Loudspeaker

Abstract

One or more embodiments of the present specification relate to a loudspeaker, comprising: a housing, a driving unit and a vibration unit, the driving unit being fixed to the housing, the driving unit being in transmission connection with the vibration unit; wherein the driving unit comprises a plurality of driving beams, any driving beam comprises a fixed area and a suspended area, any driving beam is connected with the shell through the fixed area, and any driving beam is in transmission connection with the vibration unit through the suspended area.

Description

A speaker

[0001] Cross-references

[0002] This specification claims priority to Chinese application No. 202310444739.0 filed on April 14, 2023, Chinese application No. 202310446118.6 filed on April 14, 2023, and Chinese application No. 202310425028.9 filed on April 14, 2023, all contents of which are incorporated herein by reference. Technical Field

[0003] This specification relates to the field of acoustic technology, and in particular to a loudspeaker. Background Art

[0004] Piezoelectric speakers use the inverse piezoelectric effect of piezoelectric materials to generate vibrations and radiate sound waves outward. Compared with traditional electric speakers, they have the advantages of high electromechanical conversion efficiency, low energy consumption, small size, and high integration. With the current trend of miniaturization and integration of devices, piezoelectric speakers have extremely broad prospects and a future. Speakers generally include three core parts: a driving part, a vibration part, and a supporting auxiliary part. The biggest problem faced by general piezoelectric speakers, especially micro speakers, is the insufficient driving capacity of the driving part, which results in a low output sound pressure level (SPL) of the speaker in a specific frequency range (for example, 20Hz-20kHz range), resulting in low sensitivity in the audible range.

[0005] Summary of the Invention

[0006] An embodiment of the present specification provides a loudspeaker, comprising: a shell, a drive unit and a vibration unit, wherein the drive unit is fixed to the shell and is transmission-connected to the vibration unit; wherein the drive unit comprises a plurality of drive beams, any one of the drive beams comprises a fixed area and a suspended area, any one of the drive beams is connected to the shell via the fixed area, and any one of the drive beams is transmission-connected to the vibration unit via the suspended area. BRIEF DESCRIPTION OF THE DRAWINGS

[0007] This specification will be further described in the form of exemplary embodiments, which will be described in detail with reference to the accompanying drawings. These embodiments are not limiting, and in these embodiments, like numbers represent like structures, wherein:

[0008] FIG1A is a schematic diagram of the internal structure of a speaker according to some embodiments of this specification;

[0009] FIG1B is a schematic diagram of the internal structure of a speaker according to other embodiments of this specification;

[0010] FIG2 is a schematic diagram of a model of a mass-spring-damper system according to some embodiments of this specification;

[0011] FIG3 is a velocity resonance curve diagram of a mass-spring-damper system according to some embodiments of the present specification;

[0012] FIG4 is a schematic diagram of an equivalent mechanical model of a loudspeaker according to some embodiments of this specification;

[0013] FIG5 is a schematic diagram of a speaker according to some embodiments of this specification;

[0014] FIG6 is a schematic diagram of a speaker from another perspective according to some embodiments of this specification;

[0015] FIG7 is a schematic cross-sectional view of the loudspeaker shown in FIG6 of this specification;

[0016] FIG8 is a schematic structural diagram of a driving unit according to some embodiments of this specification;

[0017] FIG9 is a schematic diagram showing the connection between the driving beam and the vibration transmission unit according to some embodiments of this specification;

[0018] FIG10 is another schematic structural diagram of a driving unit according to some embodiments of this specification;

[0019] FIG11 is a schematic diagram of the internal structure of a driving beam according to some embodiments of this specification;

[0020] FIG12 is a schematic diagram of frequency response curves of a loudspeaker corresponding to different parameters α according to some embodiments of this specification;

[0021] FIG13 is a schematic diagram of frequency response curves of a loudspeaker corresponding to different values ​​of β according to some embodiments of this specification;

[0022] 14A to 14E are schematic diagrams of driving beams with different structures according to some embodiments of this specification;

[0023] FIG15A is a partial structural diagram of an exemplary speaker according to some embodiments of this specification;

[0024] FIG15B is a schematic diagram of the internal structure of the driving unit of the speaker in FIG15A of this specification;

[0025] FIG15C is a partial structural diagram of an exemplary speaker according to some embodiments of this specification;

[0026] FIG15D is a schematic diagram of the internal structure of the driving unit of the speaker in FIG15C of this specification;

[0027] 16A to 16G are schematic diagrams of drive units with different structures according to some embodiments of this specification;

[0028] 17A to 17K are schematic diagrams of drive units with different structures according to some embodiments of this specification;

[0029] FIG17L is a schematic diagram of the internal structure of the driving unit corresponding to FIG17K of this specification;

[0030] FIG17M is a schematic diagram of a deformation of the driving beam shown in FIG17L of this specification;

[0031] FIG17N is a diagram illustrating frequency response curves of a loudspeaker including a folded structure driving beam and a loudspeaker including a non-folded structure driving beam according to FIG17L of this specification;

[0032] FIG17O is another schematic diagram of the internal structure of the driving unit corresponding to FIG17K of this specification;

[0033] FIG17P is a schematic diagram of a deformation of the driving beam shown in FIG17O according to this specification;

[0034] FIG17Q is a diagram illustrating frequency response curves of a loudspeaker including a folded structure driving beam and a loudspeaker including a non-folded structure driving beam according to FIG17O of this specification;

[0035] FIG17R is another schematic diagram of the internal structure of the driving unit corresponding to FIG17K of this specification;

[0036] FIG17S is another schematic structural diagram of a driving unit according to some embodiments of this specification;

[0037] FIG17T is another schematic structural diagram of a driving unit according to some embodiments of this specification;

[0038] 18A and 18B are schematic diagrams of the internal structure of driving units with different structures according to some embodiments of this specification;

[0039] FIG18C is a schematic diagram of frequency response curves of a loudspeaker corresponding to different values ​​of κ according to some embodiments of this specification;

[0040] 19A and 19B are schematic diagrams of driving units with different structures according to some embodiments of this specification;

[0041] FIG20A is a first view of the speaker shown in FIG1B according to this specification;

[0042] FIG20B is a cross-sectional view of the speaker shown in FIG20A according to this specification;

[0043] FIG20C is a second view of the speaker shown in FIG1B according to this specification;

[0044] FIG20D is a cross-sectional view of the speaker shown in FIG20C according to this specification;

[0045] FIG20E is a schematic structural diagram of a speaker according to some embodiments of this specification;

[0046] FIG20F is a cross-sectional view of the speaker shown in FIG20E according to this specification;

[0047] FIG20G is a schematic structural diagram of a speaker according to other embodiments of this specification;

[0048] FIG20H is a cross-sectional view of the speaker shown in FIG20G according to this specification;

[0049] FIG20I is a schematic structural diagram of a speaker according to yet other embodiments of this specification;

[0050] FIG20J is a cross-sectional view of the loudspeaker shown in FIG20I according to this specification;

[0051] FIG21A is a projection diagram of a driving beam along the vibration direction of a vibration unit according to some embodiments of this specification;

[0052] 21B to 21M are projection diagrams of the driving beam and the diaphragm along the vibration direction of the vibration unit according to some embodiments of this specification;

[0053] FIG22 is a projection diagram of a driving beam and a diaphragm along the z direction shown in some other embodiments of this specification;

[0054] FIG23 is a frequency response curve diagram of a loudspeaker corresponding to different values ​​of μ according to some embodiments of this specification;

[0055] FIG24 is a vibration deformation cloud diagram of a driving beam and a diaphragm divided into one quarter along the symmetry lines in the x-direction and the y-direction when μ=0.6 according to some embodiments of this specification;

[0056] FIG25 is a frequency response curve diagram of a loudspeaker corresponding to different values ​​of δ according to some embodiments of this specification;

[0057] FIG26 is a vibration deformation cloud diagram of a driving beam and a diaphragm divided into one quarter along the symmetry lines in the x-direction and the y-direction when δ=0.5 according to some embodiments of this specification;

[0058] FIG27 is a side view of a driving beam with electrodes along the y direction according to some embodiments of this specification;

[0059] FIG28 is a side view of a driving beam with electrodes along the y direction according to some embodiments of the present specification;

[0060] FIG29 is a projection diagram of a driving beam along the z direction according to some embodiments of the present specification;

[0061] FIG30 is a schematic diagram of frequency response curves of a loudspeaker corresponding to different γ values ​​according to some embodiments of this specification;

[0062] FIG31 is a vibration deformation cloud diagram of a driving beam and a diaphragm divided into one quarter along the symmetry lines in the x-direction and the y-direction when γ=1 according to some embodiments of this specification;

[0063] FIG32 is a vibration deformation cloud diagram of a driving beam and a diaphragm divided into one quarter along the symmetry lines in the x-direction and the y-direction when γ=0.75 according to some embodiments of this specification;

[0064] FIG33 is a schematic diagram of frequency response curves of a loudspeaker corresponding to different τ values ​​according to some embodiments of this specification;

[0065] 34A to 34F are projection diagrams of a driving beam along the z direction according to some embodiments of the present specification;

[0066] FIG35 is a partial schematic diagram of a vibration unit according to some embodiments of this specification;

[0067] FIG36 is a schematic structural diagram of a diaphragm according to some embodiments of this specification;

[0068] FIG37 is a schematic diagram of a vibration unit according to some embodiments of this specification;

[0069] FIG38A is a deformation cloud diagram of a loudspeaker corresponding to a parameter ζ=0.5 according to some embodiments of this specification;

[0070] FIG38B is a deformation cloud diagram of the speaker corresponding to FIG38A according to another perspective of this specification;

[0071] FIG39A is a deformation cloud diagram of a loudspeaker corresponding to a parameter ζ=0.4 according to some embodiments of this specification;

[0072] FIG39B is a deformation cloud diagram of the speaker corresponding to FIG39A according to another perspective of this specification;

[0073] FIG40 is a deformation cloud diagram of a loudspeaker corresponding to a parameter ζ=0.9 according to some embodiments of this specification;

[0074] FIG41 is a schematic diagram of frequency response curves of loudspeakers corresponding to different z values ​​according to some embodiments of this specification;

[0075] FIG42 is a schematic diagram of a diaphragm according to some embodiments of the present specification;

[0076] FIG43 is a schematic diagram of frequency response curves of a loudspeaker corresponding to different lambda values ​​according to some embodiments of this specification;

[0077] 44A to 44C are partial schematic diagrams of speakers according to some embodiments of this specification;

[0078] FIG45 is a schematic diagram of the internal structure of a speaker with a slit structure according to some embodiments of this specification;

[0079] 46A-46B are schematic diagrams of partial structures of speakers according to some embodiments of this specification;

[0080] FIG47 is a schematic diagram of a partial structure of a speaker according to some other embodiments of this specification;

[0081] FIG48 is a projection diagram of a vibration unit along the vibration direction of a diaphragm according to some embodiments of this specification;

[0082] FIG49A is a schematic diagram of a speaker according to some embodiments of the present specification;

[0083] FIG49B is a projection diagram of a driving beam and a diaphragm along the vibration direction of the vibration unit according to some embodiments of this specification;

[0084] 50A-50B are schematic diagrams of a loudspeaker including a plurality of parallel driving units according to some embodiments of the present specification. DETAILED DESCRIPTION

[0085] To more clearly illustrate the technical solutions of the embodiments of this specification, the following briefly describes the drawings required for describing the embodiments. Obviously, the drawings described below are merely examples or embodiments of this specification. Those skilled in the art can apply this specification to other similar scenarios based on these drawings without inventive effort. Unless otherwise apparent from the context or otherwise noted, the same reference numerals in the figures represent the same structure or operation.

[0086] It should be understood that the terms "system," "device," "unit," and / or "module" used herein are a method for distinguishing different components, elements, parts, portions, or assemblies at different levels. However, if other terms can achieve the same purpose, the terms may be replaced by other expressions.

[0087] As used in this specification and claims, unless the context clearly indicates otherwise, the words "a," "an," "an," and / or "the" do not refer to the singular but also include the plural. Generally speaking, the terms "comprises" and "include" only indicate the inclusion of the steps and elements specifically identified, and these steps and elements do not constitute an exclusive list. A method or apparatus may also include other steps or elements.

[0088] Flowcharts are used throughout this specification to illustrate the operations performed by systems according to embodiments of this specification. It should be understood that preceding or following operations do not necessarily need to be performed in exact order. Instead, the steps may be processed in reverse order or simultaneously. Furthermore, other operations may be added to these processes, or one or more operations may be removed from these processes.

[0089] FIG1A is a schematic diagram of the internal structure of a loudspeaker according to some embodiments of this specification. FIG1B is a schematic diagram of the internal structure of a loudspeaker according to other embodiments of this specification. FIG2 is a schematic diagram of a model of a mass-spring-damper system according to some embodiments of this specification. FIG3 is a velocity resonance curve diagram of a mass-spring-damper system according to some embodiments of this specification. FIG4 is a schematic diagram of an equivalent mechanical model of a loudspeaker according to some embodiments of this specification. The vibration process of the loudspeaker is described below in conjunction with FIG1A to FIG4.

[0090] 1A , in some embodiments, a speaker 100 may include a housing 110 , a driving unit 120 , a vibration unit 130 , etc. In some embodiments, the driving unit 120 is fixed to the housing 110 , and the driving unit 120 is in transmission connection with the vibration unit 130 .

[0091] The speaker 100 can be used to convert an audio signal (e.g., an electrical signal containing sound information) into a sound signal. In some embodiments, the speaker 100 can be a bone conduction speaker, an air conduction speaker, or a bone-air conduction combined speaker. In some embodiments, the speaker 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. For example, the speaker 100 can be applied to functional myopia glasses, reading glasses, cycling glasses, or sunglasses, etc., or it can be smart glasses, such as audio glasses with headphone function. In some embodiments, the speaker 100 can also be applied to head-mounted devices such as helmets, augmented reality (AR) devices, or virtual reality (VR) devices. In some embodiments, augmented reality devices or virtual reality devices can include virtual reality helmets, virtual reality glasses, augmented reality helmets, augmented reality glasses, etc., or any combination thereof. For example, virtual reality devices and / or augmented reality devices can include Google Glass, Oculus Rift, Hololens, Gear VR, etc.

[0092] The driving unit 120 serves as the driving end of the loudspeaker 100 and provides driving force for the loudspeaker 100 by converting electrical energy into mechanical energy. The types of the driving unit 120 may include, but are not limited to, electromagnetic, electrostatic, piezoelectric, etc. The vibration unit 130 serves as the load end of the loudspeaker 100 and includes a diaphragm 131 and a central reinforcement 132. In some embodiments, the diaphragm 131 may include an edge fixing portion 1311, a folding ring portion 1312, and a central portion 1313, wherein the edge fixing portion 1311 may be fixedly connected to the housing 110 of the loudspeaker 100, and the central portion 1313 may be provided with a central reinforcement 132. In some embodiments, the central reinforcement 132 may be a single part, located on the upper side or lower side of the central portion 1313. In some embodiments, the central reinforcement 132 may also be a plurality of parts, located on the upper side and lower side of the central portion 1313, respectively. The driver unit 120 can be connected to the central reinforcement member 132, or directly connected to the central portion 1313 of the diaphragm 131, to achieve mechanical energy transmission from the driving end (driver unit 120) to the load end (vibration unit 130). In some embodiments, the speaker 100 may include a supporting auxiliary structure, which mainly includes a connecting and fixing portion between the driver unit 120 and the vibration unit 130 (e.g., the vibration transmission unit 140), the housing 110, etc. In some embodiments, the diaphragm 131 can divide the space within the housing 110 into two acoustic cavities (e.g., a front cavity 111 and a rear cavity 112). The speaker 100 can be provided with corresponding structures in the acoustic cavities (e.g., the front cavity 111 and the rear cavity 112), such as corresponding sound outlets (e.g., sound outlet 111a connected to the front cavity 111) and damping mesh 113 provided on the sound outlets in the housing 110, thereby adjusting the sensitivity and Q value of the frequency response curve of the speaker 100 and improving the output performance of the speaker 100.

[0093] In some embodiments, the speaker 100 can be equivalent to a model of multiple mass-spring-damper systems connected in series and parallel. In actual operation, when the operating frequency of the speaker 100 is far from the natural frequency f0 of a mass-spring-damper system, the system undergoes forced vibration under the action of the excitation load, transmitting force and displacement. When the operating frequency approaches the natural frequency f0 of a mass-spring-damper system, the system resonates, causing the corresponding local structure of the speaker 100 to vibrate at a higher speed, ultimately manifesting as corresponding peaks and valleys on the frequency response curve of the speaker 100.

[0094] Please refer to Figure 2 and analyze the single mass-spring-damper system shown in Figure 2. The motion of the single mass-spring-damper system shown in Figure 2 can be described by the following formula (1):

[0095] Where M is the system mass, R is the system damping, K is the system elastic coefficient, F is the driving force amplitude, x is the system displacement, and ω is the external force circular frequency.

[0096] Solving the above formula (1) for the steady-state speed yields:

[0097] Among them, v is the movement speed, v a is the movement speed amplitude.

[0098] Combining formula (1) and formula (2), the motion velocity amplitude of the system is:

[0099] Among them, Q m is the mechanical quality factor,

[0100] v a Divide by the normalization factor Define v B is the normalized velocity, then:

[0101] Referring to Figure 3, when the operating frequency f of the system is equal to the natural frequency f0 of the mass-spring-damper system, that is, when f=f0, the output motion velocity of the mass-spring-damper system reaches its maximum value:

[0102] The output sound pressure amplitude (sound pressure level) of the loudspeaker 100 is positively correlated with the output motion speed of the mass-spring-damper system, that is, p a ∝v a .

[0103] Therefore, by designing the output motion velocity amplitudes of each mass-spring-damper system of the loudspeaker 100 , the output sound pressure level of the loudspeaker 100 can be regulated.

[0104] Referring to FIG. 4 , in some embodiments, each unit of the speaker 100 (eg, the driving unit 120 , the vibration unit 130 , etc.) may be equivalent to a mechanical model as shown in FIG. 4 .

[0105] One end of the drive unit 120 is fixedly connected to the housing 110, and the other end is connected to the vibration unit 130. At the same time, the drive unit 120 is in contact with the air. Because the drive unit 120 has corresponding mass Md, damping R, and stiffness K, it can be equivalently connected to the housing 110 via a spring with stiffness Kd and a damper with damping Rd, with mass Md serving as an inertial unit. Furthermore, the drive unit 120 is connected to the vibration unit 130 via a spring Kp and a damper Rp, and is connected to the air load via a spring Ka2 and a damper Ra2. Furthermore, the drive unit 120, as an electrical energy-mechanical energy conversion unit, can output force F1 or displacement S1 for the vibration system of the speaker 100. In order to improve the output sound pressure level of the speaker 100, it is necessary to increase the force F1 or displacement S1 output by the drive unit 120, and match the impedance between the drive unit 120 and the vibration unit 130, so that the force F1 or displacement S1 output by the drive unit 120 can be transmitted to the vibration unit 130 with minimal loss, so that the vibration unit 130 outputs the maximum displacement or speed.

