to the first position of the beam structure. The vibration of the vibration element can drive the mass element to vibrate in a direction perpendicular to the length direction of the beam structure, thereby generating sound.
  • the vibration modes output through the mass element are different, and accordingly, the frequency response curves of the acoustic output device are different, so it can be installed on the beam structure.
  • Embodiments of this specification can set the first position (for example, adjust the ratio between the distance from the first position to one end of the beam structure and the length of the beam structure) so that the frequency response curve of the acoustic output device is within the target frequency range (for example, 50 Hz -10000Hz), there are no or fewer resonance valleys, or the amplitude difference between the resonance peak and the resonance valley is reduced, thereby obtaining a smoother frequency response curve and ensuring that the acoustic output device can have better sound quality.
  • the target frequency range for example, 50 Hz -10000Hz
  • FIG. 1 is a block diagram of an acoustic output device according to some embodiments of this specification.
  • the acoustic output device 100 may include a vibrating element 110 and a mass element 120 .
  • the acoustic output device 100 may be used to convert an audio signal (eg, an electrical signal containing sound information) into a sound signal.
  • the acoustic output device 100 may be a bone conduction acoustic output device, an air conduction acoustic output device, or a bone-air conduction combined acoustic output device.
  • the acoustic output device 100 can be applied to glasses, smart bracelets, headphones, hearing aids, smart helmets, smart watches, smart clothing, smart backpacks, smart accessories, etc., or any combination thereof.
  • the acoustic output device 100 can be applied to functional myopia glasses, reading glasses, cycling glasses or sunglasses, etc., or it can also be intelligent glasses, such as audio glasses with a headphone function.
  • the acoustic output device 100 can also be applied to head-mounted devices such as helmets, augmented reality (Augmented Reality, AR) devices, or virtual reality (Virtual Reality, VR) devices.
  • an augmented reality device or a virtual reality device may include a virtual reality helmet, virtual reality glasses, augmented reality headset, augmented reality glasses, etc., or any combination thereof.
  • virtual reality devices and/or augmented reality devices may include Google Glass, Oculus Rift, Hololens, Gear VR, etc.
  • Vibrating element 110 may be used to convert audio signals into mechanical vibrations.
  • vibrating element 110 may include a beam structure 111 extending lengthwise.
  • the beam structure 111 may be a cantilever beam with one end fixed (eg, see Figure 2).
  • the beam structure 111 may be a beam with one end fixed and the other end hinged (eg, see FIG. 7 ).
  • the beam structure 111 may be a beam that is hinged at both ends (eg, see FIG. 10 ).
  • the beam structure 111 may be a beam with both ends fixed (eg, see FIG. 11A ).
  • the beam structure 111 may also be a beam with elastic supports at both ends (see Figure 14A). In some embodiments, the beam structure 111 may also be an intermediate elastically supported beam (eg, see FIG. 16A ). In some embodiments, the number of vibration elements 110 may be two or more (see Figure 19).
  • the vibration element 110 may also be a sheet-shaped, rod-shaped structure, etc.
  • the material of the vibration element 110 may be a material that has the ability to transmit vibration.
  • the material of the vibration element 110 may include silicone, foam, plastic, rubber, metal, etc., or any combination thereof.
  • the vibration element 110 may be a component with good elasticity (that is, easy to undergo elastic deformation).
  • the vibration element 110 may include a spring (such as an air spring, a mechanical spring, an electromagnetic spring, etc.), a vibration transmitting piece, an elastic piece, a substrate, etc., or any combination thereof.
  • beam structure 111 may include piezoelectric layer 1112 .
  • the piezoelectric layer 1112 can deform in response to an electrical signal (e.g., an electrical signal containing audio information), thereby causing the beam structure 111 to vibrate.
  • an electrical signal e.g., an electrical signal containing audio information
  • the piezoelectric layer 1112 may deform in response to an electrical signal, and the deformation may drive the beam structure 111 (or the vibration element 110) to vibrate along the polarization direction of the piezoelectric layer 1112.
  • the vibration direction of the beam structure 111 may be perpendicular to the length direction of the beam structure 111 (ie, the long axis direction of the beam structure 111).
  • the piezoelectric layer 1112 may be composed of a material having a piezoelectric effect (inverse piezoelectric effect).
  • Exemplary piezoelectric materials may include piezoelectric ceramics, piezoelectric crystals, piezoelectric polymers (eg, biased piezoelectric materials). polyvinyl fluoride), etc. or any combination thereof.
  • the piezoelectric layer 1112 can be in any shape, such as film, sheet, block, column, etc. or any combination thereof.
  • the piezoelectric layer 1112 may be in the shape of a sheet that conforms to the shape of the beam structure 111 .
  • the piezoelectric layer 1112 can be directly attached to the beam structure 111 through bonding or deposition. In some embodiments, the piezoelectric layer 1112 can be connected to the beam structure 111 through snapping, snapping, or other methods. In some embodiments, the piezoelectric layer 1112 may be attached to the beam structure 111 by physical or chemical deposition. For more description about the vibrating element, please refer to other parts of this specification, such as Figure 2, Figure 5, Figure 7, etc. and their related descriptions.
  • the mass element 120 may be a component having mass.
  • the mass element 120 may include a vibration plate, a diaphragm, or the like, so that the acoustic output device 100 can output vibration through the mass element 120 .
  • the mass element 120 can be in any shape, such as a regular structure or an irregular structure such as a cylinder, a cuboid, a cone, a cone, a sphere, etc.
  • the material of the mass element 120 may include but is not limited to plastic, wood, metal and other materials with certain rigidity.
  • the material of the mass element 120 may also include various metamaterials such as negative stiffness materials and cubic stiffness materials that are beneficial to expanding the audio frequency bandwidth of the acoustic output device 100 .
  • mass element 120 may be connected to beam structure 111 at a first location. The vibration at the first position on the beam structure 111 drives the mass element 120 to vibrate in the same direction as the vibration element 110 (that is, in a direction perpendicular to the length direction of the beam structure 111).
  • the mass element 120 can be directly connected to the first position of the beam structure 111, or can be connected to the first position of the beam structure 111 through a connecting rod (for example, when the mass element 120 is a diaphragm, the center of the diaphragm can be connected to the beam through a connecting rod. the first position of structure 111).
  • the above-mentioned connecting rod can also be regarded as a part of the mass element 120 .
  • the position of the resonance valley of the frequency response curve of the output device 100 can be adjusted without changing or substantially not changing the position of the resonance peak. , so that the frequency position corresponding to the resonance peak and the frequency position corresponding to the resonance valley on the frequency response curve of the acoustic output device 100 are close to or the same, thereby reducing the uneven range of the frequency response curve caused by the resonance peak and the resonance valley or the resonance.
  • the frequency positions of the peak and the resonant valley are the same, peak and valley cancellation is achieved, and a smooth curve with a wider frequency band is obtained, thereby improving the sound quality of the acoustic output device.
  • the resonance peak here may refer to a peak with a higher amplitude on the frequency response curve corresponding to the beam structure 111 (or the first position).
  • the resonance peak may be generated by the beam structure resonating near its resonance frequency.
  • the beam structure 111 may have multiple resonance frequencies, and accordingly, the frequency response curve may have multiple resonance peaks.
  • the resonance valley may refer to a valley with a lower amplitude on the frequency response curve corresponding to the beam structure 111 (or the first position).
  • the reasons for the formation of the resonance valley may include but are not limited to the segmentation vibration of the piezoelectric layer of the beam structure 111 , causing the radiated sound pressure of the beam structure 111 to invert and cancel at the first position, making it difficult to output vibration.
  • the piezoelectric layer can produce divided vibrations near multiple frequencies, and accordingly, the frequency response curve can have multi-order resonance valleys.
  • the frequency response curve of the acoustic output device 100 can achieve cancellation of the resonance peak and the resonance valley, and obtain a smooth curve with a wider frequency band, thereby improving the sound quality of the acoustic output device.
  • the ratio between the distance from the first position to one end of the beam structure 111 and the length of the beam structure 111 may range from 0.1 to 0.99.
  • the ratio between the distance from the first position to one end of the beam structure 111 and the length of the beam structure 111 may range from 0.2 to 0.95. In some embodiments, the ratio between the distance from the first position to one end of the beam structure 111 and the length of the beam structure 111 may range from 0.3 to 0.95.
  • a first position at which the first-order resonance valley and the second-order resonance peak can be eliminated can be determined, so that the frequency response curve of the acoustic output device 100 has a first resonance peak and a second resonance peak, and the first resonance peak and the second resonance peak are between the first resonance peak and the second resonance peak.
  • the ratio between the frequency ranges is greater than 17, and the amplitude difference between the lowest point of the frequency response between the first resonant peak and the second resonant peak and the first resonant peak or the second resonant peak is less than 40dB, so that the frequency of the acoustic output device 100
  • the response curve obtains a smooth curve with a wider frequency band at a lower frequency.
  • the first position at which the first-order resonance valley and the third-order resonance peak cancel each other can be determined, so that the frequency response curve of the acoustic output device 100 has a first resonance peak, a second resonance peak and a third resonance peak, wherein the There is a smooth transition between the first resonant peak and the second resonant peak, a smooth transition between the second resonant peak and the third resonant peak, and the ratio of the frequency ranges of the second resonant peak and the third resonant peak is greater than 4, so that the frequency range of the acoustic output device 100
  • the response curve obtains a smooth curve with a wider frequency band at higher frequencies.
  • this specification refers to the effect of increasing the amplitude achieved when the frequency positions of the resonance peak and the resonance valley are close to or the same as peak and valley cancellation.
  • the peak and valley cancellation described in this specification may include the resonance peak and the resonance valley canceling each other when the frequency positions of the resonance peak and the resonance valley are the same, or may include the resonance peak and resonance valley being harmonious when the frequency positions of the resonance peak and the resonance valley are close to each other.
  • the uneven range of the frequency response curve caused by the vibration valley is reduced, or the amplitude near the resonance peak is reduced and/or the amplitude near the resonance valley is increased.
  • the acoustic output device 100 may further include a second vibration element, the second vibration element includes a second beam structure, and the second beam structure may be connected to the beam structure 111.
  • the length direction of the second beam structure is perpendicular to the projection of the length direction of the beam structure 111 along the vibration direction of the vibrating element 110 .
  • the acoustic output device 100 may further include a third vibration element.
  • the third vibration element may include a third beam structure. In a plane perpendicular to the vibration direction of the beam structure 111, the third beam structure is flexible with the beam structure 111. connect. In some embodiments, the third beam structure extends along the length direction of the beam structure 111, one end of the beam structure 111 and the third beam structure is a fixed end, and the other end of the beam structure 111 and the third beam structure is connected through an elastic connector.
  • the third vibration element please refer to Figure 19 and its related description, which will not be described again here.
  • the acoustic output device 100 may also include one or more components (eg, signal transceiver, interaction module, battery, etc.). In some embodiments, one or more components of the acoustic output device 100 may be replaced with other components that perform similar functions. Such changes and modifications would not depart from the scope of this specification.
  • FIG 2 is a schematic diagram of an exemplary beam structure shown in accordance with some embodiments of the present specification.
  • the beam structure 211 may be a cantilever beam.
  • One end of the beam structure 211 is a fixed end 2111, and the other end away from the fixed end 2111 in the length direction (the x direction shown in Figure 2) is a free end 2112.
  • the fixed end 2111 refers to the position on the working beam structure 211 where the vibration acceleration or acceleration level is less than the vibration acceleration threshold or acceleration level threshold and the rotation angle of its cross-section is less than the rotation angle threshold.
  • the vibration acceleration level of the fixed end 2111 may be less than 5dB, 3dB, 1dB, 0.8dB, 0.6dB, 0.4dB, 0.2dB, or 0.05dB, etc.
  • the rotation angle of the cross-section may be less than 3°, 2°, 1 °, 0.5°, 0.2° or 0.05°, etc.
  • the fixed end 2111 is connected to a fixed location or structure (eg, a housing) of the acoustic output device.
  • the fixed position or structure here may refer to a position or structure on the acoustic output device where the vibration acceleration or acceleration level is less than the vibration acceleration threshold or acceleration level threshold.
  • the fixed end 2111 can be fixed on the fixed support 212, and the fixed support 212 is connected to a fixed position or structure of the acoustic output device.
  • the acoustic output device may include a housing (not shown in FIG. 2 ), the beam structure 211 may be disposed in the housing, the fixed support 212 is fixed on the housing, and the fixed end 2111 of the beam structure 211 may be connected to the housing.
  • the fixed support 212 is fixedly connected.
  • the free end 2112 refers to the end of the beam structure 211 that is free to vibrate. In some embodiments, the free end 2112 may be in a floating or unconstrained state.
  • beam structure 211 may include piezoelectric layer 2113 and base layer 2114.
  • the piezoelectric layer 2113 and the base layer 2114 extend along the length direction of the beam structure 211 .
  • the piezoelectric layer 2113 deforms along the length direction, and the deformation drives the base layer 2114 (or the vibrating element) to produce an electric field along the direction perpendicular to the beam structure. 211 vibrates in the length direction.
  • piezoelectric layer 2113 may be made of piezoelectric material.
  • the material of the base layer 2114 includes, but is not limited to, metals and alloys, glass fibers, carbon fibers, etc. or any combination thereof.
  • the piezoelectric layer 2113 and the base layer 2114 may be overlapped in the thickness direction of the beam structure 211.
  • the beam structure 211 may include a multi-layer piezoelectric layer 2113 and a base layer 2114, and the multi-layer piezoelectric layer 2113 and the base layer 2114 are overlapped in the thickness direction.
  • the mass element may be connected to the beam structure 211 at a first location.
  • the first position of the beam structure 211 may be different positions along the length direction of the beam structure 211, for example, point a, point b, point c, point d, point e shown in Figure 2 , f point, g point, etc.
  • the vibration modes at different first positions on the beam structure 211 are different, and the vibration modes output to the mass element connected to the first position are also correspondingly different, thus causing the frequency response curves of the acoustic output device to be different, See Figure 3 and its related description for details.
  • Figure 3 is a frequency response curve diagram of different positions on the beam structure according to some embodiments of the present specification.
  • curve 31, curve 32, curve 33, curve 34, curve 35, curve 36 and curve 37 are respectively point a, The frequency response curves of point b, point c, point d, point e, point f and point g.
  • the impact of the mass element on the vibration of the beam structure 211 is small or zero.
  • the curves 31-37 can also be used to characterize the acoustic output device (for example, when the mass element is connected to the above-mentioned 7 first positions) respectively. Frequency response curve of the acoustic output device 100).
  • the vibration at different first positions on the beam structure 211 produces multiple resonance peaks (for example, the first-order resonance peak A, the second-order resonance peak B, the third-order resonance peak C etc.), the resonance peak positions generated at different first positions are approximately the same, and as the first position gradually approaches the fixed end 2111 of the beam structure 211, the resonance valley corresponding to the frequency response curve gradually moves toward high frequency.
  • the resonance peak positions generated at different first positions are approximately the same, and as the first position gradually approaches the fixed end 2111 of the beam structure 211, the resonance valley corresponding to the frequency response curve gradually moves toward high frequency.
  • the curve 34 corresponding to point d is a smooth transition between the first-order resonance peak A and the second-order resonance peak B; another example is the curve 33 corresponding to point c, which is a smooth transition between the first-order resonance peak A and the second-order resonance peak B.
  • the curve transitions smoothly, and the curve between the second-order resonance peak B and the third-order resonance peak C transitions smoothly.
  • the amplitude of the acoustic output device at medium and low frequencies gradually decreases, thereby reducing the acoustic output.
  • a suitable first position can be selected so that the frequency response curve of the acoustic output device smoothly transitions between the resonance peaks in the audible range of the human ear (for example, 50Hz-10000Hz), and does not excessively reduce the frequency response of the acoustic output device in the audible range of the human ear.
  • Low frequency sensitivity the position within the range near point c can be used as the first position, thereby improving the sound quality of the acoustic output device while ensuring that the acoustic output device still has high sensitivity in the mid- to low-frequency range.
  • the ratio between the distance from point c to the fixed end 2111 and the length of the beam structure 211 may be in the range of 0.45-0.55.
  • the curve 37 transitions smoothly in the range of 500Hz-10000Hz, which is specifically manifested as a small or no resonance peak and/or resonance valley between the first-order resonance peak A and the third-order resonance peak C.
  • the amplitude difference between the lowest point of the frequency response between the first-order resonance peak A and the third-order resonance peak C (for example, point P shown in Figure 3) and the first resonance peak or the second resonance peak is less than 40dB. This is because the first-order resonance valley corresponding to the curve 37 cancels the second-order resonance peak, so that the curve 37 has no resonance peak and/or resonance valley near the frequency corresponding to the second-order resonance peak B.
  • a suitable first position (e.g., g-point) can be selected such that the first-order resonance valley and the second-order resonance peak of the acoustic output device cancel each other, so that within the human ear's partial audible range (e.g., 50Hz-10000Hz) It has a first resonant peak (i.e., the first-order resonant peak A) and a second resonant peak (i.e., the third-order resonant peak C).