[0106] In the vibration unit 130, the total mass of the diaphragm 131, the central reinforcement 132, and the vibration transfer unit 140 can be equivalent to the total mass Mn. The diaphragm 131 is connected to the shell 110 through a spring with a stiffness of Km and a damper with a damping of Rm. At the same time, the diaphragm 131 is connected to the air load through the spring Ka1 and the damping Ra1, and realizes the radiation of sound pressure by pushing the air movement. The load of the diaphragm 131 changes with the change of the movement displacement of the diaphragm 131, so the diaphragm 131 is a variable load. In some embodiments, the load of the vibration unit 130 also includes the air part pushed by the diaphragm 131. This part of the load is an inertial load, which is mainly determined by the amount of air pushed by the diaphragm 131. At the same time, the amount of air pushed by the diaphragm 131 also determines the sound pressure level that the speaker 100 can output. In some embodiments, the vibration unit 130 can also be called a diaphragm assembly.

[0107] In summary, to improve the output performance (e.g., output sound pressure level) of the loudspeaker 100, the amount of air pushed by the diaphragm 131 can be increased (i.e., the vibration amplitude of the vibration unit 130 can be increased). To increase the vibration amplitude of the vibration unit 130, the force and displacement output by the driver unit 120 can be increased (e.g., by designing the structure of the driver beam 122 of the driver unit 120). Furthermore, the efficiency of force and displacement transmission between the driver unit 120 and the vibration unit 130 can be improved (e.g., by designing the coupling elastic structure 124 of the driver unit 120).

[0108] In some embodiments, the drive unit 120 includes a plurality of drive beams, and any one of the drive beams includes a fixed area and a suspended area. Any one of the drive beams is connected to the housing 110 through the fixed area to achieve fixation, and any one of the drive beams is connected to the vibration unit 130 through the suspended area to drive the vibration unit 130 to vibrate and generate sound output. In some embodiments, the structure of the drive unit 120 can be designed to enhance the driving capability (output force and displacement) of the drive unit 120, thereby enhancing the output sound pressure level of the loudspeaker 100. In some embodiments, the suspended area has a length dimension in the direction extending from the fixed area to the suspended area; and the suspended area has a thickness dimension in the vibration direction of the vibration unit 130 (diaphragm 131). During the vibration of the drive beam, deformation mainly occurs in the suspended area, thereby providing driving force and displacement for the vibration unit 130. By designing the size of the suspended area of ​​the drive beam, the deformation of the drive beam can be regulated, thereby enhancing the driving capability of the drive beam and enhancing the output of the loudspeaker 100. On the other hand, the drive unit 120, as a spring-mass-damper system, provides stiffness and mass to the entire loudspeaker 100, thereby affecting the resonant frequency of the loudspeaker 100. By designing the structural parameters of the drive beam, the stiffness and mass of the drive unit 120 can be adjusted, thereby regulating the vibration mode of the loudspeaker 100 and optimizing the loudspeaker's output performance.

[0109] Figure 5 is a schematic diagram of a speaker according to some embodiments of this specification. Figure 6 is a schematic diagram of a speaker from another perspective according to some embodiments of this specification. Figure 7 is a cross-sectional schematic diagram of the speaker shown in Figure 6. Figure 8 is a schematic diagram of the structure of a drive unit according to some embodiments of this specification. Figure 9 is a schematic diagram of the connection between a drive beam and a vibration transmission unit according to some embodiments of this specification. Figure 10 is another schematic diagram of the structure of a drive unit according to some embodiments of this specification. Figure 11 is a schematic diagram of the internal structure of a drive beam according to some embodiments of this specification.

[0110] Please refer to Figures 5, 6 and 7. In some embodiments, the speaker 100 may include a housing 110, a drive unit 120 and a vibration unit 130. The housing 110 mainly provides a platform for mounting and fixing other components of the speaker 100. In some embodiments, the shape of the housing 110 may be circular, elliptical, quadrilateral (including but not limited to square, rectangle, diamond, kite, etc.), pentagon, hexagon, octagon and other polygons. The following example illustrates the speaker 100 with the shape of the housing 110 being rectangular. In some embodiments, the housing 110, the drive unit 120 and the vibration unit 130 may form an acoustic cavity (e.g., a rear cavity 112), as shown in Figure 7. In some embodiments, the vibration of the vibration unit 130 may drive the air in the rear cavity 112 to vibrate and generate sound output. In some embodiments, the vibration unit 130 may also vibrate to drive the air on the side of the vibration unit 130 away from the rear cavity 112 to vibrate and generate sound output.

[0111] The drive unit 120 is fixed to the housing 110 and is in transmission connection with the vibration unit 130. The drive unit 120 can drive the vibration unit 130 to vibrate to generate sound output. Referring to Figures 8 and 10, in some embodiments, the drive unit 120 may include a drive beam 122, which may be a beam-shaped structure. The drive beam 122 may include a fixed region 122-1 and a suspended region 122-2. The drive beam 122 is connected to the housing 110 via the fixed region 122-1, and is in transmission connection with the vibration unit 130 via the suspended region 122-2 (or the free end of the drive beam 122). Referring to Figures 8, 10, and 11, in some embodiments, the suspended region 122-2 has a length dimension l in the direction extending from the fixed region 122-1 to the suspended region 122-2; in the vibration direction of the vibration unit 130, the suspended region 122-2 (drive beam 122) has a thickness dimension h. Since the vibration of the vibration unit 130 is driven by the deformation of the drive beam 122, the vibration direction of the vibration unit 130 is the same as the deformation direction of the drive beam 122. The length dimension l and thickness dimension h of the suspended region 122-2 can affect the deformation of the suspended region 122-2, thereby affecting the force and displacement output by the drive beam 122, and further affecting the output sound pressure level of the speaker 100. Therefore, the length dimension l and thickness dimension h of the suspended region 122-2 can be designed to improve the output sound pressure level of the speaker 100.

[0112] Referring to Figures 7-10, in some embodiments, the driving unit 120 may further include a coupling elastic structure 124. The suspended region 122-2 of the driving beam 122 is transmission-connected to the vibration unit 130 via the coupling elastic structure 124. The coupling elastic structure 124 can effectively transmit the force and displacement generated by the deformation of the driving beam 122 to the vibration unit 130. In some embodiments, there may be one or more driving beams 122, and each driving beam 122 may correspond to one or more coupling elastic structures 124. In some embodiments, the coupling elastic structure 124 may be made of semiconductor materials, polymer materials, or the like. Exemplary semiconductor materials include silicon (Si), silicon dioxide (SiO2), silicon nitride (SiNx), and silicon carbide (SiC). Exemplary polymer materials include polyimide (PI), parylene, polydimethylsiloxane (PDMS), hydrogel, photoresist, silicone, silicone gel, silicone sealant, and the like. In some embodiments, the coupling elastic structure 124 may have a single-layer or multi-layer structure. For example, the coupling elastic structure 124 may have a single-layer structure made of a semiconductor material (e.g., Si, SiO2) or a polymer material (e.g., polyimide). For another example, the coupling elastic structure 124 may have a multi-layer structure made of multiple semiconductor materials (e.g., a Si / SiO2 double-layer structure, a Si / SiNx double-layer structure, etc.). For another example, the coupling elastic structure 124 may have a multi-layer structure made of multiple polymer materials. For another example, the coupling elastic structure 124 may have a multi-layer structure made of a polymer material and a semiconductor material.

[0113] Referring to Figures 7, 8, and 10, in some embodiments, the drive unit 120 may further include a base 126, which is secured to the housing 110 via the base 126. In some embodiments, the shape of the base 126 may be consistent with the shape of the housing 110. For example, when the housing 110 is rectangular, the base 126 may be a rectangular ring. Referring to Figure 10, in some embodiments, the fixed region 122-1 of the drive beam 122 is secured to the base 126. In the direction extending from the fixed region 122-1 to the suspended region 122-2, the length of the fixed region 122-1 may be considered to be equal to the width of the base 126. In some embodiments, the length of the fixed region 122-1 may be less than the width of the base 126. When the length of the fixed region 122-1 is considered to be equal to the width of the base 126, the length dimension l of the suspended region 122 can be calculated by subtracting the width of the base 126 from the total length of the drive beam 122.

[0114] In some embodiments, the vibration unit 130 can receive the force or displacement transmitted by the driving unit 120 and generate corresponding vibrations, thereby driving the air movement. Referring to Figures 5 and 7, in some embodiments, the vibration unit 130 mainly includes a diaphragm 131 and a central reinforcement 132. The diaphragm 131 is transmission-connected to the suspended area 122-2 of one or more driving beams 122 through a coupling elastic structure 124. The force and displacement generated by the deformation of the suspended area 122-2 are transmitted to the diaphragm 131, driving the diaphragm 131 to vibrate. The diaphragm 131 can be regarded as being partially connected to the air inertial load through springs and damping, and achieving sound pressure radiation through air movement. The load of the air pushed by the diaphragm 131 is an inertial load, which is mainly determined by the amount of air pushed by the diaphragm 131. At the same time, the amount of air pushed by the diaphragm 131 also determines the sound pressure level that the speaker 100 can output. By enhancing the driving performance of the driving unit 120, the maximum displacement or speed output by the diaphragm 131 can be increased, the amount of air pushed by the diaphragm 131 can be increased, and the output performance of the speaker 100 can be enhanced. In some embodiments, the material of the diaphragm 131 can include but is not limited to organic polymer materials. In some embodiments, the organic polymer material can be any one of polyethylene terephthalate (PET), polyetherimide (PEI), polyimide (PI), polyetheretherketone (PEEK), silicone, etc., or a combination thereof. In some embodiments, the diaphragm 131 can have a single-layer or multi-layer structure. For example, the diaphragm 131 can have a single-layer structure made of a polymer material (for example, polyimide). For another example, the diaphragm 131 can have a multi-layer structure made of multiple polymer materials.

[0115] In some embodiments, the central reinforcement member 132 is disposed in the central area of ​​the diaphragm 131. The central reinforcement member 132 can adjust the stiffness of the diaphragm 131, thereby adjusting the vibration mode of the diaphragm 131, thereby improving the vibration mode of the speaker 100 and enhancing the output performance of the speaker 100. For example, the central reinforcement member 132 can adjust the high-order vibration mode of the diaphragm 131 at high frequencies. The range of high frequencies corresponding to different scenarios may vary. For example, in some scenarios, high frequencies may refer to frequencies above 3 kHz; in other scenarios, high frequencies may refer to frequencies between 10 kHz and 20 kHz. In some embodiments, the central reinforcement member 132 can be disposed on the side of the diaphragm 131 close to the rear cavity 112 (as shown in FIG. 7 ), or on the side of the elastic member 131 facing away from the rear cavity 112. In some embodiments, the material of the central reinforcement member 132 may include metal materials, semiconductor materials, anisotropic materials, etc. Exemplary metal materials may include stainless steel, aluminum alloys, magnesium-lithium alloys, copper, copper alloys, etc. Exemplary anisotropic materials may include carbon fiber, FR4 epoxy glass fiber board, etc. Exemplary semiconductor materials may include silicon (Si), silicon dioxide (SiO2), silicon nitride (SiNx), silicon carbide (SiC), etc. In some embodiments, when the material of the central reinforcement 132 is a semiconductor material, the central reinforcement 132 may have a single-layer or multi-layer structure. For example, the central reinforcement 132 may have a single-layer structure made of a semiconductor material (e.g., Si, SiO2). For another example, the coupled elastic structure 124 may have a multi-layer structure made of multiple semiconductor materials (e.g., a Si / SiO2 double-layer structure, a Si / SiNx double-layer structure, etc.).

[0116] Referring to Figures 7, 8, and 9, in some embodiments, the speaker 100 may further include a vibration transmission unit 140. The vibration transmission unit 140 is respectively connected to the driver unit 120 (e.g., the drive beam 122 or the coupling elastic structure 124) and the diaphragm 131. The vibration transmission unit 140 can transmit the driving force and displacement output by the driver unit 120 to the diaphragm 131, causing the diaphragm 131 to vibrate, thereby generating sound output. In some embodiments, to reduce the transmission loss of force and displacement between the driver unit 120 and the diaphragm 131, the vibration transmission unit 140 can be made of a material with high stiffness and low density. In some embodiments, the material of the vibration transmission unit 140 may include metal materials, semiconductor materials, etc. Exemplary metal materials include stainless steel, aluminum alloy, magnesium-lithium alloy, copper, copper alloy, etc. Exemplary semiconductor materials include silicon (Si), silicon dioxide (SiO2), silicon nitride (SiNx), silicon carbide (SiC), etc. In some embodiments, when the vibration transmission unit 140 is made of a semiconductor material, the central reinforcement member 132 may have a single-layer or multi-layer structure. For example, the vibration transmission unit 140 may have a single-layer structure made of a single semiconductor material (e.g., Si, SiO2). For another example, the vibration transmission unit 140 may have a multi-layer structure made of multiple semiconductor materials (e.g., a Si / SiO2 double-layer structure, a Si / SiNx double-layer structure, etc.).

[0117] In some embodiments, a single driving beam 122 can be regarded as a loaded beam-shaped cantilever structure, and its natural frequency calculation formula can be determined by formula (6):

[0118] Among them, β n l is a constant term, and its value varies with the value of n, as follows: β1l==1.875104, β2l=4.694091, β3l=7.854757, β4l=10.995541, β5l=14.1372; E is the Young's modulus of the material of the driving beam 122, I is the moment of inertia, ρ is the density of the material of the driving beam 122, l is the length of the cantilever beam (i.e., the length dimension of the suspended area 122 of the driving beam 122), and h is the thickness of the cantilever beam (i.e., the thickness dimension of the driving beam 122 and the suspended area 122-2).

[0119] According to formula (6), by designing the structure and size of the driving beam 122 , the natural frequency of the driving beam 122 can be adjusted, thereby improving the output performance of the loudspeaker 100 .

[0120] In some embodiments, referring to Figures 7, 10 and 11, for any one driving beam 122, in the direction extending from the fixed area 122-1 to the suspended area 122-2 (i.e., the x direction shown in the figure), the suspended area 122-2 has a length dimension l; in the vibration direction of the vibration unit 130 (i.e., the z direction shown in the figure), the suspended area 122-2 has a thickness dimension h.

[0121] In some embodiments, the value of the ratio of the thickness dimension of the overhanging region 122-2 to the square of the length dimension of the overhanging region 122-2 to the power of one-half is in the range of 0.01-0.3. In some embodiments, a parameter α can be defined to represent the relationship between the length dimension l and the thickness dimension h of the overhanging region 122-2. That is, α is the power of one-half of the ratio of the thickness dimension h to the square of the length dimension l. For example, α can be expressed by formula (7):

[0122] In some embodiments, the value of α can reflect the stiffness of the suspended area 122-2 of the driving beam 122. When the value of α is small, the thickness h of the suspended area 122-2 is small, the length l is large, the suspended area 122-2 is easily deformed, and the stiffness is small. When the value of α is large, the thickness h of the suspended area 122-2 is large, the length l is small, the suspended area 122-2 is not easily deformed, and the stiffness is large. In some embodiments, the value range of α can be 0.01-0.3, so as to design the deformation of the suspended area 122-2 and the stiffness and mass of the driving unit 120, thereby improving the sensitivity of the speaker 100, optimizing the vibration mode of the speaker 100, and enhancing the output performance of the speaker 100. For more information about α, please refer to Figure 12 and related content, which will not be repeated here.

[0123] FIG12 is a schematic diagram of the frequency response curves of a speaker corresponding to different parameters α according to some embodiments of this specification. As shown in FIG12 , curve L121 represents the frequency response curve of speaker 100 when α = 0.02; curve L122 represents the frequency response curve of speaker 100 when α = 0.04; curve L123 represents the frequency response curve of speaker 100 when α = 0.09; curve L124 represents the frequency response curve of speaker 100 when α = 0.1; and curve L125 represents the frequency response curve of speaker 100 when α = 0.15. As can be seen from FIG12 , when α = 0.02, the stiffness of drive beam 122 is very low, and drive beam 122 cannot effectively drive the load. The output of speaker 100 is very low, and curve L121 is generally low. Second-order modes are generated in the lower frequency range (e.g., 500Hz-2000Hz), resulting in peaks and valleys in the frequency response. When α = 0.04, the stiffness of the driving beam 122 is relatively low, and the overall height of the corresponding curve L122 is relatively low. The output of the loudspeaker 100 is relatively low, and the position of the resonance peak corresponding to curve L122 is shifted to the left, with the corresponding resonance frequency f being between 500Hz and 1000Hz in the low-frequency range. Compared to α = 0.02, when α = 0.04, the output of the loudspeaker 100 increases, and the curve L122 is generally located above the curve L121. Curve L122 does not exhibit peaks and valleys in the lower frequency range (e.g., 500Hz-2000Hz), and the frequency response characteristics of the loudspeaker 100 are significantly improved. As the value of α gradually increases from 0.04 to 0.15, the overall curve gradually shifts upward, the resonance peak position of the corresponding curve gradually shifts to the right, and the corresponding resonance frequency f gradually increases. When α = 0.1, the resonance peak corresponding to curve L124 is between 1000Hz and 2000Hz, i.e., the corresponding resonance frequency f is between 1000Hz and 2000Hz. Curve L124 is generally high, indicating that the speaker 100 has high output at low frequencies (e.g., 500Hz to 2000Hz), but low output at mid- and high-frequency frequencies (e.g., above 2000Hz). When α = 0.15, the stiffness of the driving beam 122 is greater, and the resonance peak corresponding to curve L125 is positioned to the right, corresponding to the resonance frequency f between 2000Hz and 5000Hz. Curve L125 is generally high, indicating that the speaker 100 has high output sound pressure levels at mid- and high-frequency frequencies (e.g., above 2000Hz), but low output at low frequencies (e.g., 1000Hz to 2000Hz). Taking all factors into consideration, to ensure that the speaker 100 has a certain output in both the low and mid-high frequency ranges, α can be set in the range of 0.04-0.15. In some embodiments, to improve the output of the speaker 100 in the low frequency and mid-high frequency range, the value of α may be in the range of 0.05-0.13. For example, the value of α may be 0.1, so that the speaker 100 has a higher output in the low frequency and mid-high frequency range.

[0124] It should be noted that the main frequency band range of the speaker 100 can be determined according to the different application scenarios of the speaker 100, thereby adopting different values ​​of the parameter α. For example, when the speaker 100 is mainly used in high-frequency scenarios, the value of α can be 0.15, and the corresponding resonant frequency f of the speaker 100 is between 2000Hz-5000Hz, and the output of the speaker 100 in the mid- and high-frequency range is relatively large. For another example, when the speaker 100 is mainly used in full-band application scenarios, the effective frequency band of the speaker 100 needs to be as wide as possible. At this time, the value of α can be 0.09, and the frequency response curve L123 of the corresponding speaker 100 has a relatively large flat area, and has a relatively large output in both low frequencies (for example, 500Hz-2000Hz) and mid- and high frequencies (for example, above 2000Hz).

[0125] Because the vibration of the vibration unit 130 is driven by the deformation of the drive beam 122, the vibration direction of the vibration unit 130 is the deformation direction of the drive beam 122 (i.e., the z-direction). In some embodiments, as shown in FIG11 , the drive beam 122 includes a substrate layer 1225, a first electrode layer 12211, a piezoelectric layer 12212, a second electrode layer 12213, and a reinforcement layer 1223 stacked along the vibration direction of the vibration unit 130 (i.e., the z-direction).

[0126] In some embodiments, as shown in FIG11 , a first electrode layer 12211, a piezoelectric layer 12212, and a second electrode layer 12213 can form a piezoelectric structure 1221, with the first electrode layer 12211 and the second electrode layer 12213 located on opposite sides of the piezoelectric layer 12212. In some embodiments, the piezoelectric structure 1221 can cause the driving unit 120 to output vibrations from the suspended region 122-2 in response to an electrical signal. The piezoelectric structure 1221 can partially or completely cover the suspended region 122-2 in the direction extending from the fixed region 122-1 to the suspended region 122-2.

[0127] In some embodiments, the piezoelectric structure 1221 can be deformed under the action of a driving voltage, thereby generating vibration. In some embodiments, the piezoelectric layer 12212 can be made of a material having a piezoelectric effect (such as piezoelectric ceramics, piezoelectric quartz, piezoelectric crystals, piezoelectric polymers, etc.). Exemplary materials of the piezoelectric layer 12212 can include but are not limited to aluminum nitride (AlN), lead zirconate titanate (PZT), zinc oxide (ZnO), etc. In some embodiments, the first electrode layer 12211 and the second electrode layer 12213 can be made of a material with strong conductivity (such as a metal, an alloy, a conductive polymer material, etc.). For example, the first electrode layer 12211 and the second electrode layer 12213 can include metal silver (Ag), molybdenum (Mo), copper (Cu), gold (Au), titanium-gold alloy (Ti / Au), titanium (Ti), aluminum (Al), etc.

[0128] The reinforcement layer 1223 can modify the mechanical properties of the drive unit 120, for example, improving the damping and stiffness of the drive unit 120. In some embodiments, the reinforcement layer 1223 can be attached to the piezoelectric structure 1221 (e.g., the second electrode layer 12213 away from the substrate layer 1225). The piezoelectric structure 1221 can drive the reinforcement layer 1223 to vibrate. In some embodiments, the reinforcement layer 1223 can be made of semiconductor materials, polymer materials, etc. Exemplary semiconductor materials include silicon (Si), silicon oxide (SiO2), silicon nitride (SiNx), silicon carbide (SiC), etc. Exemplary polymer materials include polyimide (PI), parylene, polydimethylsiloxane (PDMS), hydrogel, photoresist, silica gel, silicone gel, silicone sealant, etc. In some embodiments, when the reinforcement layer 1223 is made of a semiconductor material, the reinforcement layer 1223 can have a single-layer or multi-layer structure. For example, the reinforcement layer 1223 may have a single-layer structure made of a semiconductor material (e.g., Si, SiO2). For another example, the reinforcement layer 1223 may have a multi-layer structure made of multiple semiconductor materials (e.g., a Si / SiO2 double-layer structure, a Si / SiNx double-layer structure, etc.). In some embodiments, the reinforcement layer 1223 may also be made of an anisotropic material. Exemplary anisotropic materials may include carbon fiber, FR4 epoxy glass fiber board, etc. In some embodiments, the reinforcement layer 1223 may also be made of a metal material. Exemplary metal materials may include stainless steel, aluminum alloy, magnesium-lithium alloy, copper, copper alloy, etc.

[0129] In some embodiments, the driving beam 122 may further include a piezoelectric seed layer (not shown in the figure), which may be disposed on a side of the piezoelectric structure 1221 away from the reinforcement layer 1223. The piezoelectric seed layer may enable the piezoelectric layer 12212 to have a better 001 crystal orientation. In some embodiments, the material of the piezoelectric seed layer may include a conductive material, such as strontium oxide (SrO), zirconium oxide (ZrO2), etc. In some embodiments, the driving beam 122 may further include a buffer layer (not shown in the figure), which may be disposed on a side of the piezoelectric structure 1221 away from the reinforcement layer 1223. For example, the buffer layer may be disposed on a side of the piezoelectric seed layer close to the reinforcement layer 1223. The buffer layer may also enable the piezoelectric layer 12212 to have a better 001 crystal orientation. In some embodiments, the material of the buffer layer may include, but is not limited to, lithium niobate (LiNbO3).

[0130] In some embodiments, the drive beam 122 may further include a substrate layer 1225 (as shown in FIG11 ). The substrate layer 1225 is disposed on a side of the piezoelectric structure 1221 away from the reinforcement layer 1223. For example, the substrate layer 1225 may be disposed on a side of the buffer layer away from the reinforcement layer 1223. The substrate layer 1225 may cooperate with the reinforcement layer 1223 to adjust the stiffness and damping of the drive unit 120, as well as the position of the neutral plane (not shown) of the drive unit 120, thereby adjusting the output performance of the drive unit 120. For example, by adjusting the thickness of the substrate layer 1225, the piezoelectric structure 1221 may be positioned entirely on one side of the neutral plane of the drive beam 122 (e.g., with the neutral plane positioned within the reinforcement layer 1223). This allows the tensile stress (or compressive stress) of the piezoelectric structure 1221 to generate greater vibration when the drive unit 120 bends. For another example, the stiffness of the drive unit 120 can be adjusted by setting the substrate layer 1225, thereby adjusting the vibration mode of the drive unit 120 and improving the output performance of the speaker 100. In some embodiments, the material of the substrate layer 1225 may include, but is not limited to, semiconductor materials. Exemplary semiconductor materials may include silicon (Si), silicon dioxide (SiO2), silicon nitride (SiNx), silicon carbide (SiC), etc. In some embodiments, the substrate layer 1225 may have a single-layer or multi-layer structure. For example, the substrate layer 1225 may have a single-layer structure made of a semiconductor material (for example, Si, SiO2). For another example, the substrate layer 1225 may have a multi-layer structure made of multiple semiconductor materials (for example, a Si / SiO2 double-layer structure, a Si / SiNx double-layer structure, etc.). In some embodiments, the substrate layer 1225 may directly use SOI (Silicon On Insulator) wafer top silicon.

[0131] In some embodiments, referring to FIG11 , when the drive beam 122 includes only one piezoelectric structure 1221, the substrate layer 1225 acts as an internal load for the drive beam 122 relative to the piezoelectric layer 12212. By properly designing the relationship between the thickness hp1 of the piezoelectric layer 12212 and the thickness hc of the substrate layer 1225, the output sound pressure level of the speaker 100 can be effectively adjusted. For example, a parameter β can be defined as the ratio of the thickness hc of the substrate layer 1225 to the thickness hp1 of the piezoelectric layer 12212. Based on the speaker frequency response curve diagrams corresponding to different values ​​of β, a suitable relationship between the thickness hp1 of the piezoelectric layer 12212 and the thickness hc of the substrate layer 1225 can be determined. For further details, see FIG13 and its accompanying description.

[0132] In some embodiments, the parameter β can be defined as the ratio of the thickness hc of the substrate layer 1225 to the thickness hp1 of the piezoelectric layer 12212:

[0133] Figure 13 illustrates frequency response curves of loudspeakers corresponding to different values ​​of β according to some embodiments of this specification. As shown in Figure 13 , curve L131 represents the frequency response curve of loudspeaker 100 when β = 0; curve L132 represents the frequency response curve of loudspeaker 100 when β = 0.25; curve L133 represents the frequency response curve of loudspeaker 100 when β = 1; curve L134 represents the frequency response curve of loudspeaker 100 when β = 2; and curve L135 represents the frequency response curve of loudspeaker 100 when β = 3. As shown in Figure 13 , when β = 2, the thickness hc of substrate layer 1225 is greater than that of piezoelectric layer 12212, thereby providing a greater internal load to piezoelectric layer 12212, restricting the movement of drive beam 122 and reducing the output of loudspeaker 100. This results in a lower overall height of curve L134. When β = 3, the thickness hc of substrate layer 1225 is greater than when β = 2, thereby providing a greater internal load on piezoelectric layer 12212 and restricting the motion of drive beam 122. This significantly reduces the output of speaker 100, and curve L135 lies entirely below curve L134. When β decreases from 2 to 1, the thickness hc of substrate layer 1225 decreases significantly relative to piezoelectric layer 12212, significantly reducing the internal load it provides on piezoelectric layer 12212 and significantly limiting the motion of drive beam 122. Consequently, the output of speaker 100 significantly increases, and corresponding curve L133 shifts upward relative to curve L134. As the value of β decreases from 1 to 0.25, the thickness hc of substrate layer 1225 decreases further relative to piezoelectric layer 12212. Consequently, the internal load it provides to piezoelectric layer 12212 decreases further, further limiting the motion of drive beam 122 and increasing the output of speaker 100. The corresponding curve L132 shifts significantly upward relative to curve L133. Furthermore, as the value of β decreases from 2 to 0.25, the resonant peak of the corresponding curve shifts gradually to the left, and the low-frequency output (e.g., 0 Hz-2000 Hz) of speaker 100 increases. When the value of β decreases to 0, the internal load provided by substrate layer 1225 is zero compared to piezoelectric layer 12212. That is, even without substrate layer 1225, the output of speaker 100 can be increased. Consequently, curve L131 shifts significantly upward relative to curves L133 and L134. In the low-frequency range (e.g., below 1000 Hz), curve L131 lies significantly below curve L132. In the mid- and high-frequency range (e.g., above 1500 Hz), curves L131 and L132 are similar. Regarding the structure of speaker 100, designing substrate layer 1225 and reinforcement layer 1223 along the thickness direction of drive beam 122 can adjust the stiffness and resonant frequency f of drive beam 122, improve reliability, adjust the neutral plane position of drive beam 122, and adjust the internal load of drive beam 122.In some embodiments, the drive beam 122 can be designed to not include the substrate layer 1225, that is, the structure corresponding to β=0. In some embodiments, in order to process the drive beam 122, the substrate layer 1225 can be used as a cutoff layer for process processing, so the design of the substrate layer 1225 can improve the yield rate (i.e., the qualified rate) of the drive beam 122. Taking all factors into consideration, in order to make the speaker 100 have a higher output in the full frequency band, the value range of β can be 0-2. In some embodiments, in order to further improve the output performance of the speaker 100, the value range of β can be 0-1.5.

[0134] In some embodiments, the structure of the driving unit 120 may also affect the driving force and displacement output by the driving unit 120 , and the resonant frequency f, thereby affecting the output performance, resonant frequency f, reliability, and manufacturing process of the speaker 100 .

[0135] 14A to 14E are schematic diagrams of driving beams with different structures according to some embodiments of this specification.

[0136] In some embodiments, as shown in FIG14A , the drive beam 122 may include two piezoelectric structures (i.e., a first piezoelectric structure 1221a and a second piezoelectric structure 1221b) and two reinforcement layers (i.e., a first reinforcement layer 1223a and a second reinforcement layer 1223b). In the thickness direction of the drive beam 122 (i.e., the z-direction, the same below), from bottom to top, the first piezoelectric structure 1221a, the second piezoelectric structure 1221b, the first reinforcement layer 1223a, and the second reinforcement layer 1223b are sequentially connected. Furthermore, two adjacent piezoelectric structures (i.e., the first piezoelectric structure 1221a and the second piezoelectric structure 1221b) may share a second electrode layer 12213 located therebetween, as shown in FIG14A . That is, from bottom to top in the thickness direction of the driving beam 122, the first electrode layer 12211, the first piezoelectric layer 12212a, the second electrode layer 12213, the second piezoelectric layer 12212b, the third electrode layer 12214, the first reinforcement layer 1223a, and the second reinforcement layer 1223b are arranged in this order. The first reinforcement layer 1223a and the second reinforcement layer 1223b can be made of the same or different materials.

[0137] In order to make the driving beam 122 have a larger displacement in the vibration direction of the vibration unit 130 (i.e., the z direction), it is possible to design the polarization direction of each piezoelectric layer (such as the first piezoelectric layer 12212a and the second piezoelectric layer 12212b) and the positive and negative applied voltage so that the deformation direction of the piezoelectric layer on one side of the neutral plane of the driving beam 122 is the same, that is, the same elongation deformation or shortening deformation; by designing the thickness of the piezoelectric layer and the reinforcement layer, the neutral plane is located inside the first reinforcement layer 1223a or the second reinforcement layer 1223b. Preferably, it can be designed so that the polarization directions of any two adjacent piezoelectric layers (such as the first piezoelectric layer 12212a and the second piezoelectric layer 12212b) are opposite (the two cases represented by the dotted arrow and the solid arrow as shown in Figure 14A), and the voltage applied to the driving beam 122 is such that the electric potential direction and the polarization direction of each piezoelectric layer (such as the first piezoelectric layer 12212a and the second piezoelectric layer 12212b) are the same; or the voltage applied to the driving beam 122 is such that the electric potential direction and the polarization direction of each piezoelectric layer (such as the first piezoelectric layer 12212a and the second piezoelectric layer 12212b) are opposite.

[0138] In some embodiments, along the thickness direction of the driving beam 122, the thickness hd1 of the first electrode layer 12211, the thickness hd2 of the second electrode layer 12213, and the thickness hd3 of the third electrode layer 12214 can be 20 nm to 200 nm. In some embodiments, according to formula (7), in order to adjust the thickness h of the driving beam 122 and the value of the design parameter α, and to adjust the stiffness of the driving beam 122, the thickness hd1 of the first electrode layer 12211, the thickness hd2 of the second electrode layer 12213, and the thickness hd3 of the third electrode layer 12214 can be 40 nm to 130 nm. The thickness hd1 of the first electrode layer 12211, the thickness hd2 of the second electrode layer 12213, and the thickness hd3 of the third electrode layer 12214 can be the same or different.

[0139] In some embodiments, the thickness hp1 of the first piezoelectric layer 12212a and the thickness hp2 of the second piezoelectric layer 12212b can be 1 μm to 5 μm. In some embodiments, according to formula (7), in order to adjust the thickness h of the drive beam 122, the value of the design parameter α is adjusted to adjust the stiffness of the drive beam 122. The thickness hp1 of the first piezoelectric layer 12212a and the thickness hp2 of the second piezoelectric layer 12212b can be 1.5 μm to 2.5 μm. The thickness hp1 of the first piezoelectric layer 12212a and the thickness hp2 of the second piezoelectric layer 12212b can be the same or different.

[0140] In some embodiments, when the reinforcing layer is made of a polymer material such as PI, PEEK, PET, PEI, silicone, or silicone gel, the thickness hj1 of the first reinforcing layer 1223a and the thickness hj2 of the second reinforcing layer 1223b can be 5 μm to 40 μm. In some embodiments, according to formula (7), in order to adjust the thickness h of the drive beam 122, the value of the design parameter α is adjusted to adjust the stiffness of the drive beam 122. When the reinforcing layer is made of a polymer material such as PI, PEEK, PET, PEI, silicone, or silicone gel, the thickness hj1 of the first reinforcing layer 1223a and the thickness hj2 of the second reinforcing layer 1223b can be 5 μm to 25 μm. The thickness hj1 of the first reinforcing layer 1223a and the thickness hj2 of the second reinforcing layer 1223b can be the same or different.

[0141] In some embodiments, when the reinforcement layer has a single-layer structure or a multi-layer structure made of a semiconductor material (e.g., Si, SiO2, SiNx, SiC, etc.), the thickness hj1 of the first reinforcement layer 1223a and the thickness hj2 of the second reinforcement layer 1223b can be 2 μm-15 μm. In some embodiments, according to formula (7), in order to adjust the thickness h of the driving beam 122, the value of the design parameter α is adjusted to adjust the stiffness of the driving beam 122. When the reinforcement layer has a single-layer structure or a multi-layer structure made of a semiconductor material (e.g., Si, SiO2, SiNx, SiC, etc.), the thickness hj1 of the first reinforcement layer 1223a and the thickness hj2 of the second reinforcement layer 1223b can be 3 μm-10 μm. The thickness hj1 of the first reinforcement layer 1223a and the thickness hj2 of the second reinforcement layer 1223b can be the same or different.

[0142] In some embodiments, by designing the structure and size of the driving beam 122 , the driving force and displacement output by the driving beam 122 can be adjusted, thereby improving the output performance of the speaker 100 .

[0143] Referring to FIG. 14B , in some embodiments, the drive beam 122 may include three piezoelectric structures (i.e., a first piezoelectric structure 1221a, a second piezoelectric structure 1221b, and a third piezoelectric structure 1221c) and two reinforcement layers (i.e., a first reinforcement layer 1223a and a second reinforcement layer 1223b). From bottom to top, along the thickness direction of the drive beam 122, the first piezoelectric structure 1221a, the second piezoelectric structure 1221b, the third piezoelectric structure 1221c, the first reinforcement layer 1223a, and the second reinforcement layer 1223b are sequentially connected. Any two adjacent piezoelectric structures may share an electrode layer located therebetween. As shown in FIG. 14B , the first piezoelectric structure 1221a and the second piezoelectric structure 1221b may share a second electrode layer 12213, while the second piezoelectric structure 1221b and the third piezoelectric structure 1221c may share a third electrode layer 12214. That is, along the thickness direction of the drive beam 122, from bottom to top, the first electrode layer 12211, the first piezoelectric layer 12212a, the second electrode layer 12213, the second piezoelectric layer 12212b, the third electrode layer 12214, the third piezoelectric layer 1221c, the fourth electrode layer 12215, the first reinforcement layer 1223a, and the second reinforcement layer 1223b are arranged in this order. The materials of the two reinforcement layers (i.e., the first reinforcement layer 1223a and the second reinforcement layer 1223b) can be the same or different. In some embodiments, a piezoelectric seed layer, a buffer layer, etc. can also be provided below the first electrode layer 12211 along the thickness direction of the drive beam 122.

[0144] Referring to FIG. 14C , in some embodiments, the driving beam 122 may include a piezoelectric structure 1221, two reinforcement layers (i.e., a first reinforcement layer 1223a and a second reinforcement layer 1223b), and a substrate layer 1225. Along the thickness direction of the driving beam 122, from bottom to top, the substrate layer 1225, the piezoelectric structure 1221, the first reinforcement layer 1223a, and the second reinforcement layer 1223b are sequentially connected. That is, along the thickness direction of the driving beam 122, from bottom to top, the substrate layer 1225, the first electrode layer 12211, the piezoelectric layer 12212, the second electrode layer 12213, the first reinforcement layer 1223a, and the second reinforcement layer 1223b are sequentially distributed. The two reinforcement layers may be made of the same or different materials. In some embodiments, a piezoelectric seed layer, a buffer layer, or the like may be disposed between the first electrode layer 12211 and the substrate layer 1225 in the thickness direction of the drive beam 122 (i.e., below the first electrode layer 12211 and above the substrate layer 1225). In some embodiments, the thickness hc of the substrate layer 1225 may be in the range of 100 nm to 5000 nm. In some embodiments, according to formula (7), to adjust the thickness h of the drive beam 122 and the value of the design parameter α, and thereby adjust the stiffness of the drive beam 122, the thickness hc of the substrate layer 1225 may be in the range of 200 nm to 2000 nm.