  • the ratio of the frequencies of the second resonant peak and the first resonant peak is greater than 17, which increases the curve 37 The frequency range corresponding to the upper smooth curve, thereby further improving the sound quality of the acoustic output device.
  • the ratio between the distance from point g to the fixed end 2111 and the length of the beam structure 211 is in the range of 0.75-0.95. In some embodiments, the ratio between the distance from point g to the fixed end 2111 and the length of the beam structure 211 is in the range of 0.78-0.85. In some embodiments, the ratio between the distance from point g to the fixed end 2111 and the length of the beam structure 211 may be 0.81.
  • a suitable first position can be selected so that the frequency response curve of the acoustic output device can have peak and valley cancellation within a specific frequency range (for example, 500Hz-10000Hz), thereby eliminating poor frequency response in the specific frequency range.
  • the resonance valley of the acoustic output device is increased, and the frequency range corresponding to the smooth curve on the frequency response curve of the acoustic output device is increased to improve the sound quality of the acoustic output device.
  • the first position (or the ratio between the first position and the length of the beam structure) can be determined by calculation, so that the frequency response curve of the acoustic output device at the first position achieves peak and valley cancellation.
  • the displacement of each position point on the beam structure can be expressed as:
  • Y(x) is the vibration shape function
  • ⁇ (t) is the harmonic function with respect to time
  • x represents the distance from the position point on the beam structure to one end of the beam structure (for example, the fixed end 2111 of the beam structure 211)
  • u( x,t) satisfies the differential equation of motion:
  • E is the elastic modulus of the beam structure
  • I is the moment of inertia of the cross-section of the beam structure
  • ⁇ is the material density of the beam structure
  • A is the cross-sectional area of the beam structure
  • F is the external force on the beam structure.
  • C 1 -C 6 are constants
  • w is the circle frequency
  • the natural mode function corresponding to different beam structures is determined.
  • the beam structure 211 shown in Figure 2 has a fixed end displacement of zero and a rotation angle (proportional to the first-order derivative of the displacement).
  • the resonant peak position of the acoustic output device is relatively fixed, and as the first position gradually approaches the fixed end of the beam structure, the resonant valley gradually moves to high frequency, and can be When it moves to the same or similar frequency position as the resonant peak, it cancels the resonant peak. Therefore, the vibration node of the natural mode function of the beam structure at the resonance peak is the first position where the peak and valley cancellation of the frequency response curve of the beam structure can be achieved.
  • the solution The distance from the fixed end 2111, the ratio between the distance from the first position to the fixed end 2111 of the beam structure 211 and the length of the beam structure 211 is approximately 0.774.
  • the ratio between the distance from the first position to the fixed end 2111 of the beam structure 211 and the length of the beam structure 211 is about 0.501;
  • the ratio between the distance from the first position to the fixed end 2111 of the beam structure 211 and the length of the beam structure 211 is approximately 0.868.
  • a first position capable of canceling the first-order resonance valley and the second-order resonance peak can be selected as the vibration output position of the acoustic output device, thereby causing the acoustic output device to operate within a specific frequency range (for example, 500 Hz-10000 Hz). ) to achieve peak and valley cancellation.
  • a specific frequency range for example, 500 Hz-10000 Hz.
  • the acoustic output device has a first resonance peak (eg, a first-order resonance peak A) and a second resonance peak (eg, a third-order resonance peak C) in the audible range of the human ear (eg, 50Hz-10000Hz), so There is a relatively smooth curve between the first resonance peak and the second resonance peak, thereby improving the sound quality of the acoustic output device in the specific frequency range.
  • a first resonance peak eg, a first-order resonance peak A
  • a second resonance peak eg, a third-order resonance peak C
  • the audible range of the human ear eg, 50Hz-10000Hz
  • the first resonance peak of the acoustic output device and the second resonance peak are There is a smooth curve with a wider frequency band between the peaks, and the ratio between the distance from the first position to the fixed end 2111 and the length of the beam structure 211 can be in the range of 0.75-0.95. In some embodiments, the ratio between the distance from the first position to the fixed end 2111 and the length of the beam structure 211 may be in the range of 0.75-0.9.
  • the ratio between the distance from the first position to the fixed end 2111 and the length of the beam structure 211 may be in the range of 0.75-0.86. In some embodiments, the ratio between the distance from the first position to the fixed end 2111 and the length of the beam structure 211 may be in the range of 0.77-0.84.
  • a first position capable of canceling the first-order resonance valley and the third-order resonance peak can also be selected as the vibration output position of the acoustic output device, thereby causing the acoustic output device to operate within a specific frequency range (for example, 2000 Hz- 20000Hz) to achieve peak and valley cancellation.
  • the acoustic output device has a first resonance peak (eg, a first-order resonance peak A), a second resonance peak (eg, a second-order resonance peak B) and a second resonance peak in a part of the audible range of the human ear (eg, 50 Hz-15000 Hz).
  • Third resonance peak for example, fourth-order resonance peak D).
  • the amplitude difference between the lowest point of the frequency response between the second resonant peak and the third resonant peak and the second resonant peak or the third resonant peak is less than 30dB
  • the frequency between the third resonant peak and the second resonant peak is
  • the ratio is greater than 4
  • the smooth transition between the first resonance peak and the second resonance peak can further improve the sound quality of the acoustic output device in a lower frequency range (for example, 500Hz-2000Hz).
  • the distance between the first position and the fixed end 2111 and the length of the beam structure 211 are The ratio can be in the range of 0.45-0.6. In some embodiments, the ratio between the distance from the first position to the fixed end 2111 and the length of the beam structure 211 may be in the range of 0.47-0.55. In some embodiments, the ratio between the distance from the first position to the fixed end 2111 and the length of the beam structure 211 may be in the range of 0.49-0.51.
  • first position and its range described in the above embodiments are only for illustrative purposes and are not intended to limit the scope of protection of this specification.
  • different first positions can also be selected so that the resonance peaks and resonance valleys of different orders cancel (for example, the first-order resonance valley cancels the third-order resonance peak, the second-order resonance valley cancels the third-order resonance Peak cancellation, etc.), so that the acoustic output device has a smooth curve with a wider frequency band at different frequencies to adapt to the needs of different scenarios.
  • FIG. 4 is a structural schematic diagram of an exemplary beam structure according to some embodiments of the present specification.
  • the beam structure 411 shown in FIG. 4 is substantially the same as the beam structure 211 shown in FIG. 2 , and the main difference is that the beam structure 411 shown in FIG. 4 also includes a second mass element 430 .
  • the beam structure 411 includes a fixed end 4111 and a free end 4112, and the second mass element 430 is connected to the free end 4112.
  • the second mass element 430 may be similar to the mass element.
  • the second mass element 430 may be an additional mass introduced to the beam structure 411 during assembly or the like.
  • the ratio between the mass of the second mass element 430 and the mass of the beam structure may be in the range of 0-1.2.
  • the vibration mode at the first position is different from the vibration mode at the same first position when the beam structure 211 is not connected to the second mass element 430. Specifically, See Figure 5.
  • Figure 5 is a frequency response curve diagram of different points along the length of the beam structure under no-load and loaded conditions according to some embodiments of this specification.
  • the unloaded state means that there is no additional mass on the beam structure (or cantilever beam) (for example, the beam structure 211 without the second mass element 430), and the loaded state means that the beam structure 411 is connected to the second mass element 430, only As an example, the second mass element 430 corresponding to the frequency response curve shown in Figure 5 is 0.28g.
  • curve 511, curve 512, and curve 513 are respectively 1/3 of the distance from the free end on the beam structure in the no-load state (that is, the distance from the first position to the free end is 1/3 of the length of the beam structure),
  • the frequency response curves at 1/2 and 2/3, curve 521, curve 522, and curve 523 are respectively the frequency responses at 1/3, 1/2, and 2/3 from the free end on the beam structure under load.
  • the curves 511, 512 and 513 of the beam structure vibration in the no-load state are roughly the same as the curves 521, 522 and 523 of the beam structure vibration in the loaded state.
  • the curves 511, 512 and 513 of the beam structure vibration in the loaded state are substantially the same.
  • the resonance peak of the structure moves to low frequency. Therefore, the second mass element will affect the ratio of the distance from the first position where peak and valley cancellation exists to the fixed end and the length of the beam structure. See Figure 6 for details.
  • the first position mentioned here refers to the first position where there are peaks and valleys (for example, a first-order resonance valley and a second-order resonance peak) that cancel.
  • the abscissa m/m 0 represents the ratio between the mass m of the second mass element and the mass m 0 of the beam structure
  • the ordinate x/l represents the distance x between the first position and the fixed end and the beam The ratio between the length l of the structure.
  • the first position can be determined based on the ratio between the mass of the second mass element and the mass of the beam structure, so that the frequency response curve of the acoustic output device achieves peak and valley cancellation within the audible range of the human ear.
  • the ratio between the mass of the second mass element and the mass of the beam structure may be in the range of 0-1.2
  • the ratio between the distance from the first position to the fixed end and the length of the beam structure (or cantilever beam) may be in the range of 0.75- Within the range of 0.95.
  • the ratio between the mass of the second mass element and the mass of the beam structure may be in the range of 0-0.5, and the ratio between the distance from the first position to the fixed end and the length of the beam structure (or cantilever beam) may be in the range of 0.75 -0.92 range.
  • the ratio between the mass of the second mass element and the mass of the beam structure may be in the range of 0.2-1, and the ratio between the distance from the first position to the fixed end and the length of the beam structure (or cantilever beam) may be in the range of 0.8 -0.95 range.
  • FIG. 7 is a structural schematic diagram of an exemplary beam structure according to some embodiments of the present specification.
  • the beam structure 711 shown in FIG. 7 is substantially the same as the beam structure 211 shown in FIG. 2 .
  • the main difference is that the beam structure 711 shown in FIG. 7 includes a hinge end 7112 .
  • the beam structure 711 includes a fixed end 7111 and a hinge end 7112.
  • the fixed end 7111 and the hinge end 7112 are respectively the beam structure 711 deviating from each other along the length direction (for example, the x direction shown in Figure 7). Both ends, among which the fixed end 7111 is similar to the fixed end 2111.
  • the hinge end 7112 is a rotatable end.
  • the hinge end 7112 has an axis perpendicular to the length direction of the beam structure 711 and the vibration direction (eg, the z direction shown in Figure 7) (for example, an axis parallel to the y direction shown in Figure 7) , the hinge end 7112 can rotate around the axis.
  • Figure 8 is a schematic structural diagram of a hinge end according to some embodiments of this specification. In some embodiments, as shown in FIG. 8 , both sides of the hinge end 7112 along its length (i.e., the y direction) can be relatively fixedly connected to the hinge rod 713 , and the axis where the hinge rod 713 is located (as shown in FIG.
  • the beam structure 711 (or acoustic output device) may also include hinge supports 714 , which may be secured in the acoustic output device (eg, on a housing) and may include hinge holes 7141 .
  • the hinge rod 713 is disposed in the hinge hole 7141 and can rotate in the hinge hole 7141. When the beam structure 711 vibrates along its vibration direction, the hinge end 7112 can rotate relative to the hinge support 714 along the axis where the hinge rod 713 is located.
  • the hinge rod 713 may be physically connected to the hinge support end 7112.
  • the hinge rod 713 and the hinge support end 7112 may be an integral structure.
  • a first position thereon may be determined such that The frequency response curve of the acoustic output device generates peak and valley cancellation to increase the smooth curve range of the frequency response curve of the acoustic output device within the audible range of the human ear, thereby improving the sound quality of the acoustic output device.
  • the solution The distance from the fixed end 7111, the ratio between the distance from the first position to the fixed end 7111 of the beam structure 711 and the length of the beam structure 711 is about 0.56. In the same way, it can be found that when the first-order resonance valley and the third-order resonance peak of the beam structure 711 cancel, the ratio between the distance from the first position to the fixed end 7111 of the beam structure 711 and the length of the beam structure 711 is about 0.39 and 0.69.
  • a first position that enables the first-order resonance valley and the second-order resonance peak to cancel can be selected as the vibration output position on the beam structure 711, thereby allowing the acoustic output device to be in a part of the audible range of the human ear (eg, 50Hz-10000Hz) has a first resonance peak (for example, the first-order resonance peak A as shown in Figure 3) and a second resonance peak (for example, the third-order resonance peak C as shown in Figure 3), the first resonance There is a smoother curve between the peak and the second resonance peak, thereby improving the sound quality of the acoustic output device in this specific frequency range.
  • a first resonance peak for example, the first-order resonance peak A as shown in Figure 3
  • a second resonance peak for example, the third-order resonance peak C as shown in Figure 3
  • the frequency range of the second resonance peak is the same as that of the first resonance peak.
  • the ratio of the frequency ranges of the peaks can be greater than 6, so that the first resonant peak and the second resonant peak of the acoustic output device have a smooth curve, and the ratio between the distance from the first position to the fixed end 7111 and the length of the beam structure 711 can be Within the range of 0.5-0.6.
  • the ratio between the distance from the first position to the fixed end 7111 and the length of the beam structure 711 may be in the range of 0.52-0.59.
  • the ratio between the distance from the first position to the fixed end 7111 and the length of the beam structure 711 may be in the range of 0.54-0.58.
  • the first position that enables the first-order resonance valley and the third-order resonance peak to cancel can also be selected as the vibration output position on the beam structure 711, so that the acoustic output device can achieve peak and valley cancellation.
  • the acoustic output device has a first resonance peak (for example, the first-order resonance peak A as shown in Figure 3), a second resonance peak (for example, as shown in Figure 3) in the audible range of the human ear (for example, 50Hz-15000Hz) The second-order resonance peak B shown in Figure 3) and the third-order resonance peak (for example, the fourth-order resonance peak D shown in Figure 3).
  • the distance between the first position and the fixed end 7111 and the length of the beam structure 711 are The ratio may be in the range of 0.35-0.45; in some embodiments, the ratio between the distance from the first position to the fixed end 7111 and the length of the beam structure 711 may be in the range of 0.36-0.43; in some embodiments, the first The ratio between the distance from the position to the fixed end 7111 and the length of the beam structure 711 may be in the range of 0.37-0.41.
  • the distance between the first position and the fixed end 7111 and the length of the beam structure 711 are The ratio can also be in the range of 0.65-0.75; in some embodiments, the ratio between the distance from the first position to the fixed end 7111 and the length of the beam structure 711 can be in the range of 0.67-0.72; in some embodiments, the The ratio between the distance from a position to the fixed end 7111 and the length of the beam structure 711 may be in the range of 0.68-0.7.
  • FIG. 9 is a structural schematic diagram of an exemplary beam structure according to some embodiments of the present specification.
  • the beam structure 911 shown in FIG. 9 is substantially the same as the beam structure 711 shown in FIG. 7 .
  • the main difference is that the beam structure 911 shown in FIG. 9 includes an elastic end 9112 .
  • the beam structure 911 includes a fixed end 9111 and an elastic end 9112 .
  • the fixed end 9111 and the elastic end 9112 are respectively two opposite ends of the beam structure 911 .
  • the fixed end 9111 is similar to the fixed end 7111.
  • the elastic end 9112 is an end of the beam structure 911 that is elastically connected to other components on the acoustic output device (for example, the housing).
  • the beam structure 211 (i.e., the free beam) may be equivalent to the beam structure 911 when the elastic coefficient k corresponding to the elastic end 9112 is 0, and the beam structure 711 may be equivalent to the elastic coefficient k corresponding to the elastic end 9112 Beam structure 911 when is ⁇ .
  • FIG. 10 is a structural schematic diagram of an exemplary beam structure according to some embodiments of the present specification.
  • the beam structure 1011 shown in FIG. 10 is substantially the same as the beam structure 711 shown in FIG. 7 .
  • the main difference is that the beam structure 1011 shown in FIG. 10 includes two hinge ends 10111 and 10112 respectively.
  • the two hinged support ends 10111 and 10112 are respectively two opposite ends of the beam structure 1011, wherein the hinged support ends 10111 and 10112 may be similar to the hinged support end 7112.
  • the first position on the beam structure 1011 can be determined so that the frequency response curve of the acoustic output device generates peak and valley cancellation, so as to increase the frequency response curve of the acoustic output device
  • the natural mode function of the beam structure 1011 can be expressed as:
  • the beam structure 1011 can be a symmetrical structure at both ends (ie, the hinge ends 10111 and 10112), and its even-order resonance mode disappears when it is actually driven by piezoelectricity. , only odd-order resonance peaks remain. It can be found that when the first-order resonance valley and the third-order resonance peak of the beam structure 1011 cancel, the ratio between the distance from the first position to the hinge end 10111 of the beam structure 1011 and the length of the beam structure 1011 is approximately 0.33 or 0.67.
  • the first position that enables the first-order resonance valley and the third-order resonance peak to cancel can also be selected as the vibration output position on the beam structure 1011, so that the acoustic output device can achieve peak and valley cancellation.
  • the acoustic output device has a first resonance peak, a second resonance peak and a third resonance peak in part of the audible range of the human ear (eg, 50 Hz-15000 Hz).
  • the first-order resonance valley moves to high frequency, there is a smooth transition between the first resonance peak and the second resonance peak, and a smooth transition between the second resonance peak and the third resonance peak, and the frequency range of the smooth curve is wider, so Improves the sound quality of acoustic output devices.
  • the ratio of the frequency range of the second resonance peak to the frequency range of the first resonance peak may be greater than 10.
  • the frequency range of the smooth curve is wider, that is, the first-order resonance valley and the third-order resonance peak of the beam structure 1011 cancel, the first position
  • the ratio between the distance to one of the two hinge ends and the length of the beam structure 1011 may be in the range of 0.3-0.4.
  • the ratio between the distance from the first position to one of the two hinge ends 10111 and the length of the beam structure 1011 may be in the range of 0.3-0.37.
  • the ratio between the distance from the first position to one of the two hinge ends 10111 and the length of the beam structure 1011 may be in the range of 0.31-0.35.
  • FIG. 11A is a structural schematic diagram of an exemplary beam structure according to some embodiments of the present specification.
  • the beam structure 1111 shown in FIG. 11A is substantially the same as the beam structure 211 shown in FIG. 2 , and the main difference is that the beam structure 1111 shown in FIG. 11A includes a fixed end 11111 and a fixed end 11112.
  • the two fixed ends are two ends of the beam structure 1111 that are away from each other along the length direction (the x direction as shown in FIG. 11A ).
  • the fixed ends may be similar to the fixed end 2111 .
  • the first position on the beam structure 1111 as shown in FIG. 11A can be determined so that the frequency response curve of the acoustic output device generates peak and valley cancellation, so as to increase the frequency response curve of the acoustic output device.
  • the natural mode function of the beam structure 1111 can be expressed as:
  • the first-order resonance valley and The ratio between the distance from the first position where the third-order resonance peak cancels to one of the fixed ends and the length of the beam structure 1111 is about 0.36 or 0.64.
  • the beam structure 1111 including the fixed end 11111 and the fixed end 11112 may be a two-end symmetrical structure, that is, the beam structure 1111 is symmetrical along the axis L, where L passes through the midpoint O and is equal to the width of the beam structure 1111 The direction y is parallel.
  • the electrodes of the piezoelectric layer on the beam structure 1111 may also be symmetrical along the axis L. Therefore, when the beam structure 1111 vibrates, the stresses on the beam structure 1111 on both sides of the axis L are symmetrically distributed, and the rotation angle of the midpoint O is 0.
  • FIG. 11B is a schematic diagram of vibration modes of the beam structure 1111 shown in FIG. 11A. As shown in Figure 11B, (a), (b) and (c) in Figure 11B respectively represent the 1st, 3rd and 5th order vibration mode curves of the beam structure 1111.
  • the beam structure 1111 when the beam structure 1111 is driven by piezoelectricity, its even-order resonance mode disappears, leaving only Resonant modes of odd order. Therefore, as shown in Figure 11B, the actual vibration of the beam structure 1111 does not include even-order vibration modes (for example, the frequency response curve of the beam structure 1111 does not include second-order peaks, second-order valleys, fourth-order peaks, fourth-order valleys, etc.) , further combined with (a), (b) and (c) in Figure 11B, the mode shape function Y i (x) does not intersect with the horizontal axis at the midpoint O. Therefore, the midpoint O of the beam structure 1111 cannot become The vibration nodes of the beam structure 1111 cannot become peak-valley cancellation points.
  • even-order vibration modes for example, the frequency response curve of the beam structure 1111 does not include second-order peaks, second-order valleys, fourth-order peaks, fourth-order valleys, etc.
  • Figure 12 is a frequency response curve diagram of different points along the length of the beam structure according to some embodiments of this specification.
  • curve 121, curve 122, curve 123, curve 124 and curve 125 are respectively the ratio between the distance from the beam structure 1111 to one of the fixed ends shown in Figure 11A and the length of the beam structure 1111 is 0.31
  • the frequency response curves of the five position points of 0.36 i.e., the theoretical first position where the first-order resonance valley and the third-order resonance peak are eliminated
  • 0.41, 0.45, and 0.5 can respectively represent when the mass element is connected to the above five positions.
  • Frequency response curve of the acoustic output device i.e., the theoretical first position where the first-order resonance valley and the third-order resonance peak are eliminated
  • the frequency response curve corresponding to the above five position points has multiple resonance peaks (for example, resonance peak E, resonance peak F, resonance peak G, etc.), and when the vibration output point ( First position)
  • the frequency response curve shows that the frequency position of each resonance peak remains basically unchanged, and the resonance valley gradually moves from high frequency to low frequency.
  • the resonant frequencies of each order on the beam structure 1111 can be expressed as:
  • the resonance peak E, the resonance peak F, and the resonance peak G can be the first-order resonance peak, the third-order resonance peak, and the fifth-order resonance peak respectively.
  • the vibration of structure 1111 does not include even-order vibration modes.
  • the first position can be adjusted so that the first-order resonance valley and the third-order resonance peak of the beam structure 1111 cancel.
  • the frequency response curve of the acoustic output device can have the first resonance peak (i.e. The first-order resonance peak E) and the second-order resonance peak (i.e.
  • the ratio between the distance from the first position to one of the two fixed ends and the length of the beam structure 1111 may be in the range of 0.3-0.4. In some embodiments, the ratio between the distance from the first position to one of the two fixed ends and the length of the beam structure 1111 may be in the range of 0.32-0.4. In some embodiments, the ratio between the distance from the first position to one of the two fixed ends and the length of the beam structure 1111 may be in the range of 0.34-0.38.
  • the frequency response curve of the vibration output point near the midpoint of the beam structure 1111 has a large resonance valley (for example, the resonance valley H shown in Figure 12).
  • the reason may be:
  • the beam structure 1111 generates a curl mode in the width direction (y direction as shown in FIG. 11A), which affects the amplitude of the resonance valley of the frequency response curve.
  • the first position can be adjusted to be near the midpoint of the length direction of the beam structure 1111. At this time, if the influence of the curl mode is not considered, the frequency response curve of the acoustic output device can have a first resonance peak (i.e.
  • the smooth transition between the resonance peak F and the fifth-order resonance peak G improves the sound quality of the acoustic output device.
  • the amplitude difference between the lowest point of the frequency response between the second resonant peak and the third resonant peak and the second resonant peak or the third resonant peak may be less than 40dB, and the third resonant peak and the third resonant peak may be less than 40dB.
  • the ratio of the frequency ranges of the two resonant peaks can be greater than 2, and there is a smooth transition between the second resonant peak and the third resonant peak.
  • the ratio between the distance from the first position to one of the two fixed ends and the length of the beam structure 1111 may be in the range of 0.45-0.5.
  • Figure 13 is a frequency response curve diagram of different position points in the width direction of the beam structure according to some embodiments of this specification.
  • curve 131, curve 132, curve 133, curve 134, curve 135 and curve 136 are respectively the ratio between the distance from the beam structure 1111 to the side 11113 shown in Figure 11A and the width of the beam structure 1111 are the frequency response curves of the six position points of 0.5, 0.4, 0.3, 0.22, 0.1 and 0, where the side 11113 refers to one of the two sides perpendicular to the width direction of the beam structure 1111, and the above 6
  • the position points are all midpoints in the length direction.
  • curve 134 is smoother than other curves. Among them, there is a smooth transition between the first-order resonance peak E and the third-order resonance peak F, and between the third-order resonance peak F and the fifth-order resonance peak G. .
  • the curling mode in the width direction of the beam structure 1111 can be approximated by the first-order mode shape of the beam structure with free ends at both ends, and its first-order natural mode function can be expressed as:
  • x′ represents the distance from the point on the beam structure 1111 to the side 11113
  • L represents the width of the beam structure.
  • the first position is to one side of the beam structure 1111
  • the ratio between the distance and the width of the beam structure 1111 may be in the range of 0.1-0.4.
  • the ratio between the distance from the first position to one side of the beam structure 1111 and the width of the beam structure 1111 may be in the range of 0.15-0.3.
  • the ratio between the distance from the first position to one side of the beam structure 1111 and the width of the beam structure 1111 may be in the range of 0.18-0.36.
  • FIG. 14A is a structural schematic diagram of a beam structure according to some embodiments of the present specification.
  • the beam structure 1411 shown in FIG. 14A is substantially the same as the beam structure 1111 shown in FIG. 11A .
  • the main difference is that the beam structure 1411 shown in FIG. 14A includes an elastic end 14111 and an elastic end 14112 .
  • the elastic end 14111 and the elastic end 14112 are respectively two opposite ends of the beam structure 1411 .
  • the two elastic ends can be connected to other components of the acoustic output device (eg, beam structure fixed supports, housings, etc.) through elastic members 1412.
  • the acoustic output device eg, beam structure fixed supports, housings, etc.
  • the elastic member 1412 may be an elastic component.
  • the elastic member 1412 may be an elastic structure, and exemplary elastic structures may include continuous bending structures, spiral structures, leaf spring structures, mechanical springs, air springs, electromagnetic springs, etc. or any combination thereof.
  • the elastic member 1412 may be made of elastic material, and exemplary elastic materials may include foam, rubber, latex, silicone, sponge, etc. or any combination thereof.
  • the beam structure 1411 may be a bisymmetric structure.
  • the elastic members 1412 corresponding to the elastic end 14111 and the elastic end 14112 may be symmetrically arranged along the length direction and/or width direction of the beam structure.
  • the elastic end 14111 is connected to other components of the acoustic output device through at least two elastic members 1412.
  • at least two elastic members 1412 may be symmetrically distributed along the beam structure 1411.
  • FIG. 14B is a schematic diagram of vibration modes of the beam structure 1411 shown in FIG. 14A.
  • (a)-(e) respectively represent the vibration mode curves of the beam structure 1411 under different vibration modes.
  • (a) shows the initial vibration mode of the beam structure 1411.
  • the beam structure 1411 which begins to be driven by piezoelectricity, first vibrates in the middle and drives the elastic members 1412 on both sides to vibrate.
  • the elastic member 1412 resonates with the elastic mass formed by the beam structure 1411, and the resonance can generate a first resonance peak.
  • the resonant frequency corresponding to the first resonant peak may be between 300 Hz and 700 Hz.
  • the frequency response curve of the beam structure 1411 shown in FIG. 15 has a first resonance peak I around 500 Hz. Furthermore, as the frequency increases, the middle part of the vibration mode curve as shown in (c) sinks, and the midpoint intersects with the horizontal axis. Correspondingly, the midpoint of the beam structure 1411 generates a vibration node, and the frequency response curve corresponding to the midpoint may have a resonance valley (for example, resonance valley J as shown in FIG. 15 ). As the frequency continues to increase, the beam structure 1411 may resonate at its natural resonant frequency, which resonance creates a second resonance peak. (d) shows a resonant mode of the beam structure 1411 in which the beam structure 1411 can resonate near the resonant frequency.
  • the resonant frequency may be between 3300Hz-4300Hz.
  • the frequency response curve of the beam structure 1411 shown in FIG. 15 has a second resonance peak K around 3800 Hz.
  • the middle part of the vibration mode curve continues to sink, and generates two intersection points with the horizontal axis near the end.
  • the beam structure 1411 generates vibration nodes at these two intersection points, and the corresponding frequency response curve may have a resonance valley.
  • the beam structure 1411 may resonate at another of its natural resonant frequencies, which resonance creates a third resonance peak.
  • (e) shows a resonant mode of the beam structure 1411 at another natural resonant frequency in which the beam structure 1411 can resonate near another resonant frequency.
  • the resonant frequency may be between 12 kHz and 18 kHz.
  • the frequency response curve of the beam structure 1411 shown in FIG. 15 has a third resonance peak L around 15000 Hz.
  • the middle part and both ends of the vibration mode curve sink and produce four intersection points with the horizontal axis.
  • the beam structure 1411 generates vibration nodes at these four intersection points, and the corresponding frequency response curve may have a resonance valley.
  • the position close to the elastic end can be selected as the first position, so that the curves between the resonant peaks of the acoustic output device can be smoothly transitioned, thereby improving the sound quality of the acoustic output device.
  • the ratio between the distance from the first position to one of the elastic ends and the length of the beam structure 1411 may be in the range of 0.1-0.25. In some embodiments, the ratio between the distance from the first position to one of the elastic ends and the length of the beam structure 1411 may be in the range of 0.15-0.2.
  • Figure 15 is a frequency response curve diagram of different positions on the beam structure according to some embodiments of the present specification.
  • curve 151 is the frequency response curve at the elastic end (for example, elastic end 14111 or 14112) of the beam structure 1411
  • curve 152 is the frequency response curve at the midpoint of the beam structure 1411
  • curve 153 is the frequency response curve of the beam structure 1411.
  • the frequency response curve at the first position on 1411, wherein the ratio between the distance from the first position to one of the elastic ends (for example, the elastic end 14111) and the length of the beam structure 1411 is 0.2.
  • the frequency response curve of the acoustic output device when the output position is the elastic end or the first position, the frequency response curve of the acoustic output device has no or small resonance valleys in the frequency range of 500Hz-15000Hz, and between each resonance peak (for example, There is a smooth transition between the first resonance peak I and the second resonance peak K, and between the second resonance peak K and the third resonance peak L), and the frequency response is better.
  • combining curve 151 and curve 153 it can be seen that in a lower frequency range (eg, less than 500 Hz), the vibration of the first position may have a higher amplitude compared with the elastic end. Therefore, the low frequency sensitivity at the first position is higher than that at the elastic end.
  • the first position connecting the mass element on the beam structure 1411 can be close to the elastic end, wherein the ratio between the distance from the first position to one of the elastic ends and the length of the beam structure 1411 can be in the range of 0.15-0.2, In order to obtain the smoothest frequency response curve while ensuring the low-frequency sensitivity of the acoustic output device.
  • the vibration of the elastic mass composed of the elastic member 1412 and the beam structure 1411 can generate a resonance peak in a lower frequency range, thereby improving the sensitivity of the acoustic output device in the low frequency range.
  • curves 151 and 152 have a first resonance peak I in a lower frequency range (eg, 300Hz-700Hz).
  • the elastic end (for example, the elastic end 14111 and The overall equivalent elastic coefficient of the elastic member 1412 corresponding to the elastic end 14112) may be in the range of 3500-4000N/m. In some embodiments, the overall equivalent elastic coefficient of the elastic member 1412 corresponding to the elastic end may be in the range of 3700-3900 N/m.
  • Figure 16A is a structural schematic diagram of a beam structure according to some embodiments of the present specification.
  • the beam structure 1611 shown in Figure 16A is substantially the same as the beam structure 1411 shown in Figure 14A.
  • the main difference is that the two ends of the beam structure 1611 shown in Figure 16A are free ends (for example, free end 16111 and free end 16112), and is connected to the fixed position or structure (for example, fixed support) of the acoustic output device through the elastic member 1612 provided in the middle.
  • the elastic member 1612 please refer to the description of the elastic member 1412 in FIG. 14A.
  • one end of the elastic member 1612 is connected to the middle part of the beam structure, and the other end is connected to the fixed position or structure of the acoustic output device.
  • the middle part of the beam structure 1611 may refer to a certain area close to the midpoint of its axis.
  • elastic members 1612 are provided on both sides of the beam structure 1611 perpendicular to its axis.
  • the connection line of the elastic members 1612 on both sides of the beam structure 1611 may be perpendicular to the axis of the beam structure 1611.
  • the elastic members 1612 on both sides of the beam structure 1611 can also be symmetrically arranged along a center line perpendicular to the axis of the beam structure 1611 (for example, the center line M as shown in Figure 16A).
  • the elastic members 1612 on both sides of the beam structure 1611 may also be spaced at the same distance from a center line perpendicular to the axis of the beam structure 1611 (for example, the center line M as shown in FIG. 16A ).
  • FIG. 16B is a schematic diagram of vibration modes of the beam structure 1611 shown in FIG. 16A.
  • (a)-(e) respectively represent the vibration mode curves of the beam structure 1611 under different vibration modes.
  • (a) shows the initial vibration mode of the beam structure 1611.
  • the beam structure 1611 which starts to be driven by piezoelectricity, first vibrates at both ends, and the two ends of the vibration mode curve sink.
  • the elastic member 1612 resonates with the elastic mass formed by the beam structure 1611, and the resonance can generate a first resonance peak.
  • the resonant frequency corresponding to the first resonant peak may be between 400 Hz and 1000 Hz.
  • the frequency response curve of the beam structure 1611 shown in FIG. 17 has a first resonance peak N around 600 Hz. Furthermore, as the frequency increases, both ends of the vibration mode curve shown in (c) lift upward, and its free end intersects with the horizontal axis. Correspondingly, the free end of the beam structure 1611 generates a vibration node, and the frequency response curve corresponding to the free end may have a resonance valley (for example, the resonance valley Q as shown in FIG. 17 ). As the frequency continues to increase, the beam structure 1611 may resonate at its natural resonant frequency, which resonance creates a second resonance peak. (d) shows a resonant mode of the beam structure 1611 in which the beam structure 1611 can resonate near the resonant frequency.