[0145] Referring to Figure 14D, in some embodiments, the driving beam 122 may include a piezoelectric structure 1221 and two reinforcement layers (i.e., a first reinforcement layer 1223a and a second reinforcement layer 1223b). In the thickness direction of the driving beam 122, from bottom to top, the piezoelectric structure 1221, the first reinforcement layer 1223a, and the second reinforcement layer 1223b are connected in sequence. That is, in the thickness direction of the driving beam 122, from bottom to top, the substrate layer 1225, the first electrode layer 12211, the piezoelectric layer 12212, the second electrode layer 12213, the first reinforcement layer 1223a, and the second reinforcement layer 1223b are distributed in sequence. The materials of the two reinforcement layers may be the same or different. In some embodiments, a piezoelectric seed layer, a buffer layer, etc. may also be provided below the first electrode layer 12211 in the thickness direction of the driving beam 122.

[0146] In some embodiments, the number of reinforcement layers 1223 of the driving beam 122 may be one, two, or more. As shown in FIG11 , in some embodiments, the driving beam 122 may include a piezoelectric structure 1221, a reinforcement layer 1223, and a substrate layer 1225. In the thickness direction of the driving beam 122, from bottom to top, the substrate layer 1225, the piezoelectric structure 1221, and the reinforcement layer 1223 are sequentially connected. That is, in the thickness direction of the driving beam 122, from bottom to top, the substrate layer 1225, the first electrode layer 12211, the piezoelectric layer 12212, the second electrode layer 12213, and the reinforcement layer 1223 are sequentially distributed. In some embodiments, in the thickness direction of the driving beam 122, a piezoelectric seed layer, a buffer layer, etc. may also be provided between the first electrode layer 12211 and the substrate layer 1225 (i.e., below the first electrode layer 12211 and above the substrate layer 1225). As shown in Figure 14E, in some embodiments, the drive beam 122 may include a piezoelectric structure 1221 and a reinforcement layer 1223. Along the thickness direction of the drive beam 122, from bottom to top, the piezoelectric structure 1221 and the reinforcement layer 1223 are sequentially connected. That is, along the thickness direction of the drive beam 122, from bottom to top, the substrate layer 1225, the first electrode layer 12211, the piezoelectric layer 12212, the second electrode layer 12213, and the reinforcement layer 1223 are sequentially arranged. In some embodiments, a piezoelectric seed layer, a buffer layer, etc. may also be disposed below the first electrode layer 12211 along the thickness direction of the drive beam 122.

[0147] In some embodiments, the stiffness of the drive unit 120 can be adjusted by directly increasing the thickness of the substrate layer 1225 and / or the thickness of the reinforcement layer 1223. However, increasing the thickness of the substrate layer 1225 and / or the thickness of the reinforcement layer 1223 also increases the load on the piezoelectric layer 12212, resulting in a decrease in the output of the drive unit 120. To address the above issues, in some embodiments, the drive beam 122 includes a piezoelectric structure and one or more reinforcement layers stacked along the vibration direction of the vibration unit 130 (i.e., the z-direction). The reinforcement layer farthest from the piezoelectric structure (e.g., the second reinforcement layer 1223b shown in Figures 14A to 14D) can be provided with a groove structure.

[0148] In some embodiments, in a direction extending from the fixed region 122 - 1 to the suspended region 122 - 2 , the groove structure includes a plurality of reinforcing components arranged at intervals, and a groove is provided between any two adjacent reinforcing components.

[0149] FIG15A is a schematic diagram of a partial structure of an exemplary speaker according to some embodiments of the present specification. FIG15B is a schematic diagram of the internal structure of a drive unit of the speaker in FIG15A. FIG15C is a schematic diagram of a partial structure of an exemplary speaker according to some embodiments of the present specification. FIG15D is a schematic diagram of the internal structure of the drive unit of the speaker in FIG15C.

[0150] As shown in Figures 15A and 15B, the reinforcement layer 1223 may include a plurality of reinforcement components spaced apart along the length direction of the drive beam 122 (i.e., the x-direction shown in Figure 15A). By arranging the plurality of reinforcement components spaced apart along the length direction of the drive beam 122, on the one hand, while continuing to increase the thickness of the reinforcement layer 1223 (e.g., the thickness of each reinforcement component), the distance between the neutral plane of the drive unit 120 and the geometric mid-plane of the piezoelectric layer 12212 can be increased, while keeping the load (i.e., the total mass of the substrate layer 1225 and the reinforcement layer 1223) unchanged or reduced; on the other hand, by arranging the reinforcement components spaced apart, the stiffness of the drive unit 120 can be adjusted, achieving impedance matching between the drive unit 120 and its load, thereby comprehensively improving the output performance of the drive unit 120.

[0151] In some embodiments, the plurality of reinforcing components and the spaces between adjacent reinforcing components together constitute a groove structure.

[0152] In some embodiments, the groove structure includes multiple grooves in the direction extending from the fixed area 122-1 to the suspended area 122-2 (i.e., the x direction shown in Figure 15A), and the size of the groove close to the fixed area 122-1 is larger than the size of the groove away from the fixed area 122-1, so as to reduce the constraint of the reinforcing component of the fixed area 122-1 close to the driving beam 122 on the bending deformation of the beam-like structure.

[0153] In some embodiments, referring to Figures 15A and 15B, the reinforcing component 1223-1 can be arranged as a first reinforcing component at a position of the driving beam 122 close to the fixed area 122-1, and the reinforcing component 1223-4 can be arranged as a second reinforcing component at a position of the driving beam 122 close to the suspended area 122-2. Other reinforcing components (for example, reinforcing components 1223-2, 1223-3, etc.) can be arranged between the first reinforcing component and the second reinforcing component at intervals along the extension direction of the beam-like structure of the driving beam 122. In some embodiments, the thickness of the plurality of reinforcing components in the vibration direction of the driving beam 122 can be the same or different. For example, the thickness of the plurality of reinforcing components in the vibration direction of the driving beam 122 can be the same to facilitate the preparation of the reinforcing layer 1223 (or the driving unit 120). For another example, the thickness of the plurality of reinforcing components in the vibration direction of the driving beam 122 can be different. Specifically, since the reinforcing components in the suspended area 122-2 near the driving beam 122 have less constraints on the bending deformation of the beam-like structure, while the reinforcing components located in the middle area of ​​the beam-like structure of the driving beam 122 have greater constraints on the bending deformation of the beam-like structure, the thickness of the reinforcing components in the suspended area 122-2 near the driving beam 122 can be greater than the thickness of the reinforcing components located in the middle area of ​​the beam-like structure of the driving beam 122.

[0154] In some embodiments, as shown in FIG15A , the spacing between adjacent reinforcement components forms a plurality of grooves (e.g., groove 1223-7, groove 1223-8, etc.) of the groove structure. The stiffness of the drive unit 120 can be adjusted by adjusting the size of the grooves (i.e., the size of the spacing between each two adjacent reinforcement components in the direction in which the beam-like structure of the drive beam 122 extends). In some embodiments, the size of each groove in the direction in which the beam-like structure of the drive beam 122 extends can be the same or different. For example, as shown in FIG15B , the size wj1 of the groove 1223-7 between reinforcement components 1223-1 and 1223-2 can be different from the size wj2 of the groove 1223-8 between reinforcement components 1223-3 and 1223-4.

[0155] In some embodiments, the size of the grooves near the fixed region 122-1 is larger than the size of the grooves away from the fixed region 122-1. For example, the size wj1 of the groove 1223-7 is larger than the size wj2 of the groove 1223-8.

[0156] In some embodiments of the present specification, the vibration close to the fixed area 122-1 has a greater impact on the vibration of the driving beam 122. By making the size of the groove close to the fixed area 122-1 larger than the size of the groove far from the fixed area 122-1, the vibration effect close to the fixed area 122-1 can be improved.

[0157] In some embodiments, the dimensions of the plurality of reinforcement components along the direction in which the beam-like structure of the drive beam 122 extends (the x-direction) may be the same or different. For example, as shown in FIG15D , the dimension wp1 of the reinforcement component 1223-5 along the direction in which the beam-like structure of the drive beam 122 extends (the x-direction) may differ from the dimension wp2 of the reinforcement component 1223-6 along the direction in which the beam-like structure of the drive beam 122 extends (the x-direction).

[0158] In some embodiments, different locations on the drive beam 122 contribute differently to the bending deformation. Typically, the deformation of the drive beam near the fixed region 122-1 of the driver unit 120 contributes more to the overall deformation of the drive beam than the deformation of the suspended region 122-2 of the drive beam 122. Therefore, in some embodiments, based on the actual deformation contribution of the piezoelectric layer 12212 at different locations along the beam-like structure of the drive beam 122 during operation, and in combination with the average stress distribution of the piezoelectric layer 12212 along the beam-like structure of the drive beam 122, reinforcing components of different sizes can be arranged at different locations along the beam-like structure. This effectively adjusts the position of the neutral plane of the driver unit 120 while also adjusting the load on the piezoelectric layer 12212 and the overall stiffness of the driver unit 120. This allows the driver unit 120 to output a larger displacement and achieve impedance matching or substantial impedance matching between the driver unit 120 and its load (e.g., the vibrating portion of the speaker), effectively transmitting the displacement generated by the speaker 100.

[0159] In some embodiments, the width of the reinforcement component farther from the fixing region 122-1 is greater than the width of the reinforcement component closer to the fixing region 122-1. For example, as shown in Figures 15C and 15D, the dimension wp2 of the reinforcement component 1223-6 along the direction in which the beam-like structure of the drive beam 122 extends (the x-direction) is greater than the dimension wp1 of the reinforcement component 1223-5 closer to the fixing region 122-1 along the direction in which the beam-like structure of the drive beam 122 extends (the x-direction).

[0160] In some embodiments of the present specification, the vibration close to the fixed area 122-1 has a greater impact on the vibration of the driving beam 122. By making the width of the reinforcing component away from the fixed area 122-1 greater than the width of the reinforcing component close to the fixed area 122-1, the vibration effect close to the fixed area 122-1 can be improved.

[0161] In some embodiments, to improve the output capacity of the drive unit 120 while also ensuring the reliability of the drive beam 122, multiple reinforcement components can be arranged along the extension direction of the drive beam 122, with their sizes decreasing first and then increasing. In other words, larger reinforcement components can be placed at the free end of the drive beam 122 or at the fixed region 122-1, while smaller reinforcement components can be placed in the middle of the beam structure. Specifically, by arranging a larger reinforcement component near the free end of the driving beam 122 (that is, the end of the driving beam 122 away from the fixed area 122-1), the thickness of the reinforcement component can be adjusted by the larger reinforcement component in the area with smaller strain, while reducing the constraint on the deformation of the beam-like structure of the driving beam 122; by arranging a larger reinforcement component near the fixed area 122-1, the stiffness of the beam-like structure of the driving beam 122 can be enhanced by the larger reinforcement component in the area with larger strain, so that the beam-like structure of the driving beam 122 is not easy to break during bending vibration, thereby enhancing the reliability of the beam-like structure of the driving beam 122; by arranging a smaller reinforcement component in the middle area of ​​the beam-like structure of the driving beam 122, while increasing the stiffness of the beam-like structure, the deformation constraint of the reinforcement component on the beam-like structure can be reduced as much as possible, thereby reducing the deformation resistance of the beam-like structure of the driving beam 122 and making the beam-like structure more deformable.

[0162] In some embodiments, the driving unit 120 includes two groups of driving beams located on opposite sides of the housing 110 . Each of the two groups of driving beams includes one or more driving beams. The shapes of the driving beams include rectangle, trapezoid or arc chamfer.

[0163] 16A to 16G are schematic diagrams of driving units with different structures according to some embodiments of this specification.

[0164] 10 , 16A and 16B , in some embodiments, the shape of the driving beam 122 of the driving unit 120 is designed to adjust the output performance, resonant frequency f, reliability and manufacturing process of the loudspeaker 100 .

[0165] In some embodiments, as shown in FIG10 , the drive unit 120 may include two drive beams 122, each of which has a rectangular structure. A fixed region 122-1 and a suspended region 122-2 are disposed at opposite ends of the rectangular structure. The fixed regions 122-1 of the two drive beams 122 are disposed at the two long sides of the base 126 of the rectangular ring structure. The suspended regions 122-2 of the two drive beams 122 are respectively connected to a vibration transmission unit 140 via one or more coupling elastic structures 124, and the vibration signal is transmitted to the vibration unit 130 via the vibration transmission unit 140.

[0166] In some embodiments, as shown in FIG16A , the drive unit 120 may include two drive beams 122, each of which has a trapezoidal structure. A fixed region 122-1 is located at the end of the trapezoidal structure, where the longer lower base is located, and a suspended region 122-2 is located at the end of the trapezoidal structure, where the shorter upper base is located. The fixed regions 122-1 of the two drive beams 122 are respectively located at the two long sides of the rectangular ring-shaped base 126. The suspended regions 122-2 of the two drive beams 122 are respectively connected to the vibration transmission unit 140 via one or more coupling elastic structures 124, and the vibration signal is transmitted to the vibration unit 130 via the vibration transmission unit 140. Compared to the rectangular drive beam 122 shown in FIG10 , the trapezoidal drive beam 122 shown in FIG16A can reduce stress in localized areas of the drive beam 122, thereby improving reliability. It also adjusts the stiffness of the drive beam 122, thereby affecting the output performance and resonant frequency f of the speaker 100.

[0167] In some embodiments, as shown in Figure 16B, the driving unit 120 may include two driving beams 122, and both driving beams 122 have rounded corner structures. Specifically, one end of the driving beam 122 where the suspended area is located is provided with a rounded corner with a smooth transition, as shown in Figure 16B. In some embodiments, the arc radius corresponding to the rounded corner is not greater than the length l of the suspended area 122-2. The fixed areas 122-1 of the two driving beams 122 are respectively arranged at the two long sides of the base 126 of the rectangular ring structure. The suspended areas 122-2 of the two driving beams 122 are respectively connected to the vibration transmission unit 140 through one or more coupling elastic structures 124, and the vibration signal is transmitted to the vibration unit 130 through the vibration transmission unit 140. Compared with the driving beam 122 with a trapezoidal structure shown in Figure 16A, the design of the driving beam 122 with a rounded corner structure shown in Figure 16B can further reduce the stress in the local area of ​​the driving beam 122 and improve reliability; at the same time, the stiffness of the driving beam 122 is adjusted, thereby affecting the output performance and resonant frequency f of the speaker 100.

[0168] In some embodiments, by designing the number of driving beams 122 of the driving unit 120 , the output performance, resonant frequency f, reliability, and manufacturing process of the loudspeaker 100 can also be adjusted.

[0169] In some embodiments, as shown in FIG16C , the drive unit 120 may include a plurality of rectangular (or trapezoidal, or rounded) drive beams 122. The plurality of drive beams 122 may be disposed on the two long sides of the base 126 of the rectangular ring structure, and the number of drive beams 122 disposed on the two long sides may be the same or different. The fixed regions 122-1 of each drive beam 122 are connected to the long sides of the base 126. The suspended regions 122-2 of each drive beam 122 transmit the vibration signal to the vibration unit 130 via the vibration transmission unit 140 through the corresponding coupling elastic structure 124. In some embodiments, the suspended regions 122-2 of each drive beam 122 may be connected or may be independent of each other. In some embodiments, the number of resonant frequencies of the plurality of drive beams 122 may be at least one, that is, the resonant frequencies of the plurality of drive beams 122 may all be the same, or at least one may be different, thereby increasing the number of resonant peaks of the speaker 100 and improving the output performance of the speaker 100.

[0170] In some embodiments, the driving unit 120 further includes two sets of driving beams 122 located on another opposite side of the housing 110 .

[0171] In some embodiments, as shown in FIG16D , the drive unit 120 may include four drive beams 122. Each of the four drive beams 122 has a trapezoidal structure, with a fixed region 122-1 located at the end of the longer lower base of the trapezoidal structure, and a suspended region 122-2 located at the end of the shorter upper base of the trapezoidal structure. A pair of the four drive beams 122 has its corresponding fixed regions 122-1 located at the two long sides of the rectangular ring structure's base 126. In this specification, this pair of drive beams 122 may be referred to as long-side drive beams 122A. Another pair of the four drive beams 122 has its corresponding fixed regions 122-1 located at the two short sides of the rectangular ring structure's base 126. In this specification, this pair of drive beams 122 may be referred to as short-side drive beams 122B. The suspended regions 122-2 corresponding to the four drive beams 122 are each transmission-connected to the vibration transmission unit 140 via one or more coupling elastic structures 124, transmitting the vibration signal to the vibration unit 130 via the vibration transmission unit 140. In some embodiments, the design of providing drive beams 122 on all four sides of the base 126 can reduce the tilt and roll modes of the speaker 100, thereby improving the output performance of the speaker 100. In some embodiments, by adjusting the dimensions of the long-side drive beams 122A and the short-side drive beams 122B, the driving force and displacement of the drive unit 120 can be increased, thereby increasing the output sound pressure level of the speaker 100. In some embodiments, by designing the dimensions of the long-side drive beams 122A and the short-side drive beams 122B so that the resonant frequency of the long-side drive beam 122A and the resonant frequency of the short-side drive beam 122B are in different frequency bands, the speaker 100 can have multiple resonant frequencies, increasing the frequency range covered by the speaker 100 and enhancing the output performance of the speaker 100. It should be noted that in this specification, in a pair of corresponding driving beams 122 (for example, the rectangular split driving beam shown in Figure 10, the trapezoidal split driving beam shown in Figure 16A, the rounded split driving beam shown in Figure 16B, the two long-side driving beams 122A and the two short-side driving beams 122B shown in Figure 16D, etc.), the resonant frequencies of the two driving beams 122 included therein may also be the same or different to increase the number of resonance peaks and output performance of the speaker 100.