  • the resonant frequency may be between 3300Hz-4300Hz.
  • the frequency response curve of the beam structure 1611 shown in FIG. 17 has a second resonance peak R around 3650 Hz.
  • the two ends of the vibration mode curve continue to lift upward, and produce two intersection points with the horizontal axis near the free end.
  • the beam structure 1611 generates vibration nodes at these two intersection points, and the corresponding frequency response curve may have a resonance valley.
  • the beam structure 1611 may resonate at another of its natural resonant frequencies, which resonance creates a third resonance peak.
  • (e) shows a resonant mode at another natural resonant frequency of the beam structure 1611 in which the beam structure 1611 can resonate near another resonant frequency.
  • the resonant frequency may be between 12 kHz and 18 kHz.
  • the frequency response curve of the beam structure 1611 shown in FIG. 17 has a third resonance peak S around 15000 Hz.
  • the resonant mode shown in (e) the middle part and the two free ends of the vibration mode curve sink, and produce four intersection points with the horizontal axis.
  • the beam structure 1611 generates vibration nodes at these four intersection points, and the corresponding frequency response curve may have a resonance valley. According to FIG.
  • the frequency response curve corresponding to the position close to the elastic end may never have a resonance valley, and between the resonance peaks (for example, the first resonance peak N and The curves between the second resonance peak R and between the second resonance peak R and the third resonance peak S) can smoothly transition.
  • the position close to the midpoint can be selected as the first position, so that the curves between the resonant peaks of the acoustic output device can be smoothly transitioned, thereby improving the sound quality of the acoustic output device.
  • the ratio between the distance from the first position to one of the elastic ends and the length of the beam structure 1611 may be in the range of 0.3-0.7. In some embodiments, the ratio between the distance from the first position to one of the elastic ends and the length of the beam structure 1611 may be in the range of 0.4-0.6.
  • Figure 17 is a frequency response curve diagram of different positions on the beam structure according to some embodiments of the present specification.
  • curve 171 is the frequency response curve at the free end (for example, free end 16111 or 16112) of the beam structure 1611
  • curve 172 is the frequency response curve at the first position on the beam structure 1611, wherein, the The ratio between the distance from the first position to one of the free ends (eg, free end 16111) and the length of the beam structure 1611 is 0.45.
  • the frequency response curve of the acoustic output device when the output position is the first position, the frequency response curve of the acoustic output device has no or a small resonance valley in the frequency range of 500Hz-15000Hz, and the resonance peaks between each resonance peak (for example, the first resonance Peak N transitions smoothly between the second resonance peak R and between the second resonance peak R and the third resonance peak S), and the frequency response is better.
  • the first position on the beam structure 1611 where the mass element is connected can be close to the midpoint of the beam structure 1611, wherein the ratio between the distance from the first position to one of the elastic ends and the length of the beam structure 1611 can be between 0.4 and - Within the range of 0.6, in order to obtain the smoothest frequency response curve and improve the sound quality of the acoustic output device.
  • Figure 18 is a partial schematic diagram of an acoustic output device according to some embodiments of the present specification.
  • the acoustic output device includes a beam structure 1811 and a second beam structure 1821 .
  • beam structure 1811 may be the same as or similar to second beam structure 1821.
  • the beam structure 1811 and the second beam structure 1821 may be similar to the beam structure 211 shown in FIG. 2 . Refer to FIG. 2 for more description of the beam structure 1811 and the second beam structure 1821 .
  • one end of the beam structure 1811 and the second beam structure 1821 is a fixed end, and the other end is connected to each other through a connector 1830 .
  • the connector 1830 may be a resilient connector.
  • the elastic connector may be an elastic structure.
  • FIG. 19 is a schematic diagram of an acoustic output device according to some embodiments of the present specification.
  • the acoustic output device may include two or more vibrating elements, each vibrating element includes a beam structure 1911, and the beam structure 1911 includes a fixed end 19111 and a free end 19112.
  • the plurality of beam structures 1911 may be distributed at intervals around the circumference of the mass element 1920, and the mass element 1920 is respectively connected to the first position 19113 of the plurality of beam structures 1911.
  • the mass element 1920 may include a vibration plate, a diaphragm, or the like, so that the acoustic output device can output vibration through the mass element 1920 .
  • the beam structure 1911 is similar to the beam structure 211 shown in FIG. 2 , and more explanation about the beam structure 1911 can be found in FIG. 2 .
  • the plurality of beam structures 1911 may be symmetrically distributed around the circumference of the mass element 1920 along the midpoint of the mass element 1920 . In some embodiments, a plurality of beam structures 1911 may be evenly spaced around the circumference of the mass element 1920 . In some embodiments, the ratio between the distance between the first position on the plurality of beam structures 1911 connected by the mass element 1920 and the fixed end 19111 of the beam structure 1911 and the length of the beam structure may be equal.
  • the first position 19113 can be determined based on the description of other embodiments of this specification (for example, Figure 3, etc.), so that the frequency response curve of the mass element 1920 (or the acoustic output device) can achieve peak and valley cancellation, A smooth curve with a wider frequency band is obtained, thereby improving the sound quality of the acoustic output device.
  • a wider frequency range is provided between the first resonance peak and the second resonance peak of the acoustic output device.
  • the ratio between the distance between the first position on each beam structure 1911 connected by the mass element 1920 and the fixed end 19111 of the beam structure 1911 and the length of the beam structure can be 0.75- Within the range of 0.95. In some embodiments, the ratio between the distance between the first position on each beam structure 1911 to which the mass element 1920 is connected and the fixed end 19111 of the beam structure 1911 and the length of the beam structure may be in the range of 0.8-0.85. In some embodiments, in order to achieve cancellation of the first-order resonance valley and the third-order resonance peak on the frequency response curve of the mass element 1920, a wider frequency range is provided between the second resonance peak and the third resonance peak of the acoustic output device.
  • the ratio between the distance between the first position on each beam structure 1911 connected by the mass element 1920 and the fixed end 19111 of the beam structure 1911 and the length of the beam structure can be 0.45- Within the range of 0.6. In some embodiments, the ratio between the distance between the first position on each beam structure 1911 to which the mass element 1920 is connected and the fixed end 19111 of the beam structure 1911 and the length of the beam structure may be in the range of 0.5-0.55.
  • this application uses specific words to describe the embodiments of the application.
  • “one embodiment”, “an embodiment”, and/or “some embodiments” means a certain feature, structure or characteristic related to at least one embodiment of the present application. Therefore, it should be emphasized and noted that “one embodiment” or “an embodiment” or “an alternative embodiment” mentioned twice or more at different places in this specification does not necessarily refer to the same embodiment. .
  • certain features, structures or characteristics in one or more embodiments of the present application may be appropriately combined.
  • 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” indicates that a 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 confirm the breadth of the ranges in some embodiments of the present application are approximations, in specific embodiments, such numerical values are set as accurately as feasible.

Abstract

本说明书实施例公开了一种声学输出装置，包括振动元件。所述振动元件包括沿着长度方向延伸的梁结构。所述梁结构包括：压电层，用于响应电信号而发生形变，所述形变带动所述振动元件振动；以及质量元件，所述质量元件连接于所述梁结构的第一位置，所述振动元件的振动带动所述质量元件在垂直于所述长度方向的方向上振动，其中，在沿着所述梁结构的长度方向上，所述第一位置到所述梁结构一端的距离与所述梁结构的长度之间的比值在0.3～0.95范围内。

Description

一种声学输出装置 技术领域
本说明书涉及声学领域，特别涉及一种声学输出装置。
背景技术
压电材料驱动的声学输出装置利用压电材料的逆压电效应产生振动以向外辐射声波。与传统电磁式声学输出装置相比，压电材料驱动的声学输出装置具有机电换能效率高、能耗低、体积小、集成度高等优势。
但与传统电磁式声学输出装置相比，压电材料驱动的声学输出装置音质较差，导致其的原因包括：目标频率范围内的振动模态较多，无法形成较平滑的频响曲线。
因此，希望提出一种能够在目标频率范围内形成较平滑频响曲线的声学输出装置。
发明内容
本说明书实施例之一提供一种声学输出装置，包括振动元件。所述振动元件包括沿着长度方向延伸的梁结构。所述梁结构包括：压电层，用于响应电信号而发生形变，所述形变带动所述振动元件振动；以及质量元件，所述质量元件连接于所述梁结构的第一位置，所述振动元件的振动带动所述质量元件在垂直于所述长度方向的方向上振动，其中，在沿着所述梁结构的长度方向上，所述第一位置到所述梁结构一端的距离与所述梁结构的长度之间的比值可以在0.3～0.95范围内。
在一些实施例中，在50Hz-10000Hz范围内，所述质量元件的振动可以具有第一谐振峰和第二谐振峰。
在一些实施例中，所述第一谐振峰和所述第二谐振峰之间的频响最低点与所述第一谐振峰或所述第二谐振峰之间的幅值差可以小于40dB。
在一些实施例中，所述梁结构可以包括固定端和自由端。
在一些实施例中，所述声学输出装置还可以包括第二质量元件，所述第二质量元件可以与所述自由端连接。
在一些实施例中，所述第二质量元件与所述梁结构的质量之间的比值可以在0-1.2范围内。
在一些实施例中，所述第一位置到所述固定端的距离与所述梁结构的长度之间的比值可以在0.7-0.95范围内。
在一些实施例中，所述第二谐振峰的频率范围与所述第一谐振峰的频率范围之比可以大于17。
在一些实施例中，所述质量元件的振动可以具有第三谐振峰，所述第二谐振峰和所述第三谐振峰之间的频响最低点与所述第二谐振峰或所述第三谐振峰之间的幅值差可以小于30dB。
在一些实施例中，所述第三谐振峰的频率范围与所述第二谐振峰的频率范围之比可以大于4。
在一些实施例中，所述第一位置到所述固定端的距离与所述梁结构的长度之间的比值可以在0.45-0.6范围内。
在一些实施例中，所述梁结构可以包括两个固定端。
在一些实施例中，所述第一位置到所述两个固定端中一个固定端的距离与所述梁结构的长度之间的比值可以在0.3-0.4范围内。
在一些实施例中，所述第二谐振峰的频率范围与所述第一谐振峰的频率范围之比可以大于13。
在一些实施例中，所述质量元件的振动可以具有第三谐振峰，所述第二谐振峰和所述第三谐振峰之间的频响最低点与所述第二谐振峰或所述第三谐振峰之间的幅值差可以小于40dB。
在一些实施例中，所述第三谐振峰的频率范围与所述第二谐振峰的频率范围之比可以大于2。
在一些实施例中，所述第一位置到所述两个固定端中一个固定端的距离与所述梁结构的长度之间的比值可以在0.45-0.5范围内。
在一些实施例中，在沿着所述梁结构的宽度方向上，所述第一位置到所述梁结构一边的距离与所述梁结构的宽度之间的比值可以在0.15-0.3范围内。
在一些实施例中，所述梁结构可以包括固定端和铰支端，在所述振动元件振动过程中，所述铰支端可以沿与所述梁结构的长度方向和振动方向垂直的轴转动。
在一些实施例中，所述第一位置到所述固定端的距离与所述梁结构的长度之间的比值可以在0.5-0.6范围内。
在一些实施例中，所述第二谐振峰的频率范围与所述第一谐振峰的频率范围之比可以大于6。
在一些实施例中，所述梁结构可以包括两个铰支端，在所述振动元件振动过程中，所述两个铰支端可以分别沿与所述梁结构的长度方向和振动方向垂直的轴转动。
在一些实施例中，所述第一位置到所述两个铰支端中的一个铰支端的距离与所述梁结构的长度之间的比值可以在0.3-0.4范围内。
在一些实施例中，所述第二谐振峰的频率范围与所述第一谐振峰的频率范围之比可以大于10。
在一些实施例中，所述梁结构可以包括两个弹性端，所述两个弹性端可以分别通过弹性件与所述声学输出装置的固定支座弹性连接。
在一些实施例中，所述梁结构可以为两端对称结构，所述两个弹性端对应的弹性件可以沿着所述梁结构的长度方向或宽度方向对称设置。
在一些实施例中，所述第一谐振峰的频率范围可以在300Hz-700Hz。
在一些实施例中，所述第一位置到所述两个弹性端中一个弹性端的距离与所述梁结构的长度之间的比值可以在0.1-0.25范围内。
在一些实施例中，所述声学输出装置还可以包括第三振动元件，所述第三振动元件可以包括第三梁结构，其中，所述梁结构和所述第三梁结构的一端为固定端，所述梁结构和所述第三梁结构的另一端可以通过弹性连接件连接。
在一些实施例中，所述振动元件的数量可以为两个或以上，其中，所述两个或以上振动元件中每个振动元件的梁结构可以包括固定端和自由端。
在一些实施例中，所述质量元件可以分别连接于所述两个或以上振动元件中每个振动元件的梁结构的第一位置，每个梁结构的第一位置与所述梁结构的固定端之间的距离与所述梁结构的长度之间的比值可以在0.7-0.95范围内。
附图说明
图1是根据本说明书一些实施例所示的示例性声学输出装置的框图；
图2是根据本说明书一些实施例所示的示例性梁结构的示意图；
图3是根据本说明书一些实施例所示的梁结构上不同位置点的频响曲线图；
图4是根据本说明书一些实施例所示的示例性梁结构的结构示意图；
图5是根据本说明书一些实施例所示的空载及负载状态下的梁结构长度方向上不同位置点的频响曲线图；
图6是根据本说明书一些实施例所示的第二质量元件与梁结构的质量比值与第一位置到固定端的距离与梁结构的长度比值之间的关系图；
图7是根据本说明书一些实施例所示的示例性梁结构的结构示意图；
图8是根据本说明书一些实施例所示的铰支端的结构示意图；
图9是根据本说明书一些实施例所示的示例性梁结构的结构示意图；
图10是根据本说明书一些实施例所示的示例性梁结构的结构示意图；
图11A是根据本说明书一些实施例所示的示例性梁结构的结构示意图；
图11B是图11A所示的梁结构的振动模态示意图；
图12是根据本说明书一些实施例所示的梁结构长度方向上不同位置点的频响曲线图；
图13是根据本说明书一些实施例所示的梁结构宽度方向上不同位置点的频响曲线图；
图14A是根据本说明书一些实施例所示的梁结构的结构示意图；
图14B是图14A所示的梁结构的振动模态示意图；
图15是根据本说明书一些实施例所示的梁结构上不同位置点的频响曲线图；
图16A是根据本说明书一些实施例所示的梁结构的结构示意图；
图16B是图16A所示的梁结构振动模态示意图；
图17是根据本说明书一些实施例所示的梁结构上不同位置点的频响曲线图；
图18是根据本说明书一些实施例所示的声学输出装置的局部示意图；
图19是根据本说明书一些实施例所示的声学输出装置的示意图。
具体实施方式
为了更清楚地说明本申请实施例的技术方案，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申请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申请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。
应当理解，本文使用的“系统”、“装置”、“单元”和/或“模块”是用于区分不同级别的不同组件、元件、部件、部分或装配的一种方法。然而，如果其他词语可实现相同的目的，则可通过其他表达来替换词语。
如本申请和权利要求书中所示，除非上下文明确提示例外情形，“一”、“一个”、“一种”和/或“该”等词并非特指单数，也可包括复数。一般说来，术语“包括”与“包含”仅提示包括已明确标识的步骤和元素，而这些步骤和元素不构成一个排它性的罗列，方法或者设备也可能包含其它的步骤或元素。
本说明书实施例描述了一种声学输出装置，所述声学输出装置可以包括振动元件，振动元件包括沿着长度方向延伸的梁结构。在一些实施例中，梁结构可以包括压电层，由于其逆压电效应，压电层可以响应电信号而发生形变，所述形变带动振动元件振动。在一些实施例中，声学输出装置还可以包括质量元件，质量元件连接于梁结构的第一位置，振动元件的振动可以带动质量元件在垂直于梁结构长度方向的方向上振动，从而产生声音。在一些实施例中，由于质量元件连接在梁结构沿其长度方向上的位置不同，经由质量元件输出的振动模态不同，相应地，声学输出装置的频响曲线不同，故可以在梁结构上确定合适的连接质量元件的第一位置，以使声学输出装置的频响曲线较为平滑。本说明书实施例可以通过设置第一位置(例如，调整第一位置到梁结构一端的距离与梁结构的长度之间的比值)，使得声学输出装置的频响曲线在目标频率范围(例如，50Hz-10000Hz)内没有或具有较少的谐振谷，或者减少谐振峰与谐振谷之间的幅值差，从而得到较为平滑的频响曲线，保证声学输出装置能够具有较好的音质。
图1是根据本说明书一些实施例所示的一种声学输出装置的框图。如图1所示，声学输出装置100可以包括振动元件110和质量元件120。
声学输出装置100可以用于将音频信号(例如，含有声音信息的电信号)转换为声音信号。在一些实施例中，声学输出装置100可以为骨传导声学输出装置、气导声学输出装置或骨气导结合的声学输出装置。在一些实施例中，声学输出装置100可以应用于眼镜、智能手环、耳机、助听器、智能头盔、智能手表、智能服装、智能背包、智能配件等，或其任意组合。例如，声学输出装置100可以应用于功能型的近视眼镜、老花镜、骑行眼镜或太阳镜等，也可以是智能化的眼镜，例如具有耳机功能的音频眼镜。在一些实施例中，声学输出装置100还可以应用于头盔、增强现实(Augmented Reality,AR)设备或虚拟现实(Virtual Reality,VR)设备等头戴式设备。在一些实施例中，增强现实设备或虚拟现实设备可以包括虚拟现实头盔、虚拟现实眼镜、增强现实头盔、增强现实眼镜等或其任何组合。例如，虚拟现实设备和/或增强现实设备可以包括Google Glass、Oculus Rift、Hololens、Gear VR等。
振动元件110可以用于将音频信号转换为机械振动。在一些实施例中，振动元件110可以包括沿着长度方向延伸的梁结构111。在一些实施例中，梁结构111可以为一端固定的悬臂梁(例如，参见图2)。在一些实施例中，梁结构111可以为一端固定另一端铰支的梁(例如，参见图7)。在一些实施例中，梁结构111可以为两端铰支的梁(例如，参见图10)。在一些实施例中，梁结构111可以为两端固定的梁(例如，参见图11A)。在一些实施例中，梁结构111还可以为两端弹性支撑的梁(参见图14A)。在一些实施例中，梁结构111还可以为中间弹性支撑的梁(例如，参见图16A)。在一些实施例中，振动元件110的数量可以为两个或以上(参见图19)。
在一些实施例中，振动元件110还可以为片状、杆状结构等。在一些实施例中，振动元件110的材料可以为具有传输振动能力的材料。例如，振动元件110的材料可以包括硅胶、泡棉、塑胶、橡胶、金属等，或其任意组合。在一些实施例中，振动元件110可以是具有良好弹性(即易发生弹性形变)的元器件。例如，振动元件110可以包括弹簧(例如，空气弹簧、机械弹簧、电磁弹簧等)、传振片、弹片、基板等，或其任意组合。
在一些实施例中，梁结构111可以包括压电层1112。压电层1112可以响应于电信号(例 如，含有音频信息的电信号)而发生形变，从而带动梁结构111振动。例如，由于逆压电效应，压电层1112可以响应于电信号而发生形变，所述形变可以带动梁结构111(或振动元件110)沿着压电层1112的极化方向产生振动。在一些实施例中，梁结构111的振动方向可以与梁结构111的长度方向(即梁结构111的长轴方向)垂直。在一些实施例中，压电层1112可以由具有压电效应(逆压电效应)的材料组成，示例性的压电材料可以包括压电陶瓷、压电晶体、压电聚合物(例如，偏聚氟乙烯)等或其任意组合。在一些实施例中，压电层1112可以为任意形状，例如膜状、片状、块状、柱状等或其任意组合。在一些实施例中，压电层1112可以为与梁结构111形状相适应的薄片形状。在一些实施例中，压电层1112可以直接通过胶接或沉积等的方式贴附于梁结构111上。在一些实施例中，压电层1112可以通过卡接、扣接等方式连接于梁结构111。在一些实施例中，压电层1112可以通过物理沉积或化学沉积的方式附着于梁结构111。关于振动元件的更多说明可以参见本说明书的其它部分，例如图2、图5、图7等及其相关描述。
质量元件120可以为具有质量的部件。在一些实施例中，质量元件120可以包括振动板、振膜等，以使声学输出装置100能够通过质量元件120输出振动。在一些实施例中，质量元件120可以为任意形状，例如圆柱体、长方体、圆锥、圆台、球体等规则结构或不规则结构体。在一些实施例中，质量元件120的材质可以包括但不限于塑胶、木质、金属等具有一定刚性的材质。在一些实施例中，质量元件120的材质还可以包括有利于拓展声学输出装置100的音频频宽的负刚度材料、立方刚度材料等各种超材料。在一些实施例中，质量元件120可以连接于梁结构111的第一位置。梁结构111上第一位置的振动带动质量元件120产生与振动元件110同方向(即垂直于梁结构111长度方向的方向)的振动。质量元件120可以直接连接在梁结构111的第一位置，也可以通过连接杆连接到梁结构111的第一位置(例如，质量元件120为振膜时，振膜中心可以通过连接杆连接于梁结构111的第一位置)。为方便描述，上述连接杆也可以看作质量元件120的一部分。
在一些实施例中，可以通过调整质量元件120连接于梁结构111上的第一位置，在不改变或基本不改变谐振峰位置的情况下，调整输出装置100的频响曲线的谐振谷的位置，使得声学输出装置100的频响曲线上谐振峰对应的频率位置与谐振谷对应的频率位置接近或相同，从而可以减小谐振峰和谐振谷导致的频响曲线上不平坦的范围或在谐振峰和谐振谷的频率位置相同时实现峰、谷相消，得到较宽频带的平滑曲线，从而提升声学输出装置的音质。这里的谐振峰可以指梁结构111(或第一位置)对应的频响曲线上表现具有较高幅值的峰，所述谐振峰可以是梁结构在其谐振频率附近发生谐振而产生的。在一些实施例中，梁结构111可以具有多个谐振频率，相应地，频响曲线上可以具有多阶谐振峰。谐振谷可以指梁结构111(或第一位置)对应的频响曲线上表现具有较低幅值的谷，所述谐振谷形成的原因可以包括但不限于梁结构111的压电层产生分割振动，使梁结构111的辐射声压在第一位置反相相消，难以输出振动。在一些实施例中，压电层可以在多个频率附近产生分割振动，相应地，频响曲线上可以具有多阶谐振谷。通过调整质量元件120连接于梁结构111上的第一位置，可以使得声学输出装置100的频响曲线实现谐振峰和谐振谷相消，得到较宽频带的平滑曲线，从而提升声学输出装置的音质。在一些实施例中，第一位置到梁结构111一端的距离与梁结构111的长度之间的比值可以在0.1～0.99范围内。在一些实施例中，第一位置到梁结构111一端的距离与梁结构111的长度之间的比值可以在0.2～0.95范围内。在一些实施例中，第一位置到梁结构111一端的距离与梁结构111的长度之间的比值可以在0.3～0.95范围内。例如，可以确定使得一阶谐振谷与二阶谐振峰相消的第一位置，使声学输出装置100的频响曲线具有第一谐振峰和第二谐振峰，第一谐振峰和第二谐振峰之间的频率范围之比大于17，并且第一谐振峰和第二谐振峰之间的频响最低点与第一谐振峰或第二谐振峰之间的幅值差小于40dB，使得声学输出装置100的频响曲线在较低的频率上得到较宽频带的平滑曲线。再例如，可以确定使得一阶谐振谷与三阶谐振峰相消的第一位置，使声学输出装置100的频响曲线具有第一谐振峰、第二谐振峰以及第三谐振峰，其中，第一谐振峰和第二谐振峰之间平滑过渡，第二谐振峰和第三谐振峰之间平滑过渡，且第二谐振峰与第三谐振峰的频率范围之比大于4，使得声学输出装置100的频响曲线在较高的频率上得到较宽频带的平滑曲线。更多关于确定第一位置的描述可以参见图3、图7、图10-图16B等及其相关描述，在此不再赘述。需要知道的是，仅仅为了描述方便，本说明书将谐振峰和谐振谷的频率位置接近或相同时实现的提升幅值的效果均称为峰、谷相消。或者，本说明书所述的峰、谷相消可以包括谐振峰和谐振谷的频率位置相同时谐振峰与谐振谷相消，也可以包括谐振峰和谐振谷的频率位置接近时使得由谐振峰和谐振谷导致的频响曲线上不平坦的范围被缩小，或者谐振峰附近的幅值降低和/或谐振谷附近的幅值提升。
在一些实施例中，声学输出装置100还可以包括第二振动元件，第二振动元件包括第二梁 结构，第二梁结构可以与梁结构111连接。在一些实施例中，第二梁结构的长度方向与梁结构111的长度方向沿着振动元件110振动方向的投影垂直。更多关于声学输出装置100还可以包括第二振动元件的描述可以参见图18和/或图19及其相关描述，在此不再赘述。