[0172] In some embodiments, as shown in FIG16E , the drive unit 120 may include four rectangular drive beams 122 (or four structures with rounded corners, etc.). A pair of the four drive beams 122 may be disposed on the two long sides of the base 126 of the rectangular ring structure, and another pair of the four drive beams 122 may be disposed on the two short sides of the base 126 of the rectangular ring structure. In some embodiments of the present specification, the pair of drive beams 122 disposed on the long sides of the base 126 may be defined as long-side drive beams 122A, and the pair of drive beams 122 disposed on the short sides of the base 126 may be defined as short-side drive beams 122B. The fixed area 122-1 of each drive beam 122 is respectively connected to the long side of the base 126. The suspended area 122-2 of each drive beam 122 transmits the vibration signal to the vibration unit 130 through the corresponding coupling elastic structure 124 via the vibration transmission unit 140. Compared with the driving unit 120 shown in FIG. 16C , the design of providing driving beams 122 on all four sides of the base 126 shown in FIG. 16E can reduce the tilting and flipping modes of the loudspeaker 100 and further improve the output of the loudspeaker 100 .

[0173] In some embodiments, by designing the structure of the vibration transfer unit 140 , the transmission effect of force and displacement between the driving unit 120 and the vibration unit 130 can be improved, thereby enhancing the output performance of the speaker 100 .

[0174] In some embodiments, as shown in FIG16F , the vibration transmission unit 140 shown in FIG16E may include an I-shaped structure, compared to the structure of the vibration transmission unit 140 shown in FIG16F . The I-shaped structure effectively transmits the force and displacement generated by the short-side driving beam 122B to the vibration unit 130 , thereby improving the energy transfer efficiency from the driving unit 120 to the vibration unit 130 and further enhancing the output performance of the speaker 100 .

[0175] In some embodiments, by designing the coupling elastic structure 124 of the driving unit 120 , the vibration characteristics of the driving unit 120 can be adjusted, thereby affecting the vibration characteristics of the loudspeaker 100 and improving the output performance of the loudspeaker 100 .

[0176] In some embodiments, as shown in FIG16G , compared to the structure of the drive unit 120 shown in FIG16E , in the drive unit 120 shown in FIG16G , the drive beam 122 is not directly connected to the base 126. Instead, the drive beam 122 and the base 126 are indirectly connected via the coupling elastic structure 124. In this case, the suspended region 122-2 of the drive beam 122 can be the portion of the drive beam 122 between the coupling elastic structure 124 connected to the base 126 and the coupling elastic structure 124 connected to the vibration transmission unit 140. The base 126 can be considered the fixed region 122-1 of the drive beam 122. The indirect connection of the drive beam 122 to the base 126 via the coupling elastic structure 122 allows the drive beam 122 to function as a spring-mass system with its own resonant frequency, thereby affecting the overall vibration characteristics of the drive unit 120 and, in turn, adjusting the vibration characteristics of the speaker 100.

[0177] In some embodiments, the structure of the driving beam 122 and the vibration transfer unit 140 can be designed to adjust the mass and / or impedance of the driving unit 120, adjust the vibration characteristics of the driving unit 120, and thus adjust the vibration characteristics of the speaker 100 to improve the output performance of the speaker 100.

[0178] In some embodiments, the vibration transfer unit 140 includes a ring structure, and any set of driving beams 122 are connected to different areas of the vibration transfer unit 140 .

[0179] 17A to 17K are schematic diagrams of driving units with different structures according to some embodiments of this specification.

[0180] Referring to FIG. 17A , in some embodiments, compared to the structure of the drive unit 120 shown in FIG. 16D , the vibration transmission unit 140 in the drive unit 120 shown in FIG. 17A is an annular structure. The suspended region 122-2 of the drive beam 122 is directly connected to the outer side of the annular vibration transmission unit 140, thereby transmitting the force and displacement of the drive beam 122 to the vibration unit 130. By designing the structure of the vibration transmission unit 140, the force and displacement generated by the long-side drive beam 122A and the short-side drive beam 122B can be effectively transmitted to the vibration unit 130, thereby improving the driving performance of the drive unit 120 and, in turn, the output performance of the speaker 100. In some embodiments, one or more coupling elastic structures 124 can also be provided between the four drive beams 122 and the annular vibration transmission unit 140 to achieve impedance adjustment of the drive unit 120 and improve the output performance of the speaker 100.

[0181] In some embodiments, the vibration transfer unit 140 is connected to a second driving beam, and the second driving beam is indirectly connected to the housing 110 .

[0182] Referring to FIG. 17B , in some embodiments, compared to the structure of the drive unit 120 shown in FIG. 17A , the drive unit 120 shown in FIG. 17B may further include a second drive beam. The second drive beam is disposed within the ring-shaped vibration transmission unit 140 and is connected to the inner side of the ring-shaped vibration transmission unit 140. The second drive beam can also provide driving force and displacement for the vibration unit 130, thereby improving the output performance of the speaker 100. In some embodiments, the second drive beam may include two rectangular drive beams 122, each of which is connected to the two long sides of the ring-shaped vibration transmission unit 140. In some embodiments of the present specification, as shown in FIG. 17B , the two rectangular drive beams 122 connected to the two long sides of the inner side of the ring-shaped vibration transmission unit 140 may be referred to as long-side second drive beams 122C.

[0183] In some embodiments, the vibration unit further includes a mass element, and one end of the second driving beam away from the vibration transmission unit is directly connected to the mass element; or, one end of the second driving beam away from the vibration transmission unit is connected to the mass element through a coupling elastic structure.

[0184] As shown in Figure 17B , the second drive beam 122C can be connected to a mass element M2. For example, the ends of the two long-side second drive beams 122C, facing away from the vibration transmission unit 140, are each connected to a mass element M2. The mass element M2 and the long-side second drive beams 122C can form a spring-mass damping system, which can influence the vibration characteristics of the drive unit 120 and, consequently, the loudspeaker 100, thereby improving its output performance.

[0185] Referring to FIG. 17C , in some embodiments, compared to the drive unit 120 shown in FIG. 17B , the second drive beam in FIG. 17C , in addition to including two long-side second drive beams 122C, may also include two trapezoidal drive beams 122, each connected to the inner side of the short side of the ring-shaped vibration transmission unit 140. In some embodiments of the present specification, the two trapezoidal drive beams 122, each connected to the two short sides of the ring-shaped vibration transmission unit 140, may be defined as short-side second drive beams 122D, as shown in FIG. In some embodiments, the second drive beams (e.g., long-side second drive beam 122C and short-side second drive beam 122D) may provide driving force and displacement for the vibration unit 130, thereby improving the output performance of the speaker 100.

[0186] In some embodiments, the second drive beams (e.g., the long-side second drive beam 122C and the short-side second drive beam 122D) can be connected to a mass element M2 via a coupling elastic structure 124. For example, one end of each of the two long-side second drive beams 122C, which is remote from the vibration transmission unit 140, and one end of each of the two short-side second drive beams 122D, which is remote from the vibration transmission unit 140, are connected to the mass element M2 via one or more coupling elastic structures 124. The mass element M2, the coupling elastic structure 124, and the second drive beams can form a spring-mass damping system that can affect the vibration characteristics of the drive unit 120, thereby affecting the vibration characteristics of the speaker 100 and improving the output performance of the speaker 100.

[0187] In some embodiments, the vibration unit further includes a mass element, and the vibration transfer unit is connected to the mass element via a coupling elastic structure.

[0188] Referring to FIG. 17D , in some embodiments, compared to the drive unit 120 shown in FIG. 17A , in the drive unit 120 shown in FIG. 17D , the inner side of the ring-shaped vibration transmission unit 140 may be connected to a mass element M2 via a coupling elastic structure 124. The mass element M2 and the coupling elastic structure 124 may form a spring-mass damping system, which may affect the vibration characteristics of the drive unit 120, thereby affecting the vibration characteristics of the speaker 100 and improving the output performance of the speaker 100.

[0189] Referring to FIG. 17E , in some embodiments, compared to the drive unit 120 shown in FIG. 17C , in the drive unit 120 shown in FIG. 17E , the suspended regions 122-2 of the long-side drive beam 122A and the suspended regions of the short-side drive beam 122B are each connected to the outer side of the rectangular vibration transmission unit 140 via one or more coupling elastic structures 124, thereby transmitting the force and displacement generated by the long-side drive beam 122A and the short-side drive beam 122B to the vibration unit 130. By providing the coupling elastic structures 124 between the long-side drive beam 122A and the vibration transmission unit 140 and between the short-side drive beam 122B and the vibration transmission unit 140, the impedance of the drive unit 120 is adjusted, thereby improving the output performance of the speaker 100. At the same time, the mass element M2, the coupled elastic structure 124 and the second driving beam structure (for example, the long-side second driving beam 122C and the short-side second driving beam 122D) can form a spring mass damping system, which can affect the vibration characteristics of the vibration unit 130, thereby affecting the vibration characteristics of the speaker 100 and improving the output performance of the speaker 100.

[0190] Referring to FIG. 17F , in some embodiments, compared to the drive unit 120 shown in FIG. 17D , the suspended regions 122-2 of the long-side drive beam 122A and the suspended regions of the short-side drive beam 122B in FIG. 17F are each connected to the outer sides of the rectangular vibration transmission unit 140 via one or more coupling elastic structures 124. This transmits the force and displacement generated by the long-side drive beam 122A and the short-side drive beam 122B to the vibration unit 130. By providing the coupling elastic structures 124 between the long-side drive beam 122A and the vibration transmission unit 140, and between the short-side drive beam 122B and the vibration transmission unit 140, the impedance of the drive unit 120 is adjusted, thereby improving the output performance of the speaker 100. Furthermore, the mass element M2 and the coupling elastic structures 124 form a spring-mass damping system that influences the vibration characteristics of the drive unit 120, thereby affecting the vibration characteristics of the speaker 100 and improving its output performance.

[0191] It should be noted that, for one or more driving units 120 including the mass element M2 shown in the above-mentioned Figures 17A to 17F, the shape structure of the driving beams 122 (for example, the long-side driving beam 122A, the short-side driving beam 122B, the long-side second driving beam 122C, and the short-side second driving beam 122D) included therein may include but is not limited to a rectangular structure, a trapezoidal structure, a structure with rounded corners, etc., and this specification does not impose any restrictions on this.

[0192] In some embodiments, the two opposing sets of drive beams 122 may extend in a staggered manner, and the corresponding vibration transmission unit 140 may include a folded structure. Each set of drive beams 122 may be connected to a different region of the vibration transmission unit 140. In some embodiments, any drive beam 122 may be directly connected to the vibration transmission unit 140, or alternatively, any drive beam 122 may be connected to the vibration transmission unit 140 via a coupling elastic structure 124.

[0193] In some embodiments, by staggering the extension of one or more drive beams within each of the two groups of drive beams, the size of the drive beams 122 can be adjusted over a wide range, thereby adjusting the resonant frequency of the loudspeaker 100 over a wide range and improving the output performance of the loudspeaker 100. Alternatively, the multiple drive beams 122 can be individually designed so that they each have one or more resonant frequencies f, thereby adjusting the vibration mode of the loudspeaker 100. In some embodiments, each drive beam 122 can be independent of one another, allowing each drive beam 122 to independently generate deformation output driving force and displacement, thereby adjusting the vibration mode of the loudspeaker 100.

[0194] Referring to FIG. 17G , in some embodiments, the drive unit 120 may include two sets of drive beams located on opposite sides of the housing 110 . Each set of drive beams includes one or more drive beams 122 (e.g., three, five, six, etc.), with the multiple drive beams 122 spaced apart from each other. In some embodiments, the multiple drive beams 122 may be independent of each other, or at least one drive beam 122 may be connected by a structure, such as a flexible membrane covering or an elastic connection structure. In some embodiments, any two adjacent drive beams 122 are staggered (i.e., offset). For example, for any two adjacent drive beams 122, the fixed region 122-1 of one drive beam 122 is disposed on one of the long sides of the base 126, while the fixed region 122-1 of the other drive beam 122 is disposed on the other long side of the base 126. The suspended regions 122-2 of the two drive beams 122 are each connected to the vibration transmission unit 140 via one or more coupling elastic structures 124, thereby achieving an elastic connection between the drive beams 122 and the vibration transmission unit 140, thereby transmitting the force and displacement output by the drive beams 122 to the vibration unit 130. In some embodiments, because the multiple drive beams 122 are staggered relative to each other, the ends of the multiple drive beams 122 where the suspended regions 122-2 are located are also staggered. To facilitate the connection between the vibration transmission unit 140 and the drive beams 122, in some embodiments, the vibration transmission unit 140 may have a folded structure, as shown in FIG17G. Through the above arrangement, compared to the structures shown in Figures 16A to 17F, the adjustable range of the size of the drive beam 122 can be increased, allowing the length l of the suspended region 122-2 of the drive beam 122 to approach the length or width of the rectangular structure of the base 126. This allows the resonant frequency of the loudspeaker 100 to be adjusted over a correspondingly larger range, thereby improving the output performance of the loudspeaker 100. In some embodiments, each drive beam 122 and its corresponding coupling elastic structure 124 and vibration transmission unit 140 can be independently configured. Therefore, by individually designing different drive beams 122 to achieve different resonant frequencies f, the vibration mode of the loudspeaker 100 can be adjusted. Furthermore, by individually stimulating each drive beam 122, each drive beam 122 can independently generate a deformation output driving force and displacement, thereby adjusting the vibration mode of the loudspeaker 100.

[0195] Please refer to Figure 17H. In some embodiments, compared with the driving unit 120 shown in Figure 17G, in the driving unit 120 shown in Figure 17H, the suspended area 122-2 of the driving beam 122 can be directly connected to the vibration transfer unit 140, thereby improving the force and displacement transmission efficiency between the driving beam 122 and the vibration unit 130, improving the output of the vibration unit 130, and thus improving the output performance of the speaker 100.

[0196] In some embodiments, the deflection (maximum deformation) of the drive beam 122 during deformation can affect the driving force and displacement output by the drive beam 122, thereby affecting the maximum displacement of the diaphragm 131 of the vibration unit 130 during vibration, affecting the amount of air displaced by the diaphragm 131, and thus affecting the output performance of the speaker 100. The deflection of the drive beam 122 is significantly affected by the length of the drive beam 122. In some embodiments, by increasing the equivalent length of the suspended region 122-2 of the drive beam 122, the driving force and displacement output by the drive unit 120 can be increased, the vibration displacement of the diaphragm 131 of the vibration unit 130 can be increased, and the output performance of the speaker 100 can be improved.

[0197] In some embodiments, each of the two groups of drive beams 122 arranged opposite to each other includes a drive beam 122 with a bending structure, and the two drive beams 122 with a bending structure in the two groups of drive beams 122 are each coupled to the same vibration transfer unit 140 at one end away from the corresponding fixed area 122 - 1.

[0198] Referring to Figure 17I , in some embodiments, the drive unit 120 may include two drive beams 122, with fixed regions 122-1 of the two drive beams 122 respectively fixed to two opposite long sides of the base 126. In some embodiments, each drive beam 122 may be a folded structure, each drive beam 122 may include one or more folded structures, with the folded structures of the drive beam 122 extending along the long sides of the base 126. In some embodiments, a greater number of folded structures corresponds to a longer equivalent length of the suspended region 122-2 of the corresponding drive beam 122, a greater deflection of the drive beam 122 during deformation, and improved output performance of the speaker 100. For example, when the drive beam 122 includes three fold structures, since the fixed region 122-1 of the drive beam 122 is disposed on the long side of the base 126, the extension direction from the fixed region 122-1 of the drive beam 122 to the suspended region 122-2 can be perpendicular to the two long sides of the base 126 (i.e., the extension direction of the short side of the base 126). In this case, during the deformation of the drive beam 122, the portion of the drive beam 122 extending along the long side of the base 126 undergoes less deformation, while the portion of the drive beam 122 extending along the short side of the base 126 primarily deforms. That is, the equivalent length l of the drive beam 122 can be the sum of the equivalent lengths (length l1, length l2, and length l3) of the three fold structures along the short side of the base 126 shown in FIG. 17I , and the equivalent length of each fold structure is no greater than the short side of the base 126. In some embodiments, the bending structure refers to the structure on the driving beam 122 that mainly produces deformation. For example, as shown in Figure 17I, the portion of the suspended area 122-2 of the driving beam 122 along the direction of extension of the short side of the base 126 is the main deformation portion of the driving beam 122. As a bending structure, it produces bending deformation in the vibration direction of the vibration unit 130 (i.e., the direction perpendicular to the paper). The portion of the suspended area 122-2 of the driving beam 122 that extends along the long side of the base 126 mainly plays a connecting role, used to connect the three bending structures. In some embodiments, the end of the suspended area 122-2 of the driving beam 122 (i.e., the end of the driving beam 122 away from the fixed area 122-1) can be transmission-connected to the vibration transmission unit 140, and the driving force and displacement generated by the deformation of the driving beam 122 are transmitted to the vibration unit 130 through the vibration transmission unit 140.

[0199] Referring to FIG. 17J , in some embodiments, compared to the drive unit 120 shown in FIG. 17I , the suspended regions 122-2 of the two drive beams 122 in the drive unit 120 shown in FIG. 17J can be connected to the vibration transmission unit 140 via one or more coupling elastic structures 124. The provision of coupling elastic structures 124 can adjust the impedance of the drive unit 120 and improve the output performance of the speaker 100.

[0200] Referring to FIG. 17K , in some embodiments, compared to the drive unit 120 shown in FIG. 17J , in the drive unit 120 shown in FIG. 17K , the fixed regions 122-1 of the two drive beams 122 are respectively fixed to two opposite short sides of the base 126. In this case, the direction extending from the fixed regions 122-1 of the drive beams 122 to the suspended regions 122-2 can be perpendicular to the two short sides of the base 126 (i.e., the direction in which the long sides of the base 126 extend). During deformation of the drive beams 122, the portion of the drive beams 122 extending along the short sides of the base 126 experiences less deformation, while the portion of the drive beams 122 extending along the long sides of the base 126 primarily deforms. Accordingly, the equivalent length l of the drive beam 122 can be the sum of the equivalent lengths of the multiple bending structures along the long sides of the base 126 shown in FIG. 17K , with the equivalent length of each bending structure being no greater than the long side of the base 126. For example, as shown in FIG17K , the drive beam 122 may include two bending structures, and the equivalent length l of the drive beam 122 may be the sum of the equivalent lengths (length l1 and length l2) of the two bending structures in the direction extending along the long side of the base 126 in FIG17K . Compared to the drive unit 120 shown in FIG17J , the drive unit 120 shown in FIG17K has a wider design range for the equivalent length of the bending structures of the drive beam 122. Therefore, when the equivalent length of the drive beam 122 is the same, the drive beam 122 of the drive unit 120 shown in FIG17K can have fewer bending structures, thereby reducing stress concentration in the drive beam 122 and increasing the operating reliability of the drive beam 122.

[0201] It should be noted that, in some embodiments of the present specification, since the driving beam 122 is mainly deformed by the suspended area 122 - 2 , the above-mentioned equivalent length is mainly the equivalent length l of the suspended area 122 - 2 .