在一些实施例中，声学输出装置100还可以包括第三振动元件，第三振动元件可以包括第三梁结构，在与梁结构111振动方向垂直的平面内，第三梁结构与梁结构111柔性连接。在一些实施例中，第三梁结构沿梁结构111长度方向延伸，梁结构111和第三梁结构的一端为固定端，梁结构111和第三梁结构的另一端通过弹性连接件连接。更多关于第三振动元件的描述可以参见图19及其相关描述，在此不再赘述。
需要说明的是，以上关于图1的描述仅仅是出于说明的目的而提供的，并不旨在限制本申请的范围。对于本领域的普通技术人员来说，根据本申请的指导可以做出多种变化和修改。例如，在一些实施例中，声学输出装置100还可以包括一个或多个部件(例如，信号收发器、交互模块、电池等)。在一些实施例中，声学输出装置100中的一个或多个部件可以被其他能实现类似功能的元件替代。这些变化和修改不会背离本说明书的范围。
图2是根据本说明书一些实施例所示的示例性梁结构的示意图。如图2所示，梁结构211可以为悬臂梁，梁结构211的一端为固定端2111，在长度方向(图2所示的x方向)上背离固定端2111的另一端为自由端2112。
固定端2111是指工作状态的梁结构211上振动加速度或加速度级小于振动加速度阈值或加速度级阈值且其横截面的转角小于转角阈值的位置。仅作为示例，固定端2111的振动加速度级可以小于5dB、3dB、1dB、0.8dB、0.6dB、0.4dB、0.2dB、或者0.05dB等，且横截面的转角可以小于3°、2°、1°、0.5°、0.2°或0.05°等。在一些实施例中，固定端2111与声学输出装置的固定位置或结构(例如壳体)连接。这里的固定位置或结构可以是指声学输出装置上振动加速度或加速度级小于振动加速度阈值或加速度级阈值的位置或结构。在一些实施例中，固定端2111可以固定在固定支座212上，固定支座212与声学输出装置的固定位置或结构连接。例如，声学输出装置可以包括壳体(图2中未示出)，梁结构211可以设置于壳体内，固定支座212固定在壳体上，梁结构211的固定端2111可以与壳体上的固定支座212固定连接。自由端2112是指梁结构211上自由振动的一端。在一些实施例中，自由端2112可以处于悬空或无约束状态。
在一些实施例中，梁结构211可以包括压电层2113和基底层2114。在一些实施例中，压电层2113及基底层2114沿梁结构211的长度方向延伸。振动元件受到沿其厚度方向(图2所示z方向)的电场作用时，压电层2113发生沿长度方向的形变，所述形变带动基底层2114(或振动元件)产生沿着垂直于梁结构211长度方向的方向上振动。在一些实施例中，压电层2113可以由压电材料制成。在一些实施例中，基底层2114的材料包括不限于：金属及合金、玻璃纤维、碳纤维等或其任意组合。在一些实施例中，压电层2113和基底层2114可以在梁结构211的厚度方向上重叠设置。在一些实施例中，梁结构211可以包括多层压电层2113和基底层2114，多层压电层2113和基底层2114在厚度方向上交叠设置。
质量元件可以连接于梁结构211的第一位置。在一些实施例中，梁结构211的第一位置可以是梁结构211上沿长度方向上的不同位置，例如，图2示出的a点、b点、点、c点、d点、e点、f点、g点等。在一些实施例中，梁结构211上的不同第一位置的振动模态不同，向连接于第一位置的质量元件输出的振动模态也相应不同，继而使声学输出装置的频响曲线不同，具体参见图3及其相关描述。
图3是根据本说明书一些实施例所示的梁结构上不同位置点的频响曲线图。如图3所示，曲线31、曲线32、曲线33、曲线34、曲线35、曲线36及曲线37分别为图2所示的梁结构211(即悬臂梁)发生振动时其上的a点、b点、c点、d点、e点、f点及g点的频响曲线。在一些实施例中，质量元件对梁结构211的振动影响较小或为0，所述曲线31-37也可以分别用于表征质量元件连接于上述7个第一位置时声学输出装置(例如，声学输出装置100)的频响曲线。
从图3可以看出，在50Hz-10000Hz范围内，梁结构211上不同第一位置的振动均产生多个谐振峰(例如，一阶谐振峰A、二阶谐振峰B、三阶谐振峰C等)，不同第一位置处产生的谐振峰位置大致相同，并且随着第一位置逐渐靠近梁结构211的固定端2111，对应频响曲线的谐振谷逐渐向高频移动。仅作为示例，对比曲线34、曲线35以及曲线36可知，随着第一位置从f点到d点逐渐向固定端2111移动，f点对应的一阶谐振谷361、e点对应的一阶谐振谷351以及d点对应的一阶谐振谷341逐渐向高频移动。进一步结合a点-c点对应的曲线31-33可知，随着第一位置逐渐靠近梁结构211的固定端2111，声学输出装置的频响曲线在一阶谐振峰A与二阶谐振峰B之间和/ 或在二阶谐振峰B与三阶谐振峰C之间较为平滑，具体表现为一阶谐振峰A与二阶谐振峰B之间和/或在二阶谐振峰B与三阶谐振峰C之间平滑过渡，没有出现较低的谐振谷，两个谐振峰之间的曲线呈现为“U”形。例如，d点对应的曲线34在一阶谐振峰A和二阶谐振峰B之间的曲线平滑过渡；再例如c点对应的曲线33在一阶谐振峰A和二阶谐振峰B之间的曲线平滑过渡，并且在二阶谐振峰B和三阶谐振峰C之间的曲线平滑过渡。另外，结合曲线31-36，随着第一位置逐渐靠近梁结构211的固定端2111，声学输出装置在中低频(例如，图3中的50Hz-500Hz)的振幅逐渐降低，从而会降低声学输出装置在中低频的灵敏度。由此，可以选择合适的第一位置，使得声学输出装置在人耳可听域(例如，50Hz-10000Hz)内的谐振峰之间的频响曲线平滑过渡，并且不会过分降低声学输出装置在中低频的灵敏度。在一些实施例中，可以将c点附近范围内的位置作为第一位置，从而在提升声学输出装置音质的同时，保证声学输出装置在中低频仍具有较高的灵敏度。在一些实施例中，位于c点附近到固定端2111的距离与梁结构211的长度之间的比值可以在0.45-0.55范围内。
进一步地，结合g点对应的曲线37，曲线37在500Hz-10000Hz范围内平滑过渡，具体表现为一阶谐振峰A与三阶谐振峰C之间具有较小或没有谐振峰和/或谐振谷，且一阶谐振峰A与三阶谐振峰C之间的频响最低点(例如，图3所示的P点)与第一谐振峰或第二谐振峰之间的幅值差小于40dB。这是由于曲线37对应的一阶谐振谷与二阶谐振峰相消，从而使曲线37在二阶谐振峰B对应的频率附近没有谐振峰和/或谐振谷。由此，可以选择合适的第一位置(例如，g点)，使得声学输出装置的一阶谐振谷与二阶谐振峰相消，从而在人耳部分可听域(例如，50Hz-10000Hz)内具有第一谐振峰(即一阶谐振峰A)和第二谐振峰(即三阶谐振峰C)，所述第二谐振峰和第一谐振峰的频率之比大于17，增大了曲线37上平滑曲线对应的频率范围，从而进一步提升声学输出装置的音质。在一些实施例中，g点到固定端2111的距离与梁结构211的长度之间的比值在0.75-0.95范围内。在一些实施例中，g点到固定端2111的距离与梁结构211的长度之间的比值在0.78-0.85范围内。在一些实施例中，g点到固定端2111的距离与梁结构211的长度之间的比值可以为0.81。
结合图3及其描述，可以选择合适的第一位置，使得声学输出装置的频响曲线在特定频率范围内(例如500Hz-10000Hz)发生峰、谷相消，从而消除特定频率范围频响较差的谐振谷，并增大了声学输出装置频响曲线上的平滑曲线对应的频率范围，以提升声学输出装置的音质。在一些实施例中，可以通过计算确定第一位置(或第一位置与梁结构的长度之间的比值)，以使得声学输出装置在该第一位置处的频响曲线实现峰、谷相消。在一些实施例中，梁结构上各位置点的位移可以表示为：
u(x,t)＝Y(x)*φ(t)，         (1)
其中，Y(x)为振型函数，φ(t)为关于时间的谐函数，x表示梁结构上的位置点到梁结构一端(例如，梁结构211的固定端2111)的距离，u(x,t)满足运动微分方程：
Figure PCTCN2022108205-appb-000001
其中，E为梁结构的弹性模量，I为梁结构横截面的惯性矩，ρ为梁结构的材料密度，A为梁结构的横截面积，F为梁结构所受的外力。令外力F＝0，并分离变量可以求得梁结构的固有振型函数Y(x)：
Figure PCTCN2022108205-appb-000002
其中，C 1-C 6为常数，
Figure PCTCN2022108205-appb-000003
其中，w为圆频率。
基于上述公式(3)，可以代入不同梁结构的不同边界条件。从而确定不同梁结构对应的固有振型函数。例如，如图2所示的梁结构211，其固定端部位移为零、转角(正比于位移一阶导数)为零，同时自由端弯矩和剪力(分别正比于位移二阶、三阶导数)为零，其边界条件可以为：Y(0)＝Y′(0)＝Y″(l)＝Y″′(l)＝0，将所述边界条件代入公式(3)可得梁结构211(即悬臂梁)的固有振型函数为：
Figure PCTCN2022108205-appb-000004
其中，i为固有振型对应的阶数，β i满足ch(β il)·cos(β il)+1＝0，解得β 1l＝1.875，β 2l＝4.694，β 3l＝7.855……。
结合图3及其描述，选择不同的第一位置时，声学输出装置的谐振峰位置相对固定，并且随着第一位置逐渐靠近梁结构的固定端，谐振谷逐渐向高频移动，并可以在移动至与谐振峰相同或相近的频率位置时与该谐振峰相消。由此，梁结构的固有振型函数在该谐振峰处的振动节点即为能够使梁结构的频响曲线实现峰、谷相消的第一位置。对于梁结构211，令公式(4)中Y i(x)＝0，其解 即为在第i(i＝1、2、3……)阶谐振峰处发生峰、谷相消的第一位置。
仅作为示例，结合公式(4)，令Y 2(x)＝0所求得的解x即为梁结构211的一阶谐振谷与二阶谐振峰相消的第一位置到梁结构211的固定端2111的距离，该第一位置到梁结构211的固定端2111的距离与梁结构211的长度之间的比值约为0.774。同理，可以求得梁结构211的一阶谐振谷与三阶谐振峰相消时，第一位置到梁结构211的固定端2111的距离与梁结构211的长度之间的比值约为0.501；梁结构211的二阶谐振谷与三阶谐振峰相消时，第一位置到梁结构211的固定端2111的距离与梁结构211的长度之间的比值约为0.868。
在一些实施例中，可以选择能够使一阶谐振谷与二阶谐振峰相消的第一位置作为声学输出装置的振动输出位置，从而使声学输出装置在特定频率范围内(例如，500Hz-10000Hz)实现峰、谷相消。相应地，声学输出装置在人耳部分可听域(例如，50Hz-10000Hz)具有第一谐振峰(例如，一阶谐振峰A)和第二谐振峰(例如，三阶谐振峰C)，所述第一谐振峰与第二谐振峰之间具有较为平滑的曲线，从而提升声学输出装置在该特定频率范围的音质。基于上述理论解，同时考虑到实际应用的误差，在一些实施例中，为了使梁结构211的一阶谐振谷与二阶谐振峰相消，使声学输出装置的第一谐振峰与第二谐振峰之间具有较宽频段的平滑曲线，第一位置到固定端2111的距离与梁结构211的长度之间的比值可以在0.75-0.95范围内。在一些实施例中，第一位置到固定端2111的距离与梁结构211的长度之间的比值可以在0.75-0.9范围内。在一些实施例中，第一位置到固定端2111的距离与梁结构211的长度之间的比值可以在0.75-0.86范围内。在一些实施例中，第一位置到固定端2111的距离与梁结构211的长度之间的比值可以在0.77-0.84范围内。
在一些实施例中，还可以选择能够使一阶谐振谷与三阶谐振峰相消的第一位置作为声学输出装置的振动输出位置，从而使声学输出装置在特定频率范围内(例如，2000Hz-20000Hz)实现峰、谷相消。相应地，声学输出装置在人耳部分可听域(例如，50Hz-15000Hz)具有第一谐振峰(例如，一阶谐振峰A)、第二谐振峰(例如，二阶谐振峰B)和第三谐振峰(例如，四阶谐振峰D)。其中，第二谐振峰和第三谐振峰之间的频响最低点与第二谐振峰或第三谐振峰之间的幅值差小于30dB，并且第三谐振峰和第二谐振峰的频率之间的比值大于4，第二谐振峰和第三谐振峰之间具有较宽频段的平滑曲线，从而提升声学输出装置在特定频率范围内(例如，2000Hz-15000Hz)的音质。另外，由于一阶谐振谷向高频移动，第一谐振峰与第二谐振峰之间平滑过渡，可以进一步提升声学输出装置在较低频率范围内(例如，500Hz-2000Hz)的音质。在一些实施例中，为使梁结构211的一阶谐振谷与三阶谐振峰相消，从而提升声学输出装置的音质，第一位置到固定端2111的距离与梁结构211的长度之间的比值可以在0.45-0.6范围内。在一些实施例中，第一位置到固定端2111的距离与梁结构211的长度之间的比值可以在0.47-0.55范围内。在一些实施例中，第一位置到固定端2111的距离与梁结构211的长度之间的比值可以在0.49-0.51范围内。
需要知道的是，上述实施例所述的第一位置及其范围仅用来示例性说明，并无意于限制本说明书的保护范围。在一些实施例中，还可以选择不同的第一位置，使得不同阶数的谐振峰与谐振谷相消(例如，一阶谐振谷与三阶谐振峰相消、二阶谐振谷与三阶谐振峰相消等)，从而使得声学输出装置在不同的频率上具有较宽频段的平滑曲线，以适应不同场景的需求。
图4是根据本说明书一些实施例所示的示例性梁结构的结构示意图。图4所示的梁结构411与图2所示的梁结构211的大致相同，其主要区别之处在于图4所示的梁结构411还包括第二质量元件430。如图4所示，梁结构411包括固定端4111和自由端4112，第二质量元件430与自由端4112连接。在一些实施例中，第二质量元件430可以与质量元件类似。在一些实施例中，第二质量元件430可以为梁结构411在装配等过程中引入的附加质量。在一些实施例中，为了防止第二质量元件430的质量过大影响梁结构411的振动模态，第二质量元件430的质量与梁结构的质量之间的比值可以在0-1.2范围内。
当梁结构411的上连接有第二质量元件430时，其第一位置的振动模态与梁结构211不与第二质量元件430连接时在相同第一位置的振动模态有所不同，具体参见图5。
图5是根据本说明书一些实施例所示的空载及负载状态下的梁结构长度方向上不同位置点的频响曲线图。其中，空载状态是指梁结构(或悬臂梁)上无附加质量(例如，无第二质量元件430的梁结构211)，负载状态是指梁结构411上连接有第二质量元件430，仅作为示例，图5所述的频响曲线对应的第二质量元件430为0.28g。如图5所示，曲线511、曲线512、曲线513分别为空载状态下的梁结构上距离自由端1/3处(即第一位置到自由端的距离为梁结构长度的1/3)、1/2处及2/3处的频响曲线，曲线521、曲线522、曲线523分别为负载状态下的梁结构上距离自由端1/3处、1/2处及2/3的频响曲线。空载状态下梁结构振动的曲线511、曲线512及曲线513与负载状态下梁 结构振动的曲线521、曲线522及曲线523的形状大致相同，其中，相比于空载状态，负载状态下梁结构的谐振峰向低频移动。由此，第二质量元件会影响存在峰、谷相消的第一位置到固定端的距离与梁结构长度的比值。具体参见图6。
图6是根据本说明书一些实施例所示的第二质量元件与梁结构的质量比值与第一位置到固定端的距离与梁结构(或悬臂梁)的长度比值之间的关系图。这里所说的第一位置是指存在峰、谷(例如，一阶谐振谷与二阶谐振峰)相消的第一位置。如图6所示的曲线，横坐标m/m 0表示第二质量元件的质量m与梁结构的质量m 0之间的比值，纵坐标x/l表示第一位置到固定端的距离x与梁结构的长度l之间的比值。根据图6可知，随着第二质量元件与梁结构的质量比值增大，第一位置到固定端的距离与梁结构的长度比值逐渐增大。由此，可以根据第二质量元件的质量与梁结构的质量之间的比值确定第一位置，使得声学输出装置的频响曲线在人耳可听域内实现峰、谷相消。例如，第二质量元件的质量与梁结构的质量之间的比值可以在0-1.2范围内，第一位置到固定端的距离与梁结构(或悬臂梁)的长度之间的比值可以在0.75-0.95范围内。再例如，第二质量元件的质量与梁结构的质量之间的比值可以在0-0.5范围内，第一位置到固定端的距离与梁结构(或悬臂梁)的长度之间的比值可以在0.75-0.92范围内。再例如，第二质量元件的质量与梁结构的质量之间的比值可以在0.2-1范围内，第一位置到固定端的距离与梁结构(或悬臂梁)的长度之间的比值可以在0.8-0.95范围内。
图7是根据本说明书一些实施例所示的示例性梁结构的结构示意图。图7所示的梁结构711与图2所示的梁结构211的大致相同，其主要区别之处在于图7所示的梁结构711包括铰支端7112。如图7所示，梁结构711包括固定端7111和铰支端7112，固定端7111和铰支端7112分别为梁结构711沿长度方向(例如，图7所示的x方向)上相背离的两端，其中，固定端7111与固定端2111类似。
铰支端7112为可转动的一端。在一些实施例中，铰支端7112处具有垂直于梁结构711长度方向和振动方向(例如，图7所示的z方向)的轴(例如，平行于图7所示的y方向的轴)，铰支端7112可以围绕该轴边发生转动。图8是根据本说明书一些实施例所示的铰支端的结构示意图。在一些实施例中，如图8所示，铰支端7112沿着其长度(即y方向)方向的两侧可以与铰杆713相对固定地连接，铰杆713所在的轴(图8所示的y方向)与梁结构711的长度方向(图8所示的x方向)和振动方向(图8所示的z方向)垂直。梁结构711(或声学输出装置)还可以包括铰支座714，铰支座714可以固定在声学输出装置中(例如，壳体上)，并可以包括铰孔7141。铰杆713设置在铰孔7141内并可以在铰孔7141内自转。当梁结构711沿着其振动方向振动时，铰支端7112可以沿着铰杆713所在的轴相对铰支座714转动。在一些实施例中，铰杆713可以与铰支端7112物理连接。在一些实施例中，铰杆713可以与铰支端7112为一体结构。
在一些实施例中，与本说明书所述的悬臂梁(例如，梁结构211、梁结构411等)相似地，对于如图7所示的梁结构711，可以确定其上的第一位置，使得声学输出装置的频响曲线产生峰、谷相消，以增加声学输出装置的频响曲线在人耳可听域内的平滑曲线的范围，从而提升声学输出装置的音质。在一些实施例中，包括固定端7111和铰支端7112的梁结构711的固有振型函数Y i(x)可以与梁结构211的固有振型函数(即公式(4))类似，并且对于梁结构711的固有振型函数，其中的β i满足ch(β il)*sin(β il)-cos(β il)*sh(β il)＝0，由此可解得各阶对应的β il值，将其代入公式(4)后，另令公式(4)中Y i(x)＝0的解即为在第i(i＝1、2、3……)阶谐振峰处发生峰、谷相消的第一位置到梁结构711的固定端7111的距离。
仅作为示例，结合公式(4)，令Y 2(x)＝0所求得的解x即为梁结构711的一阶谐振谷与二阶谐振峰相消的第一位置到梁结构711的固定端7111的距离，该第一位置到梁结构711的固定端7111的距离与梁结构711的长度之间的比值约为0.56。同理，可以求得梁结构711的一阶谐振谷与三阶谐振峰相消时，第一位置到梁结构711的固定端7111的距离与梁结构711的长度之间的比值约为0.39和0.69。
在一些实施例中，可以选择能够使一阶谐振谷与二阶谐振峰相消的第一位置作为梁结构711上的振动输出位置，从而使声学输出装置在人耳部分可听域(例如，50Hz-10000Hz)具有第一谐振峰(例如，如图3所示的一阶谐振峰A)和第二谐振峰(例如，如图3所示的三阶谐振峰C)，所述第一谐振峰与第二谐振峰之间具有较为平滑的曲线，从而提升声学输出装置在该特定频率范围的音质。基于上述理论解，同时考虑到实际应用的误差，在一些实施例中，为了使梁结构711的一阶谐振谷与二阶谐振峰相消，其中，第二谐振峰的频率范围与第一谐振峰的频率范围之比可以大于6，使声学输出装置的第一谐振峰与第二谐振峰之间具有平滑曲线，第一位置到固定端7111的距离 与梁结构711的长度之间的比值可以在0.5-0.6范围内。在一些实施例中，第一位置到固定端7111的距离与梁结构711的长度之间的比值可以在0.52-0.59范围内。在一些实施例中，第一位置到固定端7111的距离与梁结构711的长度之间的比值可以在0.54-0.58范围内。
在一些实施例中，还可以选择能够使一阶谐振谷与三阶谐振峰相消的第一位置作为梁结构711上的振动输出位置，从而使声学输出装置实现峰、谷相消。相应地，声学输出装置在人耳部分可听域(例如，50Hz-15000Hz)具有第一谐振峰(例如，如图3所示的一阶谐振峰A)、第二谐振峰(例如，如图3所示的二阶谐振峰B)和第三谐振峰(例如，如图3所示的四阶谐振峰D)。此时，由于一阶谐振谷向高频移动，第一谐振峰与第二谐振峰之间平滑过渡，并且第二谐振峰与第三谐振峰之间平滑过渡，且平滑曲线的频率范围更宽，从而提升声学输出装置的音质。在一些实施例中，为使梁结构711的一阶谐振谷与三阶谐振峰相消，从而提升声学输出装置的音质，第一位置到固定端7111的距离与梁结构711的长度之间的比值可以在0.35-0.45范围内；在一些实施例中，第一位置到固定端7111的距离与梁结构711的长度之间的比值可以在0.36-0.43范围内；在一些实施例中，第一位置到固定端7111的距离与梁结构711的长度之间的比值可以在0.37-0.41范围内。在一些实施例中，为使梁结构711的一阶谐振谷与三阶谐振峰相消，从而提升声学输出装置的音质，第一位置到固定端7111的距离与梁结构711的长度之间的比值还可以在0.65-0.75范围内；在一些实施例中，第一位置到固定端7111的距离与梁结构711的长度之间的比值可以在0.67-0.72范围内；在一些实施例中，第一位置到固定端7111的距离与梁结构711的长度之间的比值可以在0.68-0.7范围内。
图9是根据本说明书一些实施例所示的示例性梁结构的结构示意图。图9所示的梁结构911与图7所示的梁结构711的大致相同，其主要区别之处在于图9所示的梁结构911包括弹性端9112。如图9所示，梁结构911包括固定端9111和弹性端9112，固定端9111和弹性端9112分别为梁结构911上相背离的两端。固定端9111与固定端7111类似。弹性端9112为梁结构911上与声学输出装置上的其他组件(例如，壳体)弹性连接的一端。在一些实施例中，代入边界条件后求得梁结构911的固有振型函数可以与梁结构211的固有振型函数(即公式(4))类似，并且对于梁结构911的固有振型函数，其中的β i满足：
Figure PCTCN2022108205-appb-000005
其中，k表示弹性端9112的弹性连接对应的弹性系数。根据该满足条件可解得各阶β i的值，将其代入公式(4)，另令公式(4)中Y i(x)＝0的解即为在第i(i＝1、2、3……)阶谐振峰处发生峰、谷相消的第一位置到梁结构911的固定端9111的距离。可选地或附加地，梁结构211(即自由梁)可以等效于弹性端9112对应的弹性系数k为0时的梁结构911，梁结构711可以等效于弹性端9112对应的弹性系数k为∞时的梁结构911。
图10是根据本说明书一些实施例所示的示例性梁结构的结构示意图。图10所示的梁结构1011与图7所示的梁结构711的大致相同，其主要区别之处在于图10所示的梁结构1011分别包括两个铰支端10111和10112。如图10所示，两个铰支端10111和10112分别为梁结构1011上相背离的两端，其中，铰支端10111和10112可以与铰支端7112类似。
在一些实施例中，对于如图10所示的梁结构1011，可以确定其上的第一位置，使得声学输出装置的频响曲线产生峰、谷相消，以增加声学输出装置的频响曲线在人耳可听域内的平滑曲线的范围，从而提升声学输出装置的音质。在一些实施例中，代入边界条件后求得梁结构1011的固有振型函数可以表示为：
Y i(x)＝sin(β ix)，        (5)
其中，β i满足：sin(β il)＝0，可解得各阶β il的值，将其代入公式(5)后，令公式(5)中Y i(x)＝0，其解即为在第i(i＝1、2、3……)阶谐振峰处发生峰、谷相消的第一位置。
仅作为示例，结合公式(5)，在一些实施例中，梁结构1011可以为两端(即铰支端10111和10112)对称结构，实际受压电驱动时其偶数阶次的谐振模态消失，只剩奇数阶次谐振峰。可以求得梁结构1011的一阶谐振谷与三阶谐振峰相消时，第一位置到梁结构1011的铰支端10111的距离与梁结构1011的长度之间的比值约为0.33或0.67。
在一些实施例中，还可以选择能够使一阶谐振谷与三阶谐振峰相消的第一位置作为梁结构1011上的振动输出位置，从而使声学输出装置实现峰、谷相消。相应地，声学输出装置在人耳部分可听域(例如，50Hz-15000Hz)具有第一谐振峰、第二谐振峰和第三谐振峰。此时，由于一阶谐振谷向高频移动，第一谐振峰与第二谐振峰之间平滑过渡，并且第二谐振峰与第三谐振峰之间平滑过渡，且平滑曲线的频率范围更宽，从而提升声学输出装置的音质。仅作为示例，第二谐振峰的频率 范围与第一谐振峰的频率范围之比可以大于10。在一些实施例中，为使第一谐振峰与第二谐振峰之间为平滑曲线，平滑曲线的频率范围更宽，即梁结构1011的一阶谐振谷与三阶谐振峰相消，第一位置到两个铰支端中一个铰支端的距离与梁结构1011的长度之间的比值可以在0.3-0.4范围内。在一些实施例中，第一位置到两个铰支端中一个铰支端10111的距离与梁结构1011的长度之间的比值可以在0.3-0.37范围内。在一些实施例中，第一位置到两个铰支端中一个铰支端10111的距离与梁结构1011的长度之间的比值可以在0.31-0.35范围内。
图11A是根据本说明书一些实施例所示的示例性梁结构的结构示意图。图11A所示的梁结构1111与图2所示的梁结构211的大致相同，其主要区别之处在于图11A所示的梁结构1111包括固定端11111和固定端11112。如图11A所示，两个固定端分别为梁结构1111上沿长度方向(如图11A所示的x方向)相背离的两端，固定端可以与固定端2111类似。
在一些实施例中，对于如图11A所示的梁结构1111，可以确定其上的第一位置，使得声学输出装置的频响曲线产生峰、谷相消，以增加声学输出装置的频响曲线在人耳可听域内的平滑曲线的范围，从而提升声学输出装置的音质。在一些实施例中，代入边界条件后求得梁结构1111的固有振型函数可以表示为：
Figure PCTCN2022108205-appb-000006
其中，β i满足：cos(β il)*ch(β il)＝1，可解得各阶β il的值为β 1l＝4.73，β 2l＝7.85，β 3l＝10.99……。将其代入公式(6)，令公式(6)中Y i(x)＝0，便可得发生各阶峰谷相消的第一位置与固定端11111的距离与梁结构1111的长度之间的比值。仅作为示例，对称边界条件下实际受压电驱动时其偶数阶次的谐振模态消失，只剩奇数阶次谐振峰，结合公式(6)，可求得梁结构1111上一阶谐振谷与三阶谐振峰相消的第一位置到其中一个固定端的距离与梁结构1111的长度之间的比值约为0.36或0.64。
在一些实施例中，包括固定端11111和固定端11112的梁结构1111可以为两端对称结构，即梁结构1111沿着轴L对称，其中，L穿过中点O且与梁结构1111的宽度方向y平行。在一些实施例中，梁结构1111上压电层的电极也可以沿着轴L对称。由此，梁结构1111发生振动时，轴L两侧的梁结构1111所受到的应力对称分布，中点O的转角为0。这里所述的点的转角可以指梁结构振动(或形变)后，梁结构上该点所在横截面绕其中性轴(例如，图11A所示的x轴或z轴)所旋转的角位移。图11B是图11A所示的梁结构1111的振动模态示意图。如图11B所示，图11B中的(a)、(b)和(c)分别表示梁结构1111第1、3、5阶的振动模态曲线。所述1、3、5阶振动模态曲线分别与公式(6)所示的1、3、5阶振型函数Y 1、Y 1以及Y 5对应，其中，横轴表示梁结构1111各点，纵轴表示梁结构1111的固有振型函数Y i(x)，振动模态曲线与横轴的交点(即Y i(x)＝0)即为梁结构1111的振动节点。需要知道的是，由于中点O两侧所受到的应力对称分布，中点O的转角应为0，相应地，梁结构1111受压电驱动时其偶数阶次的谐振模态消失，只剩奇数阶次的谐振模态。因此，如图11B所示，梁结构1111的实际振动不包括偶数阶振动模态(例如，梁结构1111的频响曲线不包括二阶峰、二阶谷、四阶峰、四阶谷等)，进一步结合图11B中的(a)、(b)和(c)，振型函数Y i(x)在中点O处不与横轴相交，由此，梁结构1111的中点O无法成为梁结构1111的振动节点，也就不能成为峰谷相消点。
图12是根据本说明书一些实施例所示的梁结构长度方向上不同位置点的频响曲线图。如图12所示，曲线121、曲线122、曲线123、曲线124及曲线125分别为图11A所示的梁结构1111上到其中一个固定端的距离与梁结构1111的长度之间的比值为0.31、0.36(即发生一阶谐振谷和三阶谐振峰相消的理论第一位置)、0.41、0.45及0.5的5个位置点的频响曲线，可以分别表征质量元件连接于上述5个位置点时的声学输出装置的频响曲线。
根据图12可知，在50Hz-20000Hz范围内，上述5个位置点对应的频响曲线具有多个谐振峰(例如，谐振峰E、谐振峰F、谐振峰G等)，并且当振动输出点(第一位置)从中点向固定端移动时，频响曲线表现为各个谐振峰的频率位置基本不变，谐振谷逐渐从高频向低频移动。其中，谐振峰E对应的频率f E、谐振峰F对应的频率f F、谐振峰G对应的频率f G三者之间的比值约为：f E:f F:f G＝1:5.36:13.06。梁结构1111上各阶谐振频率可以表示为：
Figure PCTCN2022108205-appb-000007
根据公式(7)，梁结构1111的一阶谐振峰对应的频率f 1、三阶谐振峰对应的频率f 2、以及五阶谐振峰对应的频率f 5三者之间的比值可以为：f 1:f 3:f 5＝(β 1l) 2:(β 3l) 2:(β 5l) 2，进一步结合公式(6)求得 各阶β il的值可得：f 1:f 3:f 5＝1:5.40:13.35。对比f 1:f 3:f 5以及f E:f F:f G可知，谐振峰E、谐振峰F、谐振峰G可以分别为一阶谐振峰、三阶谐振峰以及五阶谐振峰，梁结构1111的振动不包括偶数阶振动模态。
进一步地，如曲线122所示，谐振谷在移动至三阶谐振峰F对应的频率附近时可以与三阶谐振峰F发生峰、谷相消，形成一阶谐振峰E至五阶谐振峰G之间(1000Hz-13000Hz范围内)的较宽频段的平滑曲线。由此，在一些实施例中，可以调整第一位置，使梁结构1111的一阶谐振谷与三阶谐振峰相消，此时，声学输出装置的频响曲线可以具有第一谐振峰(即一阶谐振峰E)和第二谐振峰(即五阶谐振峰G)，第二谐振峰与第一谐振峰的频率范围之比大于13(例如，f 1:f 5＝1:13.35)，第一谐振峰和第二谐振峰之间具有较宽频段的平滑曲线，从而提升声学输出装置的音质。结合上述公式(6)以及图12，在一些实施例中，第一位置到两个固定端中一个固定端的距离与梁结构1111的长度之间的比值可以在0.3-0.4范围内。在一些实施例中，第一位置到两个固定端中一个固定端的距离与梁结构1111的长度之间的比值可以在0.32-0.4范围内。在一些实施例中，第一位置到两个固定端中一个固定端的距离与梁结构1111的长度之间的比值可以在0.34-0.38范围内。
另外，结合曲线123、曲线124及曲线125可知，梁结构1111中点附近的振动输出点的频响曲线具有较大的谐振谷(例如，图12所示的谐振谷H)，其原因可以是梁结构1111在宽度方向(如图11A所示的y方向)产生卷曲模态，所述卷曲模态影响了频响曲线谐振谷的幅值。进一步结合曲线125所示，可以调整第一位置在梁结构1111长度方向的中点附近，此时，若不考虑卷曲模态的影响，声学输出装置的频响曲线可以具有第一谐振峰(即一阶谐振峰E)、第二谐振峰(即三阶谐振峰F)和第三谐振峰(即五阶谐振峰G)，一阶谐振峰E与三阶谐振峰F之间、以及三阶谐振峰F与五阶谐振峰G之间平滑过渡，从而提升声学输出装置的音质。仅作为示例，如图12所示，第二谐振峰和第三谐振峰之间的频响最低点与第二谐振峰或第三谐振峰之间的幅值差可以小于40dB，第三谐振峰与第二谐振峰的频率范围之比可以大于2，第二谐振峰和第三谐振峰之间平滑过渡。在一些实施例中，第一位置到两个固定端中一个固定端的距离与梁结构1111的长度之间的比值可以在0.45-0.5范围内。
图13是根据本说明书一些实施例所示的梁结构宽度方向上不同位置点的频响曲线图。如图13所示，曲线131、曲线132、曲线133、曲线134、曲线135及曲线136分别为图11A所示的梁结构1111上到侧边11113的距离与梁结构1111的宽度之间的比值为0.5、0.4、0.3、0.22、0.1及0的6个位置点的频响曲线，其中，侧边11113是指与梁结构1111宽度方向垂直的两侧边中的一侧边，且上述6个位置点均为长度方向上的中点。在上述6条曲线中，曲线134上相较其它曲线更为平滑，其中，一阶谐振峰E与三阶谐振峰F之间、以及三阶谐振峰F与五阶谐振峰G之间平滑过渡。
梁结构1111上宽度方向的卷曲模态可以近似于两端均为自由端的梁结构的一阶振型，其一阶固有振型函数可以表示为：
Figure PCTCN2022108205-appb-000008
其中，x′表示梁结构1111上的点到侧边11113的距离，L表示梁结构的宽度。令Y(x′)＝0，解得卷曲模态的振动节点位置x′/L＝0.22。结合图13可知，在该振动节点处，宽度方向上的卷曲模态可消除。
由上，为消除宽度方向上的卷曲模态，在一定程度上提升振幅较大的谐振谷，在一些实施例中，在沿着梁结构的宽度方向上，第一位置到梁结构1111的一边的距离与梁结构1111的宽度之间的比值可以在0.1-0.4范围内。在一些实施例中，在沿着梁结构的宽度方向上，第一位置到梁结构1111一边的距离与梁结构1111的宽度之间的比值可以在0.15-0.3范围内。在一些实施例中，在沿着梁结构的宽度方向上，第一位置到梁结构1111一边的距离与梁结构1111的宽度之间的比值可以在0.18-0.36范围内。
图14A是根据本说明书一些实施例所示的梁结构的结构示意图。图14A所示的梁结构1411与图11A所示的梁结构1111的大致相同，其主要区别之处在于图14A所示的梁结构1411包括弹性端14111和弹性端14112。如图14A所示，弹性端14111和弹性端14112分别为梁结构1411上相背离的两端。在一些实施例中，两个弹性端可以通过弹性件1412与声学输出装置的其他组件(例如，梁结构固定支座、壳体等)连接。
弹性件1412可以为具有弹性的部件。在一些实施例中，弹性件1412可以为弹性结构，示例性的弹性结构可以包括连续折弯结构、螺旋结构、片簧结构、机械弹簧、空气弹簧、电磁弹簧等 或其任意组合。在一些实施例中，弹性件1412可以由弹性材料制成，示例性的弹性材料可以包括泡棉、橡胶、乳胶、硅胶、海绵等或其任意组合。在一些实施例中，梁结构1411可以为两端对称结构。弹性端14111和弹性端14112对应的弹性件1412可以沿着梁结构的长度方向和/或宽度方向对称设置。
在一些实施例中，为保证结构的稳定，弹性端14111通过至少两个弹性件1412与声学输出装置的其他组件连接。在一些实施例中，至少两个弹性件1412可以沿梁结构1411对称分布。
图14B是图14A所示的梁结构1411的振动模态示意图。如图14B所示，(a)-(e)分别表示梁结构1411不同振动模态下的振动模态曲线。其中，(a)示出了梁结构1411的初始振动模态，在该初始振动模态中，开始受到压电驱动的梁结构1411首先在中部发生振动，并带动两边的弹性件1412发生振动。随着频率的增加，如(b)所示，弹性件1412与梁结构1411形成的弹性质量发生谐振，所述谐振可以产生第一谐振峰。在一些实施例中，所述第一谐振峰对应的谐振频率可以在300Hz-700Hz之间。仅作为示例，图15所示的梁结构1411的频响曲线在500Hz左右具有第一谐振峰I。进一步地，随着频率的增加，如(c)所示的振动模态曲线中部下沉，其中点与横轴产生交点。相应地，梁结构1411的中点产生振动节点，中点对应的频响曲线可以具有谐振谷(例如，如图15所示的谐振谷J)。随着频率的继续增加，梁结构1411可以在其固有谐振频率处发生谐振，所述谐振产生第二谐振峰。(d)示出了梁结构1411的谐振模态，在该谐振模态中，梁结构1411可以在谐振频率附近发生谐振。在一些实施例中，所述谐振频率可以在3300Hz-4300Hz之间。仅作为示例，图15所示的梁结构1411的频响曲线在3800Hz左右具有第二谐振峰K。在该谐振模态中，振动模态曲线的中部继续下沉，并在靠近端部的位置分别与横轴产生两个交点。相应地，梁结构1411在这两个交点处产生振动节点，对应的频响曲线可以具有谐振谷。随着频率的继续增加，梁结构1411可以在其另一固有谐振频率处发生谐振，所述谐振产生第三谐振峰。(e)示出了梁结构1411在另一固有谐振频率处的谐振模态，在该谐振模态中，梁结构1411可以在另一谐振频率附近发生谐振。在一些实施例中，所述谐振频率可以在12kHz-18kHz之间。仅作为示例，图15所示的梁结构1411的频响曲线在15000Hz左右具有第三谐振峰L。在(e)所示的谐振模态中，振动模态曲线的中部及两个端部下沉，并与横轴产生四个交点。相应地，梁结构1411在这四个交点处产生振动节点，对应的频响曲线可以具有谐振谷。根据图14B可知，在(a)-(e)所示的振动模态中，梁结构1411上靠近弹性端的位置(例如，虚线L1与L2之间的位置、虚线L3与L4之间的位置)可以始终不存在节点。相应地，在(a)-(e)所示的振动模态中，所述靠近弹性端的位置对应的频响曲线可以始终不具有谐振谷，各谐振峰之间(例如，第一谐振峰I与第二谐振峰K之间、第二谐振峰K与第三谐振峰L之间)的曲线可以平滑过渡。由此，可以选择该靠近弹性端的位置作为第一位置，从而可以使得声学输出装置的谐振峰之间的曲线平滑过渡，进而提升声学输出装置的音质。在一些实施例中，为了使声学输出装置的谐振峰之间的曲线平滑过渡，所述第一位置到其中一个弹性端的距离与梁结构1411的长度之间的比值可以在0.1-0.25范围内。在一些实施例中，所述第一位置到其中一个弹性端的距离与梁结构1411的长度之间的比值可以在0.15-0.2范围内。