[0202] Figure 17L is a schematic diagram of the internal structure of the drive unit corresponding to Figure 17K , Figure 17M is a schematic diagram of the deformation of the drive beam shown in Figure 17L , and Figure 17N is a schematic diagram of the frequency response curves of the speaker shown in Figure 17L including a folded drive beam and a speaker including a non-folded drive beam. Referring to Figure 17L , Figure 17L only shows a portion of the internal structure of the drive unit 120 including a drive beam 122. In some embodiments, the drive beam 122 is provided with a first electrode covering area T1 and a second electrode covering area T2. The first electrode covering area T1 can be located at the end of the suspended area 122-2 of the drive beam 122 near the fixed area 122-1, and the second electrode covering area T2 can be located at the end of the suspended area 122-2 of the drive beam 122 near the vibration transmission unit 140. The electrode layer 12211 within the first electrode covering area T1 and the second electrode covering area T2 can be conductive. Based on the polarization direction of the corresponding piezoelectric layer 12212, the same polarity voltage is applied to the first electrode covering area T1 and the second electrode covering area T2, causing the portions of the drive beam 122 corresponding to the first electrode covering area T1 and the second electrode covering area T2 to simultaneously bend and deform in the same direction, thereby increasing the output displacement of the drive beam 122 and enhancing the output performance of the speaker 100. For example, the portion of the suspended area 122-2 of the drive beam 122 near the fixed area 122-1 and the portion of the suspended area 122-2 of the drive beam 122 near the vibration transmission unit 140 simultaneously bend upward or downward. As shown in Figure 17M, after deformation, segment A1A2 of the drive beam 122 bends upward, and segment A2A3 bends downward.

[0203] Please refer to Figure 17M, where the solid line structure represents the drive beam 122 before deformation, and the dashed line structure represents the drive beam 122 after deformation. In some embodiments, by providing a drive beam 122 with a folded structure, the bending deformation of the portion of the drive beam 122 near the fixed area 122-1 (segment A1A2) forms a vertical displacement (deflection value) y1, and the bending of the portion of the drive beam 122 near the vibration transmission unit 140 (segment A2A3) forms a vertical displacement (deflection value) y2. Ultimately, the overall vertical displacement of the drive beam 122 is y1+y2, thereby increasing the output displacement of the drive beam 122, effectively increasing the displacement of the speaker 100, and thus improving the output performance of the speaker 100.

[0204] Referring to FIG17N , broken line L1711 represents the frequency response curve of the loudspeaker 100 having a folded drive beam 122 as shown in FIG17L , while broken line L1712 represents the frequency response curve of the loudspeaker 100 having a non-folded drive beam 122. As shown in FIG17N , within the low-frequency range (e.g., 200 Hz-450 Hz) corresponding to the dotted-line box N1, broken line L1711 is clearly above broken line L1712, indicating that the loudspeaker 100 having a folded drive beam 122 exhibits a significant improvement in output within the low-frequency range (e.g., 200 Hz-450 Hz).

[0205] FIG17O is another schematic diagram of the internal structure of the driving unit corresponding to FIG17K, FIG17P is a schematic diagram of the deformation of the driving beam shown in FIG17O, and FIG17Q is a schematic diagram of the frequency response curves of the loudspeaker including the folded driving beam and the loudspeaker including the non-folded driving beam shown in FIG17O. Referring to FIG17O, in some embodiments, compared to the driving unit 120 shown in FIG17L, in FIG17O In the driving unit 120 shown, by partitioning the interior of the first electrode covering area T1, the second electrode covering area T2, and the third electrode covering area T3, the same polarity voltage is applied according to the polarization direction of the corresponding piezoelectric layer 12212, and the same polarity voltage is applied to the first electrode covering area T1 and the second electrode covering area T2, so that the parts of the driving beam 122 corresponding to the first electrode covering area T1 and the second electrode covering area T2 respectively produce the same direction of bending deformation at the same time, and opposite polarity voltages are applied to the first electrode covering area T1 and the third electrode covering area T3, so that the parts of the driving beam 122 corresponding to the first electrode covering area T1 and the third electrode covering area T3 (that is, the part of the suspended area 122-2 close to the fixed area 122-1, such as the A1A2 segment shown in Figure 17P) are second-order bending, and the part of the driving beam 122 corresponding to the second electrode covering area T2 (that is, the part of the suspended area 122-2 close to the vibration transfer unit 140, such as the A2A3 segment shown in Figure 17P) is first-order bending (the whole is bent in one direction). First-order bending refers to bending in one direction as a whole. For example, as shown in FIG17P , the A2A3 section of the deformed driving beam 122 bends upward as a whole. Second-order bending refers to bending in two directions on both sides of the lengthwise direction of the suspended region 122-2 near the fixed region 122-1. For example, as shown in FIG17P , the A1A2 section of the deformed driving beam 122 bends in two directions on both sides of its lengthwise direction (A1 and A2), with A1 bending upward and A2 bending downward.

[0206] Please refer to Figure 17P , where the solid line structure represents the drive beam 122 before deformation, and the dashed line structure represents the drive beam 122 after deformation. In some embodiments, by providing a drive beam 122 with a folded structure, the bending deformation of the portion of the drive beam 122 near the fixed area 122-1 (segment A1A2) forms a vertical displacement (deflection value) y1, and the bending of the portion of the drive beam 122 near the vibration transmission unit 140 (segment A2A3) forms a vertical displacement (deflection value) y2. Ultimately, the overall vertical displacement of the drive beam 122 is y1 + y2, thereby increasing the output displacement of the drive beam 122, effectively increasing the displacement of the speaker 100, and thus improving the output performance of the speaker 100.

[0207] Referring to FIG17Q , broken line L1721 represents the frequency response curve of the loudspeaker 100 having a folded drive beam 122 with a folded structure, as shown in FIG17O , while broken line L1722 represents the frequency response curve of the loudspeaker 100 having a non-folded drive beam 122. As shown in FIG17Q , within the low-frequency range (e.g., 200 Hz-1000 Hz) corresponding to the dotted box N2, broken line L1721 is clearly above broken line L1722, indicating that the loudspeaker 100 having a folded drive beam 122 exhibits a significant improvement in output within the low-frequency range (e.g., 200 Hz-1000 Hz).

[0208] FIG17R is another schematic diagram of the internal structure of the drive unit corresponding to FIG17K. Referring to FIG17R, in some embodiments, compared to the drive unit 120 shown in FIG17L or FIG17O, the drive unit 120 shown in FIG17R further includes a second vibration transmission unit 140'. The vibration transmission unit 140 and the second vibration transmission unit 140' are respectively arranged at both ends of the extension direction of the folded structure of the suspended area 122-2 of the drive beam 122, as shown in FIG17R. Through the provision of the second vibration transmission unit 140', the driving force and displacement generated by the vibration of the drive beam 122 can be further effectively transmitted to the vibration unit 130, thereby improving the output sound pressure level of the speaker 100; at the same time, the vibration mode of the drive beam 122 can be effectively adjusted, thereby adjusting the vibration mode of the speaker 100 and improving the output performance of the speaker 100.

[0209] Figure 17S is another structural schematic diagram of the drive unit shown in some embodiments of this specification. As shown in Figure 17S, in some embodiments, the drive unit 120 may include four drive beams 122, and the four drive beams 122 may all be rectangular structures. Two of the four drive beams 122 can be spaced apart on one of the short sides of the base 126, and the other two can be spaced apart on the other short side of the base 126. The four drive beams 122 can be connected to the vibration transmission unit 140 through one or more coupling elastic structures 124, respectively, so that the force and displacement output by the drive beam 122 are transmitted to the vibration unit 130. In some embodiments, the extension direction of the four drive beams 122 (i.e., the direction from the fixed area 122-1 to the suspended area 122-2) is parallel to the long side direction of the base 126. Through the above arrangement, the size adjustment range of the drive beam 122 is large, so that the resonant frequency of the speaker 100 can be adjusted accordingly within a large range, thereby improving the output performance of the speaker 100. At the same time, compared with the folded structure, the driving beam 122 with a rectangular structure can effectively reduce the possibility of stress concentration in the driving beam 122 and improve the working reliability of the driving beam 122.

[0210] Figure 17T is another structural diagram of the drive unit shown in some embodiments of this specification. Referring to Figure 17T, in some embodiments, the speaker 100 may include multiple (for example, 2, 3, 4 or more) drive units 120, and each drive unit 120 may respectively include a corresponding drive beam 122, a coupling elastic structure 124, and a vibration transfer unit 140. In some embodiments, the multiple drive units 120 can be interconnected, for example, the multiple drive units 120 can be connected through their respective corresponding bases 126. In some embodiments, at least one of the multiple drive units 120 can also be provided separately and not connected to the other drive units 120. In some embodiments, the multiple drive units 120 can be distributed in any shape, such as a straight line, a rectangle, a T-shape, etc., and this specification does not impose too many restrictions on this. In some embodiments, the multiple drive units 120 operate independently of each other and do not affect each other. Through the above settings, different drive units 120 can be designed separately so that multiple drive units 120 can have different resonant frequencies. At the same time, each drive unit 120 can be excited separately to achieve the adjustment of the vibration mode of the speaker 100 and improve the output performance of the speaker 100.

[0211] In some embodiments, any one of the driving beams 122 can be connected to the vibration transfer unit 140 via the coupling elastic structure 124 .

[0212] In some embodiments, the driving beam 122 includes a piezoelectric structure 1221 and one or more reinforcement layers 1223 stacked along the vibration direction (ie, z direction) of the vibration unit 130 , and the reinforcement layer 1223 farthest from the piezoelectric structure 1221 is connected to the coupling elastic structure 124 .

[0213] 18A and 18B are schematic diagrams of the internal structure of driving units with different structures according to some embodiments of this specification.

[0214] 18A , in some embodiments, in the vibration direction of the vibration unit 130, the driving beam 122 includes a piezoelectric structure 1221 and a reinforcement layer 1223 connected to each other. The reinforcement layer 1223 is connected to the coupling elastic structure 124. The piezoelectric structure 1221 can respond to an electrical signal to cause the driving unit 120 to output vibrations from the suspended region 122-2. In the direction extending from the fixed region 122-1 to the suspended region 122-2, the piezoelectric structure 1221 can partially or completely cover the suspended region 122.

[0215] The piezoelectric structure 1221 can deform under the action of a driving voltage, thereby generating vibration. In some embodiments, the piezoelectric structure 1221 can include two electrode layers (e.g., a first electrode layer 12211 and a second electrode layer 12213) and a piezoelectric layer 12212, with the two electrode layers being located on opposite sides of the piezoelectric layer 12212, as shown in FIG18A . For more information about the structure of the drive beam 122, please refer to FIG11 , FIG14A through FIG14E , and the related descriptions, which will not be repeated here.

[0216] The difference between the driving beam 122 shown in Figure 18B and the driving beam 122 shown in Figure 18A is that the driving beam 122 shown in Figure 18B includes two reinforcement layers (i.e., the first reinforcement layer 1223a and the second reinforcement layer 1223b), and the reinforcement layer 1223B farthest from the piezoelectric structure 1221 is connected to the coupling elastic structure 124.

[0217] In some embodiments, the force and displacement generated by the piezoelectric layer 12212 itself are determined by the size of the drive beam 122 and the material of the piezoelectric layer 12212. Once the size of the drive beam 122 and the material of the piezoelectric layer 12212 are determined, the greater the distance between the piezoelectric layer 12212 and the neutral plane of the drive unit 120, the greater the deformation of the drive beam 122 (or drive unit 120).

[0218] In some embodiments, in the vibration direction of the vibration unit 130 , a ratio of the thickness of the coupling elastic structure 124 to the thickness of the driving beam 122 is 0.65-1.

[0219] In some embodiments, the parameter κ may be defined as the ratio of the thickness h0 of the coupling elastic structure 124 to the thickness h of the driving beam 122 in the vibration direction of the vibration unit 130 (ie, the z direction):

[0220] When κ is small, the impedance of the coupling elastic structure 124 itself is too small; when κ is large, the impedance of the coupling elastic structure 124 itself is too large.

[0221] FIG18C is a diagram illustrating frequency response curves of a speaker corresponding to different values ​​of κ according to some embodiments of this specification. As shown in FIG18C , curve L181 represents the frequency response curve of speaker 100 when κ = 0.55; curve L182 represents the frequency response curve of speaker 100 when κ = 0.65; curve L183 represents the frequency response curve of speaker 100 when κ = 0.82; curve L184 represents the frequency response curve of speaker 100 when κ = 0.88; curve L185 represents the frequency response curve of speaker 100 when κ = 0.9; and curve L186 represents the frequency response curve of speaker 100 when κ = 1.

[0222] As can be seen from Figure 18C, as the value of κ gradually increases from 0.55 to 1, the corresponding curve gradually shifts upward as a whole, and the output sound pressure level of the speaker 100 in the frequency range between the two resonance peaks gradually increases. When the parameter κ is too small, for example, when κ = 0.55, the output sound pressure level of the speaker 100 in most frequency ranges is significantly reduced compared to when κ = 0.65, which is not conducive to the application of the speaker 100. When κ = 1, although the increase in the frequency of the first resonance peak will cause the output sound pressure in the frequency range before it to decrease, the SPL in the mid- and high-frequency bands increases, which has an advantage in improving the sound effect in the mid- and high-frequency bands. In some embodiments, in order to make the speaker 100 have a larger output sound pressure level in the range of 500Hz-20kHz, the value range of κ can be 0.65-1. In some embodiments, in order to make the speaker 100 have a larger output sound pressure level in the range of 800Hz-20kHz and have a relatively flat sound pressure curve, the value range of κ can be 0.82-1. In some embodiments, to ensure that the speaker 100 has a high output sound pressure level and a relatively flat sound pressure curve in the range of 1 kHz-20 kHz, the value of κ may be in the range of 0.88-1. In some embodiments, to ensure that the speaker 100 has a high output sound pressure level and a relatively flat sound pressure curve in the range of 1.5 kHz-20 kHz, the value of κ may be in the range of 0.9-1.

[0223] In some embodiments, the stiffness of the coupling elastic structure 124 can be adjusted by changing the structure of the coupling elastic structure 124. For example, as shown in FIG10 , in some embodiments, the coupling elastic structure 124 can include a strip-shaped structure, and the base 126, the driving beam 122, the coupling elastic structure 124, and the vibration transmission unit 140 can form a continuous sheet structure, thereby efficiently transmitting the force and displacement of the driving beam 122 to the vibration unit 130.

[0224] In some embodiments, a hollow structure may be provided on the coupling elastic structure 124 to adjust the stiffness of the coupling elastic structure 124 .

[0225] Figures 19A and 19B are schematic diagrams of drive units of different structures according to some embodiments of this specification. Referring to Figure 19A, in some embodiments, compared to the drive unit 120 shown in Figure 10, in the drive unit 120 shown in Figure 19A, a hollow structure may be provided on the coupling elastic structure 124 of the strip structure. Through the design of the hollow structure, the stiffness of the coupling elastic structure 124 can be effectively adjusted, thereby achieving the matching of the impedance of the coupling elastic structure 124 with the impedance of the drive beam 122 and the impedance of the vibration unit 130. In some embodiments, the hollow structure may include a circle (as shown in Figure 19A), a triangle, a quadrilateral or other polygon, and other arbitrary shapes, and this specification does not impose too many restrictions on this.

[0226] In some embodiments, the coupling elastic structure 124 includes a bending structure to adjust the stiffness of the coupling elastic structure 124 .

[0227] Referring to FIG. 19B , in some embodiments, the coupling elastic structure 124 may include a folded structure. In some embodiments, the folded coupling elastic structure 124 may include at least one bend. This folded structure design allows the coupling elastic structure 124 to have greater flexibility within a smaller space, thereby enabling the impedance of the coupling elastic structure 124 to match the impedance of the drive beam 122 and the impedance of the vibration unit 130 over a wide range.

[0228] In some embodiments, the speaker 100 may not include the vibration transfer unit 140. In this case, the drive unit 120 may be directly connected to the vibration unit 130. In some embodiments, any one of the drive beams 122 is stacked in different areas of the vibration unit 130. For example, as shown in FIG1B , the drive unit 120 may include a drive beam 122, and the vibration unit 130 may include a diaphragm 131. The diaphragm 131 may not include the central reinforcement 132 shown in FIG1A . One end of the drive beam 122 (the end close to the fixed area 122-1) is fixedly connected to the shell 110, and the other end (the end close to the suspended area 122-2) is suspended. The diaphragm 131 can be directly covered on the drive beam 122, and the diaphragm 131 can vibrate with the vibration of the drive beam 122, thereby pushing the air in the front cavity 111 and generating sound. In some embodiments, the diaphragm 131 can partially or completely cover the drive beam 122. For example, as shown in FIG1B , the diaphragm 131 may completely cover the driving beam 122, and form a vibration suspension region 1314 at the gap formed by the driving beam 122. For another example, to further reduce the load on the driving beam 122, the diaphragm 131 may only cover an area within half the length of the driving beam 122 near the free end of the driving beam 122 (i.e., the end near the suspension region 122-2), while also covering the gap formed by the driving beam 122 to form the vibration suspension region 1314 at the gap.

[0229] Compared to the speaker shown in FIG1A , the speaker shown in FIG1B lacks loads such as the vibration transmission unit 140 and the central reinforcement member 132. Therefore, with the same drive unit structure, a greater proportion of the driving force can be used to push the air load to produce the sound signal, thereby increasing the output SPL of the speaker 100. Furthermore, omitting the vibration transmission unit 140 and the central reinforcement member 132 significantly reduces the overall thickness of the speaker 100, which is of great significance for micro speakers.

[0230] Figure 20A is a first view of the speaker shown in Figure 1B of this specification. Figure 20B is a cross-sectional view of the speaker shown in Figure 20A. Figure 20C is a second view of the speaker shown in Figure 1B of this specification. Figure 20D is a cross-sectional view of the speaker shown in Figure 20C.

[0231] Referring to FIG. 1B and FIG. 20A to 20D , the vibration unit 130 can be connected to the driving beam 122 and cover the gap formed by the driving beam 122 to separate the acoustic cavity into a front cavity 111 and a rear cavity 112 located on opposite sides of the vibration unit 130. The vibration unit 130 can be used to receive the deformation or displacement of the driving beam 122 and generate vibration that is transmitted outward. Due to the non-redundant structural design between the vibration unit 130 and the driving beam 122, the vibration unit 130 directly responds to the deformation or displacement of the driving beam 122 to generate vibration. Therefore, based on the same driving unit 120, compared with an additional vibration transmission unit provided between the driving beam 122 and the vibration unit 130, the speaker 100 in this embodiment can use a larger proportion of the vibration driving force to generate sound signals, thereby improving the output sound pressure level and significantly reducing the overall thickness of the speaker 100, which has significant inspiration for the design and development of micro speakers 100.