图15是根据本说明书一些实施例所示的梁结构上不同位置点的频响曲线图。如图15所示，曲线151为梁结构1411上弹性端(例如，弹性端14111或14112)处的频响曲线，曲线152为梁结构1411上中点处的频响曲线，曲线153为梁结构1411上第一位置处的频响曲线，其中，所述第一位置到其中一个弹性端(例如，弹性端14111)的距离与梁结构1411的长度之间的比值为0.2。根据曲线151-153可知，当输出位置为弹性端或第一位置时，声学输出装置的频响曲线在500Hz-15000Hz频率范围内没有或具有较小的谐振谷，且各个谐振峰之间(例如，第一谐振峰I于第二谐振峰K之间、第二谐振峰K与第三谐振峰L之间)平滑过渡，频率响应更好。另外，结合曲线151和曲线153可知，在较低频率(例如，小于500Hz)范围内，与弹性端相比，第一位置的振动可以具有较高的幅值。因此，第一位置处的低频灵敏度高于弹性端处的低频灵敏度。由此，梁结构1411上连接质量元件的第一位置可以靠近弹性端，其中，所述第一位置到其中一个弹性端的距离与梁结构1411的长度之间的比值可以在0.15-0.2范围内，以获得为平滑的频响曲线，同时保证声学输出装置的低频灵敏度。
在一些实施例中，弹性件1412与梁结构1411的组成的弹性质量的振动可以在较低的频率范围内产生谐振峰，从而提高声学输出装置在低频范围内的灵敏度。例如，如图15所示，曲线151和曲线152在较低的频率范围内(例如，300Hz-700Hz)具有第一谐振峰I。为了使弹性件1412与梁结构1411的振动可以在较低的频率范围内产生谐振峰，从而提高声学输出装置在低频范围内的灵敏度，在一些实施例中，弹性端(例如，弹性端14111和弹性端14112)对应的弹性件1412的整 体等效弹性系数可以在3500-4000N/m范围内。在一些实施例中，弹性端对应的弹性件1412的整体等效弹性系数可以在3700-3900N/m范围内。
图16A是根据本说明书一些实施例所示的梁结构的结构示意图。图16A所示的梁结构1611与图14A所示的梁结构1411的大致相同，其主要区别之处在于图16A所示的梁结构1611的两端为自由端(例如，自由端16111和自由端16112)，并通过其中部设置的弹性件1612与声学输出装置的固定位置或结构(例如，固定支座)连接。关于弹性件1612的具体说明可以参考图14A中关于弹性件1412的描述。如图16A所示，弹性件1612的一端与梁结构的中部连接，其另一端与声学输出装置的固定位置或结构连接。需要知道的是，梁结构1611的中部可以是指靠近其轴线中点的一定区域范围。
在一些实施例中，为维持梁结构1611的结构稳定，梁结构1611上垂直于其轴线的两侧均设置有弹性件1612。在一些实施例中，梁结构1611两侧的弹性件1612的连线可以垂直于梁结构1611的轴线。在一些实施例中，梁结构1611两侧的弹性件1612也可以沿着垂直于梁结构1611轴线的中线(例如，如图16A所示的中线M)对称设置。在一些实施例中，梁结构1611两侧的弹性件1612也可以与垂直于梁结构1611轴线的中线(例如，如图16A所示的中线M)间隔相同距离。
图16B是图16A所示的梁结构1611的振动模态示意图。如图16B所示，(a)-(e)分别表示梁结构1611不同振动模态下的振动模态曲线。其中，(a)示出了梁结构1611的初始振动模态，在该初始振动模态中，开始受到压电驱动的梁结构1611首先在两端发生振动，振动模态曲线两端下沉。随着频率的增加，如(b)所示，弹性件1612与梁结构1611形成的弹性质量发生谐振，所述谐振可以产生第一谐振峰。在一些实施例中，所述第一谐振峰对应的谐振频率可以在400Hz-1000Hz之间。仅作为示例，图17所示的梁结构1611的频响曲线在600Hz左右具有第一谐振峰N。进一步地，随着频率的增加，如(c)所示的振动模态曲线两端向上抬起，其自由端与横轴产生交点。相应地，梁结构1611的自由端产生振动节点，自由端对应的频响曲线可以具有谐振谷(例如，如图17所示的谐振谷Q)。随着频率的继续增加，梁结构1611可以在其固有谐振频率处发生谐振，所述谐振产生第二谐振峰。(d)示出了梁结构1611的谐振模态，在该谐振模态中，梁结构1611可以在谐振频率附近发生谐振。在一些实施例中，所述谐振频率可以在3300Hz-4300Hz之间。仅作为示例，图17所示的梁结构1611的频响曲线在3650Hz左右具有第二谐振峰R。在该谐振模态中，振动模态曲线的两端继续向上抬起，并在靠近自由端的位置分别与横轴产生两个交点。相应地，梁结构1611在这两个交点处产生振动节点，对应的频响曲线可以具有谐振谷。随着频率的继续增加，梁结构1611可以在其另一固有谐振频率处发生谐振，所述谐振产生第三谐振峰。(e)示出了梁结构1611另一固有谐振频率处的谐振模态，在该谐振模态中，梁结构1611可以在另一谐振频率附近发生谐振。在一些实施例中，所述谐振频率可以在12kHz-18kHz之间。仅作为示例，图17所示的梁结构1611的频响曲线15000Hz左右具有第三谐振峰S。在(e)所示的谐振模态中，振动模态曲线的中部及两个自由端下沉，并与横轴产生四个交点。相应地，梁结构1611在这四个交点处产生振动节点，对应的频响曲线可以具有谐振谷。根据图16B可知，在(a)-(e)所示的振动模态中，梁结构1611上靠近中点的位置(例如，虚线L5与L6之间的位置)可以始终不存在节点。相应地，在(a)-(e)所示的振动模态中，所述靠近弹性端的位置对应的频响曲线可以始终不具有谐振谷，各谐振峰之间(例如，第一谐振峰N与第二谐振峰R之间、第二谐振峰R与第三谐振峰S之间)的曲线可以平滑过渡。由此，可以选择该靠近中点的位置作为第一位置，从而可以使得声学输出装置的谐振峰之间的曲线平滑过渡，进而提升声学输出装置的音质。在一些实施例中，为了使声学输出装置的谐振峰之间的曲线平滑过渡，所述第一位置到其中一个弹性端的距离与梁结构1611的长度之间的比值可以在0.3-0.7范围内。在一些实施例中，所述第一位置到其中一个弹性端的距离与梁结构1611的长度之间的比值可以在0.4-0.6范围内。
图17是根据本说明书一些实施例所示的梁结构上不同位置点的频响曲线图。如图17所示，曲线171为梁结构1611上自由端(例如，自由端16111或16112)处的频响曲线，曲线172为梁结构1611上第一位置处的频响曲线，其中，所述第一位置到其中一个自由端(例如，自由端16111)的距离与梁结构1611的长度之间的比值为0.45。根据曲线171和172可知，当输出位置为第一位置时，声学输出装置的频响曲线在500Hz-15000Hz频率范围内没有或具有较小的谐振谷，且各个谐振峰之间(例如，第一谐振峰N于第二谐振峰R之间、第二谐振峰R与第三谐振峰S之间)平滑过渡，频率响应更好。由此，梁结构1611上连接质量元件的第一位置可以靠近梁结构1611的中点，其中，所述第一位置到其中一个弹性端的距离与梁结构1611的长度之间的比值可以在0.4-0.6范围内，以获得为平滑的频响曲线，提升声学输出装置的音质。
图18是根据本说明书一些实施例所示的声学输出装置的局部示意图。如图18所示，声学输出装置包括梁结构1811和第二梁结构1821。在一些实施例中，梁结构1811可以与第二梁结构1821相同或相似。梁结构1811和第二梁结构1821可以与图2所示的梁结构211类似，关于梁结构1811和第二梁结构1821的更多说明可以参见图2。
如图18所示，梁结构1811和第二梁结构1821的一端为固定端，另一端通过连接件1830相互连接。在一些实施例中，连接件1830可以为弹性连接件。在一些实施例中，弹性连接件可以为弹性结构。
图19是根据本说明书一些实施例所示的声学输出装置的示意图。如图19所示，声学输出装置可以包括两个或以上的振动元件，每个振动元件均包括梁结构1911，梁结构1911包括固定端19111和自由端19112。多个梁结构1911可以间隔分布于质量元件1920的周侧，质量元件1920分别与多个梁结构1911的第一位置19113连接。在一些实施例中，质量元件1920可以包括振动板、振膜等，以使声学输出装置能够通过质量元件1920输出振动。梁结构1911与图2所示的梁结构211类似，关于梁结构1911的更多说明可以参见图2。
在一些实施例中，多个梁结构1911可以沿质量元件1920的中点对称分布于质量元件1920的周侧。在一些实施例中，多个梁结构1911可以均匀间隔分布于质量元件1920的周侧。在一些实施例中，质量元件1920连接的多个梁结构1911上的第一位置与梁结构1911的固定端19111之间的距离与梁结构的长度之间的比值可以相等。在一些实施例中，可以基于本说明书其他实施例(例如，图3等)的描述确定第一位置19113，使质量元件1920(或声学输出装置)的频响曲线可以实现峰、谷相消，得到较宽频段的平滑曲线，进而提升声学输出装置的音质。在一些实施例中，为了使得质量元件1920的频响曲线上实现一阶谐振谷与二阶谐振峰相消，使声学输出装置的第一谐振峰与第二谐振峰之间具有较宽频段的平滑曲线，进而提升声学输出装置的音质，质量元件1920连接的每个梁结构1911上的第一位置与梁结构1911的固定端19111之间的距离与梁结构的长度之间的比值可以在0.75-0.95范围内。在一些实施例中，质量元件1920连接的每个梁结构1911上的第一位置与梁结构1911的固定端19111之间的距离与梁结构的长度之间的比值可以在0.8-0.85范围内。在一些实施例中，为了使得质量元件1920的频响曲线上实现一阶谐振谷与三阶谐振峰相消，使声学输出装置的第二谐振峰与第三谐振峰之间具有较宽频段的平滑曲线，进而提升声学输出装置的音质，质量元件1920连接的每个梁结构1911上的第一位置与梁结构1911的固定端19111之间的距离与梁结构的长度之间的比值可以在0.45-0.6范围内。在一些实施例中，质量元件1920连接的每个梁结构1911上的第一位置与梁结构1911的固定端19111之间的距离与梁结构的长度之间的比值可以在0.5-0.55范围内。
需要知道的是，图2-图19中所示的振动元件或梁结构仅用于示例性描述，并不对其构成限制。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，而并不构成对本申请的限定。虽然此处并没有明确说明，本领域技术人员可能会对本申请进行各种修改、改进和修正。该类修改、改进和修正在本申请中被建议，所以该类修改、改进、修正仍属于本申请示范实施例的精神和范围。
同时，本申请使用了特定词语来描述本申请的实施例。如“一个实施例”、“一实施例”、和/或“一些实施例”意指与本申请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，本申请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。
此外，除非权利要求中明确说明，本申请处理元素和序列的顺序、数字字母的使用、或其他名称的使用，并非用于限定本申请流程和方法的顺序。尽管上述披露中通过各种示例讨论了一些目前认为有用的发明实施例，但应当理解的是，该类细节仅起到说明的目的，附加的权利要求并不仅限于披露的实施例，相反，权利要求旨在覆盖所有符合本申请实施例实质和范围的修正和等价组合。例如，虽然以上所描述的系统组件可以通过硬件设备实现，但是也可以只通过软件的解决方案得以实现，如在现有的服务器或移动设备上安装所描述的系统。
同理，应当注意的是，为了简化本申请披露的表述，从而帮助对一个或多个发明实施例的理解，前文对本申请实施例的描述中，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申请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。尽管本申请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。
针对本申请引用的每个专利、专利申请、专利申请公开物和其他材料，如文章、书籍、说明书、出版物、文档等，特此将其全部内容并入本申请作为参考。与本申请内容不一致或产生冲突的申请历史文件除外，对本申请权利要求最广范围有限制的文件(当前或之后附加于本申请中的)也除外。需要说明的是，如果本申请附属材料中的描述、定义、和/或术语的使用与本申请内容有不一致或冲突的地方，以本申请的描述、定义和/或术语的使用为准。
最后，应当理解的是，本申请中实施例仅用以说明本申请实施例的原则。其他的变形也可能属于本申请的范围。因此，作为示例而非限制，本申请实施例的替代配置可视为与本申请的教导一致。相应地，本申请的实施例不仅限于本申请明确介绍和描述的实施例。

Claims (31)

  1. 一种声学输出装置，包括：
    振动元件，所述振动元件包括沿着长度方向延伸的梁结构，所述梁结构包括：
    压电层，用于响应电信号而发生形变，所述形变带动所述振动元件振动；以及质量元件，所述质量元件连接于所述梁结构的第一位置，所述振动元件的振动带动所述质量元件在垂直于所述长度方向的方向上振动，其中，在沿着所述梁结构的长度方向上，所述第一位置到所述梁结构一端的距离与所述梁结构的长度之间的比值在0.3～0.95范围内。
  2. 根据权利要求1所述的声学输出装置，其特征在于，在50Hz-10000Hz范围内，所述质量元件的振动具有第一谐振峰和第二谐振峰。
  3. 根据权利要求2所述的声学输出装置，其特征在于，所述第一谐振峰和所述第二谐振峰之间的频响最低点与所述第一谐振峰或所述第二谐振峰之间的幅值差小于40dB。
  4. 根据权利要求3所述的声学输出装置，其特征在于，所述梁结构包括固定端和自由端。
  5. 根据权利要求4所述的声学输出装置，其特征在于，还包括第二质量元件，所述第二质量元件与所述自由端连接。
  6. 根据权利要求5所述的声学输出装置，其特征在于，所述第二质量元件与所述梁结构的质量之间的比值在0-1.2范围内。
  7. 根据权利要求6所述的声学输出装置，其特征在于，所述第一位置到所述固定端的距离与所述梁结构的长度之间的比值在0.7-0.95范围内。
  8. 根据权利要求7所述的声学输出装置，其特征在于，所述第二谐振峰的频率范围与所述第一谐振峰的频率范围之比大于17。
  9. 根据权利要求4所述的声学输出装置，其特征在于，所述质量元件的振动具有第三谐振峰，所述第二谐振峰和所述第三谐振峰之间的频响最低点与所述第二谐振峰或所述第三谐振峰之间的幅值差小于30dB。
  10. 根据权利要求9所述的声学输出装置，其特征在于，所述第三谐振峰的频率范围与所述第二谐振峰的频率范围之比大于4。
  11. 根据权利要求10所述的声学输出装置，其特征在于，所述第一位置到所述固定端的距离与所述梁结构的长度之间的比值在0.45-0.6范围内。
  12. 根据权利要求3所述的声学输出装置，其特征在于，所述梁结构包括两个固定端。
  13. 根据权利要求12所述的声学输出装置，其特征在于，所述第一位置到所述两个固定端中一个固定端的距离与所述梁结构的长度之间的比值在0.3-0.4范围内。
  14. 根据权利要求13所述的声学输出装置，其特征在于，所述第二谐振峰的频率范围与所述第 一谐振峰的频率范围之比大于13。
  15. 根据权利要求12所述的声学输出装置，其特征在于，所述质量元件的振动具有第三谐振峰，所述第二谐振峰和所述第三谐振峰之间的频响最低点与所述第二谐振峰或所述第三谐振峰之间的幅值差小于40dB。
  16. 根据权利要求15所述的声学输出装置，其特征在于，所述第三谐振峰的频率范围与所述第二谐振峰的频率范围之比大于2。
  17. 根据权利要求16所述的声学输出装置，其特征在于，所述第一位置到所述两个固定端中一个固定端的距离与所述梁结构的长度之间的比值在0.45-0.5范围内。
  18. 根据权利要求12所述的声学输出装置，其特征在于，在沿着所述梁结构的宽度方向上，所述第一位置到所述梁结构一边的距离与所述梁结构的宽度之间的比值在0.15-0.3范围内。
  19. 根据权利要求3所述的声学输出装置，其特征在于，所述梁结构包括固定端和铰支端，在所述振动元件振动过程中，所述铰支端沿与所述梁结构的长度方向和振动方向垂直的轴转动。
  20. 根据权利要求19所述的声学输出装置，其特征在于，所述第一位置到所述固定端的距离与所述梁结构的长度之间的比值在0.5-0.6范围内。
  21. 根据权利要求20所述的声学输出装置，其特征在于，所述第二谐振峰的频率范围与所述第一谐振峰的频率范围之比大于6。
  22. 根据权利要求3所述的声学输出装置，其特征在于，所述梁结构包括两个铰支端，在所述振动元件振动过程中，所述两个铰支端分别沿与所述梁结构的长度方向和振动方向垂直的轴转动。
  23. 根据权利要求11所述的声学输出装置，其特征在于，所述第一位置到所述两个铰支端中的一个铰支端的距离与所述梁结构的长度之间的比值在0.3-0.4范围内。
  24. 根据权利要求12所述的声学输出装置，其特征在于，所述第二谐振峰的频率范围与所述第一谐振峰的频率范围之比大于10。
  25. 根据权利要求3所述的声学输出装置，其特征在于，所述梁结构包括两个弹性端，所述两个弹性端分别通过弹性件与所述声学输出装置的固定支座弹性连接。
  26. 根据权利要求25所述的声学输出装置，其特征在于，所述梁结构为两端对称结构，所述两个弹性端对应的弹性件沿着所述梁结构的长度方向或宽度方向对称设置。
  27. 根据权利要求26所述的声学输出装置，其特征在于，所述第一谐振峰的频率范围在300Hz-700Hz。
  28. 根据权利要求26所述的声学输出装置，其特征在于，所述第一位置到所述两个弹性端中一个弹性端的距离与所述梁结构的长度之间的比值在0.1-0.25范围内。
  29. 根据权利要求3所述的声学输出装置，其特征在于，还包括第三振动元件，所述第三振动元件包括第三梁结构，其中，所述梁结构和所述第三梁结构的一端为固定端，所述梁结构和所述第三梁结构的另一端通过弹性连接件连接。
  30. 根据权利要求1所述的声学输出装置，其特征在于，所述振动元件的数量为两个或以上，其中，所述两个或以上振动元件中每个振动元件的梁结构包括固定端和自由端。
  31. 根据权利要求30所述的声学输出装置，其特征在于，所述质量元件分别连接于所述两个或以上振动元件中每个振动元件的梁结构的第一位置，每个梁结构的第一位置与所述梁结构的固定端之间的距离与所述梁结构的长度之间的比值在0.7-0.95范围内。
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