[0232] In some embodiments, the vibration unit 130 may include a diaphragm 131, which is connected to the drive beam 122 and covers the vacant area between the drive beam 122 and the base 126 or the housing 110. The diaphragm 131 directly responds to the deformation or displacement of the drive beam 122 to generate vibrations, and can use a larger proportion of the vibration driving force to push the air in the acoustic cavity to generate fluctuations, i.e., sound waves (sound signals). The sound waves can be transmitted outward through holes connecting the acoustic cavity to the outside (e.g., sound outlet holes provided in the housing 110, or openings in the base 126). In some embodiments, the diaphragm 131 may be a flexible thin film structure. In some embodiments, the material of the diaphragm 131 may include but is not limited to one or more of polyimide (PI), polyethylene terephthalate (PET), polyethyleneimine (PEI), polyetheretherketone (PEEK), silicone, polycarbonate (PC), vinyl polymer (PVC), acrylonitrile-butadiene-styrene copolymer (ABS), polyethylene (PE), polyparaxylene (PPX), etc., or it may be a multilayer composite material composed of the above materials.

[0233] In some embodiments, as shown in FIG1B and FIG20A to FIG20D , the side of the diaphragm 131 near the rear cavity 112 is connected to the side of the drive beam 122 near the front cavity 111. At this time, the diaphragm 131 pushes the air in the front cavity 111 to generate sound waves, and the sound waves can be transmitted outward through the hole connecting the front cavity 111 to the outside. In other embodiments, the side of the diaphragm 131 near the front cavity 111 is connected to the side of the drive beam 122 near the rear cavity 112. The diaphragm 131 pushes the air in the rear cavity 112 to generate sound waves, and the sound waves can be transmitted outward through the hole connecting the rear cavity 112 to the outside. In some embodiments, as shown in FIG20A to FIG20D , the drive beam 122 is disposed on the side of the diaphragm 131 located in the rear cavity 112, or the drive beam 122 is disposed on the side of the diaphragm 131 located in the front cavity 111. The diaphragm 131 pushes the air in the rear cavity 112 to generate sound waves, and the sound waves can be transmitted outward through the hole connecting the rear cavity 112 to the outside. In yet other embodiments, as shown in FIG1B and FIG20A-20D , the diaphragm 131 is connected to the drive beam 122 while its peripheral side is connected to the inner wall of the housing 110 or the base 126. In some embodiments, the diaphragm 131 can also be connected to the drive beam 122 by connecting its peripheral side to the side surface of the drive beam 122 near its free end. In some embodiments, the diaphragm 131 is provided on both sides of the drive beam 122 near the front cavity 111 and the rear cavity 112. In this case, the diaphragms 131 on both sides can respectively push the air in the front cavity 111 and the rear cavity 112 to generate sound waves, which can be transmitted outward through the holes connecting the front cavity 111 and the rear cavity 112 to the outside.

[0234] Figure 20E is a schematic structural diagram of a loudspeaker according to some embodiments of the present specification. Figure 20F is a cross-sectional view of the loudspeaker shown in Figure 20E.

[0235] The loudspeaker 100 shown in Figures 20E to 20F is similar to the loudspeaker 100 shown in Figure 1B and Figures 20A to 20D, except that the loudspeaker 100 further includes a mass element M2. As shown in Figures 20E to 20F, the mass element M2 is a rectangular parallelepiped structure. The mass element M2 is connected to the side of the diaphragm 131 close to the front cavity 111, and the mass element M2 is located in the central area of ​​the diaphragm 131, so that when the diaphragm 131 carries the mass element M2, the force and vibration state of the diaphragm 131 are balanced. In some embodiments, the mass element M2 can also be offset from the central area of ​​the diaphragm 131. In some embodiments, in order to ensure the flexibility and vibration displacement of the diaphragm 131, the mass element M2 is not connected to other components (such as the housing 110).

[0236] Figure 20G is a schematic diagram of the structure of a speaker according to some other embodiments of this specification. Figure 20H is a cross-sectional view of the speaker shown in Figure 20G.

[0237] The loudspeaker 100 shown in Figures 20G to 20H is similar to the loudspeaker 100 shown in Figures 20E to 20F, except that the mass element M2 is connected to the side of the diaphragm 131 near the rear cavity 112. In some embodiments, to ensure the flexibility and vibration displacement of the diaphragm 131, the mass element M2 is not connected to other components (such as the drive beam 122). In some embodiments, a second diaphragm 131 may be provided on the side of the drive beam 122 near the rear cavity 112. The second diaphragm 131 is provided in a manner similar to that of the diaphragm 131. For example, the side of the second diaphragm 131 near the front cavity 111 is connected to the side of the drive beam 122 near the rear cavity 112. In this case, the side of the mass element M2 near the front cavity 111 is connected to the diaphragm 131, and the side near the rear cavity 112 is connected to the second diaphragm 131. In this way, the sound waves of the loudspeaker 100 can be output through both the front cavity 111 and the rear cavity 112. In some embodiments, the second diaphragm 131 may also be arranged in the rear cavity 112. For example, the second diaphragm 131 is connected to the shell 110 (or the base 126) through its peripheral side or edge area. At this time, the mass element M2 is arranged to protrude from the driving beam 122, and its side close to the front cavity 111 is connected to the diaphragm 131, and its side close to the rear cavity 112 is connected to the second diaphragm 131.

[0238] Figure 20I is a schematic structural diagram of a speaker according to some other embodiments of the present disclosure. Figure 20J is a cross-sectional view of the speaker shown in Figure 20I.

[0239] The loudspeaker 100 shown in Figures 20I to 20J is similar to the loudspeaker 100 shown in Figures 20G to 20H , except that a mass element M2 is connected to both the side of the diaphragm 131 closest to the front cavity 111 and the side of the rear cavity 112. In some embodiments, when the diaphragm 131 is located on the side of the drive beam 122 closest to the front cavity 111, the second diaphragm 131 can be connected to the mass element M2 located within the rear cavity 112; when the diaphragm 131 is located on the side of the drive beam 122 closest to the rear cavity 112, the second diaphragm 131 can be connected to the mass element M2 located within the front cavity 111. For more information about the drive beam 122, the mass element M2, the diaphragm 131, etc., please refer to the relevant sections above, such as Figures 1A to 17K.

[0240] In some embodiments, the driving unit 120 includes two groups of driving beams 122 located on opposite sides of the housing 110 . Each of the two groups of driving beams 122 includes one or more driving beams 122 . The shapes of the driving beams 122 include rectangle, trapezoid or arc chamfer.

[0241] FIG21A is a projection diagram of the driving beam along the vibration direction of the vibration unit 130 according to some embodiments of the present disclosure, wherein the vibration direction of the vibration unit 130 refers to the z direction in FIG10 , FIG11 , etc.

[0242] In some embodiments, as shown in FIG. 21A , the driving beam 122 includes a fixed region 122 - 1 and a suspended region 122 - 2 .

[0243] In some embodiments, each set of drive beams 122 includes one or more drive beams 122 .

[0244] 21B to 21M are projection diagrams of the driving beam and the diaphragm along the vibration direction of the vibration unit shown in some embodiments of this specification.

[0245] As shown in FIG21B , a plurality of drive beams 122 are spaced apart on both sides of the base 126 extending in the y direction. The plurality of drive beams 122 on both sides are correspondingly arranged. The fixed end of the drive beam 122 (the end close to the fixed area 122-1) is connected to the base 126, and the diaphragm 131 covers each drive beam. In some embodiments, the width of the plurality of drive beams distributed in the y direction is consistent with the width of the acoustic cavity in the y direction. In some embodiments, the drive beams 122 can be connected to each other by the above-mentioned coupling elastic structure 124, or can be arranged independently of each other. In some embodiments, the resonant frequencies of the plurality of drive beams 122 can be the same, or the resonant frequency of at least one of the plurality of drive beams 122 can be different. In some embodiments, the different resonant frequencies of the plurality of drive beams 122 can be achieved by adjusting their dimensions. For example, the free ends of the plurality of drive beams 122 (the end close to the suspended area 122-2) are not on the same straight line along the y direction.

[0246] In some embodiments, the driving unit 120 further includes two sets of driving beams 122 located on another opposite side of the housing 110 .

[0247] As shown in FIG21C , two driving beams 122, positioned opposite each other along the x-direction, are identical. The suspended regions 122-2 of each driving beam 122 are trapezoidal in shape, with their longer sides along the y-direction positioned adjacent to the fixed regions 122-1 of the driving beam 122. The diaphragm 131 covers the trapezoidal driving beam 122, and the diaphragm 131 is fixedly connected to the base 126 (or housing 110) of the loudspeaker 100 on all sides. In some embodiments, to reduce stress concentration on the driving beam 122, the corners of the trapezoidal driving beam 122 at its free end (the end adjacent to the suspended region 122-2) can be rounded (not shown in FIG21C ).

[0248] The driving beam 122 in FIG21D is similar to the driving beam 122 shown in FIG21C , except that the base 126 is further provided with driving beams 122 on both sides of the y-direction. The driving beams 122 on both sides of the y-direction are defined as short-side driving beams 122. The short-side driving beams 122 can be triangular beams. The driving beams 122 are provided on all four sides of the base 126. The structural balance can reduce the tilt and flip modes of the loudspeaker 100. In some embodiments, the short-side driving beams 122 can be trapezoidal beams or beams of other shapes. In some embodiments, the driving beams 122 on both sides of the x-direction are defined as long-side driving beams 122. By adjusting the dimensions of the long-side driving beams 122 and the short-side driving beams 122, the driving force of the driving beams 122 can be increased, thereby increasing the output sound pressure level of the loudspeaker 100. In some embodiments, the dimensions of the long-side drive beam 122 and the short-side drive beam 122 can be adjusted to allow their resonant frequencies to fall within different frequency ranges. This means that the long-side drive beam 122 and the short-side drive beam 122 have different resonant frequencies, thereby enabling the speaker 100 to have multiple resonant frequencies. In some embodiments, the dimensions of the long-side drive beam 122 or the short-side drive beam 122 can also be designed to allow their resonant frequencies to fall within different frequency ranges. This means that the two long-side drive beams 122 or the two short-side drive beams 122 have different resonant frequencies. This allows the speaker 100 to generate more resonant peaks and improve the sound pressure level output. This is also applicable to drive beams 122 with other shapes and structures.

[0249] In some embodiments, the vibration unit 130 further includes a mass element M2 , and any set of driving beams 122 are connected to different regions of the mass element M2 .

[0250] As shown in FIG21E , the driving beam 122 in FIG21E is similar to the driving beam 122 in FIG21D , except that the loudspeaker 100 further includes a mass element M2 . The mass element M2 is connected to the center region of the diaphragm 131 and is located between the two driving beams 122 that are opposite each other along the x-direction.

[0251] The drive beam 122 in FIG21F is similar to the drive beam 122 in FIG21E , except that the corner at the free end of the drive beam 122 is rounded. Compared to the drive beam 122 in FIG21D , the rounded corner at the free end can reduce stress in a localized area of ​​the drive beam 122 and improve reliability. In some embodiments, the radius of the rounded corner does not exceed the length dimension l of the overhanging region 122-2 of the drive beam 122.

[0252] In some embodiments, the mass element M2 comprises a ring structure.

[0253] The drive beam 122 in Figure 21G is similar to the drive beam 122 in Figure 21D , except that the loudspeaker 100 further includes a mass element M2, which has a ring-shaped structure. This ring-shaped mass element M2 is connected to the center of the diaphragm 131 and is positioned between the long-side drive beam 122 and the short-side drive beam 122. This ring-shaped mass element M2 ensures that the drive beams 122 on all four sides of the base 126 have a certain mass distribution.

[0254] In some embodiments, the vibration unit 130 further includes a second driving beam 122E, which is indirectly connected to the housing 110 .

[0255] In some embodiments, the vibration unit 130 further includes a mass element M2 , and the second driving beam 122E is connected to the mass element M2 .

[0256] The drive beam 122 in FIG21H is similar to the drive beam 122 shown in FIG21D , except that the speaker 100 further includes a second drive beam 122E and a mass element M2, with the mass element M2 being connected to the center region of the diaphragm 131. In some embodiments, the second drive beam 122E is located within the acoustic cavity and can be connected to the base 126 of the speaker 100, enabling the speaker 100 to generate more resonance peaks and improve the sound pressure level output. In some embodiments, the second drive beam 122E can be connected to the diaphragm 131. In some embodiments, the second drive beam 122E is connected to the center region of the diaphragm 131. In some embodiments, the mass element M2 can be connected to the second drive beam 122E. In some embodiments, the second drive beam 122E and the mass element M2 are respectively connected to opposite sides of the diaphragm 131, with the two sides of the diaphragm 131 being located within the front cavity 111 and the rear cavity 112, respectively.

[0257] In some embodiments, the speaker 100 may include multiple drive units 120. The multiple drive units 120 may be arranged in parallel as shown in FIG21I . The drive units 120 include a base 126 and a drive beam 122, with the base 126 being connected to the drive beam 122 on all four sides. The arrangement of the multiple drive units 120 is not limited to the parallel arrangement shown in FIG21I , and may also be arranged in a regular or irregular manner, such as an array, a diagonal line, a ring, or a fan.

[0258] In some embodiments, as shown in FIG21I , the drive unit 120 further includes a second drive beam 122E. This second drive beam 122E is connected to the drive beams 122 surrounding the base 126 via a coupling elastic structure 124. The arrangement of multiple drive beams 122 and second drive beams 122E enables the speaker 100 to generate more resonance peaks, thereby improving the sound pressure level output. For more information on the coupling elastic structure 124, see FIG7 through FIG10 and the related descriptions.

[0259] In some embodiments, the two oppositely disposed groups of driving beams 122 may be staggered and extended.

[0260] The drive beam 122 in FIG21J is similar to the drive beam 122 shown in FIG21B , except that the multiple drive beams 122 are staggered on both sides of the base 126 along the y-direction. Specifically, the free ends of the drive beams 122 (the ends proximal to the suspended region 122-2) extend toward the opposite side of the base 126. This arrangement allows the length of the drive beams 122 to be adjusted over a wide range, while maintaining a constant length along the x-direction of the loudspeaker 100, thereby adjusting the resonant frequency of the loudspeaker 100 over a wider range. Furthermore, different resonant frequencies can be achieved by individually designing each drive beam 122, and the modal state of the diaphragm 131 of the loudspeaker 100 can be adjusted by individually exciting each drive beam 122. This mechanism of individually exciting each drive beam 122 is also applicable to other embodiments including multiple independent drive beams 122, such as those shown in FIG21B and FIG21D .

[0261] In some embodiments, each set of driving beams 122 may include a driving beam 122 having a bent structure.

[0262] As shown in FIG21K , two drive beams 122 are disposed on either side of the base 126 along the y-direction. The drive beams 122 are shaped with multiple bends. Their fixed ends (the ends near the fixed region 122-1) are connected to the long side of the base 126 and are disposed near the short side of the base 126 (extending along the x-direction). Their free ends (the ends near the suspended region 122-2) extend in the y-direction, and the free ends of the two drive beams 122 are close to each other. The length of the drive beams 122 along the x-direction is slightly less than the length of the acoustic cavity along the x-direction, and the diaphragm 131 covers the two drive beams 122. This design can increase the length of the drive beams 122 within a limited acoustic cavity. In some embodiments, different sections on the drive beam 122 can be excited with separate voltages to achieve modal adjustment of different regions on the diaphragm 131.

[0263] As shown in Figure 21L , two drive beams 122 are disposed on either side of the base 126 along the x-direction. The drive beams 122 have multiple bends, with their fixed ends connected to the short sides of the base 126 and positioned close to the long sides. Their free ends extend in the x-direction, and the free ends of the two drive beams 122 are close together. The width of the drive beams 122 along the y-direction is slightly smaller than the width of the acoustic cavity along the y-direction. The diaphragm 131 covers both drive beams 122. This design effectively increases the vibration displacement of the drive beams 122, thereby effectively increasing the amplitude of the diaphragm 131 and thereby improving the output sound pressure level. Specifically, taking the first beam 531 and second beam 532 of one of the drive beams 122 as an example, the first beam 531 is connected to the base 126. Both the first beam 531 and the second beam 532 are arranged along the y-direction and connected by another beam.

[0264] In some embodiments, different driving beams 122 may be connected via a coupling elastic structure 124 .

[0265] The drive beam 122 shown in FIG. 21M is similar to the drive beam 122 shown in FIG. 21C , except that the two drive beams 122, disposed opposite each other along the x-direction, are elastically connected by a coupling elastic structure 124. In some embodiments, the two drive beams 122 may be connected by one or more coupling elastic structures 124. In some embodiments, the multiple coupling elastic structures 124 between the two drive beams 122 may be evenly spaced. In some embodiments, the coupling elastic structures 124 may have regular shapes, such as zigzags, rectangles, trapezoids, and other polygonal shapes, as well as irregular shapes. In some embodiments, the thickness of the coupling elastic structure 124 along the z-direction (i.e., the vibration direction of the vibration unit 130) may be equal to the total thickness of the layers of the drive beam 122. In some embodiments, the material and material distribution of the coupling elastic structure 124 are consistent with the material and material distribution of the layers of the drive beam 122. In some embodiments, the thickness of the coupling elastic structure 124 may also be the thickness of at least one of the layers of the drive beam 122. In some embodiments, the material and material distribution of the coupling elastic structure 124 may also be the material and material distribution of at least one of the layers of the drive beam 122. In some embodiments, the thickness of the coupling elastic structure 124 may be inconsistent with the total thickness of the driving beam 122 . In some embodiments, the material of the coupling elastic structure 124 may be a material with a certain elasticity other than the materials of the various layers of the driving beam 122 .

[0266] In some embodiments, the vibration unit 130 includes a hollow area not covered by the driving beam 122, and the suspended area 122-2 has a length dimension in a direction extending from the fixed area 122-1 to the suspended area 122-2. The sum of the length of the driving beam 122 and half the length of the hollow area is defined as a first parameter, and the ratio of the length dimension of the suspended area 122-2 to the first parameter is 0.7-1.

[0267] FIG22 is a projection diagram of a driving beam and a diaphragm along the z direction shown in some other embodiments of this specification.

[0268] As shown in FIG22 , the edge area of ​​the driving beam 122 near its peripheral side along the length direction x is a fixed area 122-1 connected to the shell 110 (or base 126), the area of ​​the driving beam 122 suspended in the acoustic cavity is a suspended area 122-2, and the area between the suspended area 122-2 and the shell 110 (or base 126) is a vacant area. The movement of the suspended area 122-2 of the driving beam 122 provides driving force for the loudspeaker 100. In some embodiments, the long side of the driving beam 122 is a fixed side, and the short side is a suspended side. The long side of the driving beam 122 extends along the width direction y of the driving beam 122 (see FIG22 ), and the short side extends along the length direction x of the driving beam 122 (see FIG22 ).

[0269] In some embodiments, referring again to FIG22 , a portion of the vibration area of ​​the diaphragm 131 is covered by the driving beam 122, while another portion is uncovered by the driving beam 122. The portion of the vibration area of ​​the diaphragm 131 uncovered by the driving beam 122 is defined as a hollow area 131-1. The size of the hollow area 131-1 can affect the vibration mode of the diaphragm 131. Along the x-direction, the sum of the length of the driving beam 122 and half the length of the hollow area 131-1 is defined as a first parameter lt. Since the two driving beams 122 spaced apart along the x-direction of the loudspeaker 100 are symmetrically arranged, lt is marked in FIG22 as the distance between the long side of the driving beam 122 near the fixed area 122-1 and the symmetry line of the loudspeaker 100 parallel to the y-direction. The relationship between the length l of the suspended area 122-2 of the driving beam 122 and lt determines the length dimension ratio of the diaphragm 131. The width of the hollow area 131 - 1 of the diaphragm 131 along the y direction is defined as wt , and the relationship between the width w of the driving beam 122 and wt determines the width size ratio of the hollow area 131 - 1 of the diaphragm. When the length dimension ratio and / or width dimension ratio of the hollow area 131-1 of the diaphragm are large, for example, when the ratio of l to lt and / or the ratio of w to wt are small, the hollow area 131-1 of the diaphragm 131 is large, which causes the hollow area 131-1 to generate local modes at lower frequencies, which are inconsistent with the modes of the driving beam 122, and even modes in opposite directions, which will cause the audio response to have more peaks and valleys, and the output sound pressure level to be low; when the length dimension ratio and width dimension ratio of the hollow area 131-1 are small, for example, when the ratio of l to lt and the ratio of w to wt are large, the diaphragm 131 covers a larger area of ​​the driving beam 122, which reduces the stiffness of the driving beam 122 and reduces the resonant frequency, thereby making the mid- and high-frequency output of the speaker 100 poor. Therefore, it is necessary to reasonably design the relationship between l and lt and the relationship between w and wt.

[0270] In some embodiments, the physical quantity μ is defined as:

[0271] FIG. 23 is a frequency response curve diagram of a loudspeaker corresponding to different values ​​of μ according to some embodiments of this specification.

[0272] As shown in Figure 23, when μ = 0.6, the length dimension of hollow region 131-1 accounts for a large proportion, causing local resonance within hollow region 131-1 in the lower frequency range (e.g., within the frequency range below 1 kHz), generating the first resonance peak F221 of the frequency response curve. At this time, the length dimension l of suspended region 122-2 is smaller, resulting in a greater stiffness of drive beam 122, which generates a second resonance peak F222 of the frequency response curve at a higher frequency. Consequently, two resonance peaks appear in the low- to mid-frequency range (e.g., within the frequency range below 6 kHz), affecting the flatness of the frequency response curve of loudspeaker 100. Furthermore, due to the local resonance of hollow region 131-1 at a lower frequency, after the resonant frequency, vibration direction reversal and higher-order modes that are inconsistent with the modes of drive beam 122 may occur. Modes in the opposite direction to the modes of drive beam 122 may even appear, significantly reducing the output sound pressure level.

[0273] Figure 24 shows a vibration deformation cloud diagram of the drive beam and diaphragm, divided into quarters along the x- and y-direction symmetry lines, when μ = 0.6, according to some embodiments of this specification. As shown in Figure 24 , when the length of hollow region 131-1 accounts for a large proportion, hollow region 131-1 generates local modes within a lower frequency range, which appear inconsistent with and opposite to the modes of drive beam 122. Region 131-2 refers to the vibration region of diaphragm 131.

[0274] As μ increases, for example, to μ = 0.8, the length dimension l of the suspended region 122-2 increases, while the length dimension l of the hollow region 131-1 decreases, making it less likely for local resonance of the hollow region 131-1 to occur at lower frequencies. This allows the local modes of the hollow region 131-1 to follow the modes of the suspended region 122-2 within a wide frequency band of mid- and low-frequency frequencies, exhibiting consistent motion directions. This results in the speaker 100 achieving a relatively flat frequency response curve across the wide frequency band of mid- and low-frequency frequencies. Further increasing μ, for example to μ = 1, completely covers the length of the suspended region 122-2, i.e., the length of the hollow region 131-1 is zero. However, due to the larger size of the driving beam 122, the stiffness of the driving beam 122 decreases, resulting in a lower resonant frequency. This results in poor mid- and high-frequency performance of the speaker 100, significantly degrading the mid-frequency performance compared to μ values ​​of 0.7-0.8.

[0275] Therefore, the frequency response flatness and output sound pressure level of speaker 100 can be adjusted by adjusting the ratio of the length dimension l of the suspended region 122-2 to the first parameter lt. In some embodiments, μ can be in the range of 0.7-1. In some embodiments, μ can be in the range of 0.75-1. In some embodiments, μ can be in the range of 0.7-0.95. This ensures that speaker 100 maintains a certain sound pressure level output across a wide frequency band and has a relatively flat frequency response curve within the wide frequency band, thereby improving the sound quality of speaker 100.

[0276] In some embodiments, the sound quality of the speaker 100 can be adjusted by properly designing the relationship between the width w of the driving beam 122 and the width wt of the hollow region 131-1. Taking μ = 0.6 as an example, the relationship between w and wt is designed. In some embodiments, in the direction perpendicular to the direction extending from the fixed region 122-1 to the suspended region 122-2 (i.e., the y direction in FIG. 22 ), the ratio of the width w of the suspended region 122-2 to the width wt of the hollow region 131-1 is 0.5-0.95.

[0277] In some embodiments, a physical quantity δ is defined as:

[0278] FIG. 25 is a frequency response curve diagram of a loudspeaker corresponding to different values ​​of δ according to some embodiments of this specification.

[0279] As shown in Figure 25 , when δ = 0.5, the width of hollow region 131-1 accounts for a significant portion of the total width, causing local resonance within hollow region 131-1 within a relatively low frequency range (e.g., within a frequency range below 1 kHz), resulting in a first resonance peak F241 of the frequency response curve. Since the resonant frequency of drive beam 122 is primarily determined by its thickness, material, and length, the position of the second resonance peak remains essentially unchanged compared to the frequency response curve shown in Figure 23 when μ = 0.6. However, the presence of first resonance peak F241 results in two resonance peaks in the mid- and low-frequency ranges, affecting the flatness of the frequency response curve of loudspeaker 100. Furthermore, due to the local resonance within hollow region 131-1 at relatively low frequencies, vibration direction reversal and higher-order modes that are inconsistent with the modes of drive beam 122 may occur after the resonance frequency, even leading to modes in the opposite direction of the modes of drive beam 122, significantly reducing the output sound pressure level. Figure 26 shows a vibration deformation contour plot of the drive beam and diaphragm divided into four quarters along the x- and y-direction symmetry lines when δ = 0.5, according to some embodiments of this specification. As shown in FIG26 , when the width dimension of the hollow area 131 - 1 accounts for a large proportion, the hollow area 131 - 1 generates a local mode in a lower frequency range, which is inconsistent with the mode of the driving beam 122 and is opposite to the mode of the driving beam 122 .

[0280] As δ increases, for example, when δ = 0.65, the width of the suspended region 122-2 increases, while the width of the hollow region 131-1 decreases in proportion. This reduces the likelihood of local resonance in the hollow region 131-1 at lower frequencies. This allows the local modes of the hollow region 131-1 to follow the modes of the suspended region 122-2 across a wide frequency band of mid- and low-frequency frequencies, exhibiting consistent motion directions. This results in the loudspeaker 100 achieving a relatively flat frequency response curve across the wide frequency band of mid- and low-frequency frequencies. Furthermore, as the width w of the driving beam 122 increases, the driving force provided by the movement of the driving beam 122 increases, increasing the output sound pressure level of the loudspeaker 100 across a wider frequency band. Therefore, a larger width w of the driving beam 122 can be preferred. However, if δ is further increased, for example, to δ = 0.95, the width w of the driving beam 122 will make the width area of ​​the hollow region 131-1 too small, thereby increasing the local stiffness and further increasing the resonant frequency of the loudspeaker 100, which will reduce the output. Therefore, the width w of the driving beam 122 cannot be too large.

[0281] Therefore, the frequency response flatness and output sound pressure level of the speaker 100 can be adjusted by adjusting the ratio of the width w of the driving beam 122 to the width wt of the hollow region 131-1. In some embodiments, the value of δ can range from 0.5 to 0.95. In some embodiments, the value of δ can range from 0.65 to 0.95, ensuring that the speaker 100 maintains a certain sound pressure level output across a wide frequency band and a relatively flat frequency response curve within the wide frequency band, thereby improving the sound quality of the speaker 100.

[0282] In some embodiments, the suspended region 122 - 2 of any one of the driving beams 122 of the loudspeaker 100 includes an electrode covering region.

[0283] In some embodiments, the suspended region 122 - 2 of any driving beam 122 of the speaker 100 includes a non-electrode covering region, and the non-electrode covering region is at least partially located at an end of the driving beam 122 away from the fixed region 122 - 1 .

[0284] The electrodes in the drive beam 122 are used to transmit electrical signals (e.g., apply voltage) to the drive beam 122. In some embodiments, when the drive unit 120 is transmission-connected to the vibration unit 130 via the vibration transmission unit 140, the electrodes can be disposed on a side of the drive beam 122 away from the vibration transmission unit 140. In some embodiments, when the drive unit 120 is directly transmission-connected to the vibration unit 130, for example, when the diaphragm 131 directly covers the surface of the drive beam 122, the electrodes can be connected to the side of the drive beam 122 away from the diaphragm 131. In some embodiments, the electrodes can be regular shapes such as rectangles, circles, polygons, or any irregular shapes. In some embodiments, an electrode layer of the drive beam 122 can include one electrode or multiple electrodes, and the multiple electrodes can be randomly distributed, for example, the multiple electrodes can be distributed in an array. In some embodiments, the electrodes can cover the entire side of the drive beam 122, or they can cover a local area on the side of the drive beam 122. In some embodiments, the electrodes can be evenly distributed or unevenly distributed on the side of the drive beam 122.

[0285] Figure 27 is a side view of a drive beam with electrodes, shown in some embodiments of this specification, along the y-direction. As shown in Figure 27 , one side of the drive beam 122 is a fixed region 122-1, which is connected to the housing 110 or the base 126. The opposite side of the fixed region 122-1 along the x-direction is a suspended region 122-2. The electrodes cover the entire length of the drive beam 122 in the x-direction. When the drive beam 122 deforms in response to an electrical signal, the deformation occurs throughout the entire length of the drive beam 122 in the x-direction.

[0286] Figure 28 is a side view of a drive beam with electrodes, shown in some embodiments of this specification, along the y-direction. As shown in Figure 28, one side of the drive beam 122 is a fixed region 122-1, which is connected to the housing 110 or the base 126. The other side of the fixed region 122-1 along the x-direction is a suspended region 122-2. The electrodes cover the area within a portion of the length x of the fixed region 122-1. The area of ​​the drive beam 122 covered by the electrodes is defined as the electrode-covered area 1215. When the drive beam 122 deforms in response to an electrical signal, the deformation occurs only in the electrode-covered area 1215. Therefore, the vibration pattern of the drive beam 122 can be effectively controlled by adjusting the distribution of the electrodes, thereby adjusting the output sound pressure level of the speaker 100.

[0287] As shown in Figures 27 and 28 , compared to the electrode covering the entire length direction x of the driving beam 122, the electrode covering the suspended region 122-2 of the driving beam 122 includes a non-electrode-covered area. The non-electrode-covered area is at least partially located at the end of the driving beam 122 away from the fixed region 122-1, facilitating control of the vibration mode of the driving beam 122. In some embodiments, the vibration mode of the driving beam 122 can be effectively controlled by adjusting the electrode coverage area in the length direction x of the driving beam 122, thereby adjusting the vibration displacement of the driving beam 122 and adjusting the output sound pressure level of the speaker 100.

[0288] FIG. 29 is a projection diagram of a driving beam along the z direction according to some embodiments of the present specification.

[0289] In some embodiments, as shown in FIG29 , the electrode covering area 1215 can be rectangular in shape. The electrode covering area 1215 is disposed within the suspended area 122-2 of the drive beam 122, and the width of the electrode covering area 1215 is consistent with the width of the suspended area 122-2 of the drive beam 122. In some embodiments, to facilitate controlling the vibration of the drive beam 122, the electrode covering area 1215 can be disposed near the fixed area 122-1 of the drive beam 122. In some embodiments, the electrode covering area 1215 can also be disposed near the suspended area 122-2 of the drive beam 122, or even located midway between the fixed area 122-1 and the suspended area 122-2 of the drive beam 122. In some embodiments, since the fixed area 122-1 is fixed to the base 126 or the housing 110 and does not participate in the vibration of the drive beam 122, the electrode can be disposed only within the suspended area 122-2. Of course, electrodes can also be disposed within the fixed area 122-1 as needed. In some embodiments, the vibration mode of the driving beam 122 can be adjusted by properly designing the relationship between the length dimension of the electrode covering area 1215 along the longitudinal direction x and the length dimension of the driving beam 122. Here, the electrode covering area 1215 is described as a rectangle. It should be noted that the electrode covering area 1215 can also have other shapes (e.g., a trapezoid, a rounded rectangle, etc.).

[0290] In some embodiments, in a direction extending from the fixed region 122 - 1 to the suspended region 122 - 2 , a ratio of a length dimension of the electrode covering region 1215 to a length dimension of the suspended region 122 - 2 is 0.3-1.

[0291] In some embodiments, a physical quantity γ is defined as:

[0292] Wherein, la is the length of the electrode covering area 1215 on the driving beam 122 along the length direction x, l is the length of the suspended area 122-2 along the length direction x, and γ is the ratio of la to l.

[0293] FIG30 is a schematic diagram of the frequency response curves of a speaker corresponding to different γ values ​​according to some embodiments of this specification. As shown in FIG30 , curve L301 represents the frequency response curve of speaker 100 when γ = 0.3; curve L302 represents the frequency response curve of speaker 100 when γ = 0.6; curve L303 represents the frequency response curve of speaker 100 when γ = 0.9; and curve L304 represents the frequency response curve of speaker 100 when γ = 1. As FIG30 shows, when γ = 1, the corresponding curve L304 is at the highest position overall, and the output sound pressure level of the corresponding speaker 100 is the highest. As γ gradually decreases from 1 to 0.6, the corresponding curve gradually shifts downward, and the output sound pressure level of speaker 100 gradually decreases. When γ decreases from 0.6 to 0.3, the corresponding curve shifts downward significantly, and the output sound pressure level of speaker 100 significantly decreases. This is because when the value of γ is too small, the ratio of the length of the electrode covering area 1215 on the driving beam 122 to the length of the suspended area 122-2 is too small, and the length of the area in the suspended area 122-2 of the driving beam 122 where deformation occurs to generate driving force is too small, resulting in the driving beam generated by the driving beam 122 being too small, thereby reducing the output sound pressure level of the speaker 100.

[0294] Figure 31 is a vibration deformation cloud diagram of the drive beam and diaphragm divided into one quarter along the symmetry lines in the x- and y-directions when γ = 1, as shown in some embodiments of this specification. Figure 32 is a vibration deformation cloud diagram of the drive beam and diaphragm divided into one quarter along the symmetry lines in the x- and y-directions when γ = 0.75, as shown in some embodiments of this specification. As shown in Figure 31 , if the length of the electrode coverage area 1215 is too large, when the drive beam 122 vibrates and deforms, the area of ​​the drive beam 122 near its fixed area 122-1 and suspended area 122-2 (for example, the deformation reversal area 301 shown in Figure 31 ) will exhibit modes with opposite deformation directions at certain frequencies. As shown in Figure 32, when the length of the electrode covering area 1215 is appropriately reduced, the portion of the suspended area 122-2 that is not covered by the electrode only transmits vibration as a mechanical structure without deformation, so that the deformation of the mode with the opposite deformation direction that appears at certain frequencies in the area close to the speaker 100 and its fixed area 122-1 and the suspended area 122-2 (for example, the deformation reverse area 311a shown in Figure 32) is reduced, which can push more air and output a correspondingly larger sound pressure level.

[0295] In some embodiments, to enable the drive beam 122 to generate a greater driving force and thereby enable the speaker 100 to have a greater output sound pressure level, the ratio γ of the length 1a of the electrode covering area 1215 to the length l of the suspended area 122-2 may be in the range of 0.3-1. In some embodiments, to further increase the output sound pressure level of the speaker 100, the ratio γ of the length 1a of the electrode covering area 1215 to the length l of the suspended area 122-2 may be in the range of 0.5-0.1. In some embodiments, to further increase the output sound pressure level of the speaker 100, the ratio γ of the length 1a of the electrode covering area 1215 to the length l of the suspended area 122-2 may be in the range of 0.5-0.75. In some embodiments, the ratio γ of the length 1a of the electrode covering area 1215 to the length l of the suspended area 122-2 may be in the range of 0.5-0.8, thereby increasing the vibration displacement of the drive beam 122 and thereby improving the output sound pressure level of the speaker 100.

[0296] In some embodiments, only the suspended area 122-2 within the electrode-covered area 1215 of the driving beam 122 can deform and provide driving force. The suspended area 122-2, not covered by the electrode, serves only as a mechanical structure, transmitting force and displacement. Therefore, in some embodiments, the driving force of the driving beam 122 can be enhanced, thereby improving the output sound pressure level of the speaker 100, by designing the electrode coverage area on the driving beam 122 (i.e., the relationship between the area of ​​the electrode-covered area 1215 and the area of ​​the suspended area 122-2).

[0297] In some embodiments, the total area of ​​the suspended region 122-2 may be defined as Sk, the area of ​​the electrode covering region 1215 may be defined as Sd, and the parameter τ may be defined as the ratio of the area Sd of the electrode covering region 1215 to the total area Sk of the suspended region 122-2:

[0298] The parameter τ may represent the ratio of the area of ​​the deformed portion of the driving beam 122 (ie, the area corresponding to the electrode covering area 122 - 21 ) to the total area of ​​the suspended area 122 - 2 .

[0299] FIG33 is a schematic diagram of the frequency response curves of a speaker corresponding to different values ​​of τ according to some embodiments of this specification. As shown in FIG33 , curve L331 represents the frequency response curve of the speaker 100 when τ = 0.1; curve L332 represents the frequency response curve of the speaker 100 when τ = 0.28; curve L333 represents the frequency response curve of the speaker 100 when τ = 0.6; and curve L334 represents the frequency response curve of the speaker 100 when τ = 1. As shown in FIG33 , as the value of τ gradually increases from 0.1 to 1, the corresponding curve gradually moves upward, and the output sound pressure level of the speaker 100 gradually increases. In some embodiments, in order to make the speaker 100 have a larger output sound pressure level, the value of τ can range from 0.28 to 1. It should be noted that the larger the value of τ, the more deformation occurs on the drive beam 122, and the greater the driving force of the drive beam 122. However, due to the actual sample processing technology, electrode routing, and vibration mode control requirements, in some cases it cannot be guaranteed that the area Sd of the electrode coverage area 1215 can be the same as the total area Sk of the suspended area 122-2. Therefore, the value of τ sometimes cannot reach the maximum value of 1. In some embodiments, to ensure that the speaker 100 has a higher output sound pressure level, the ratio τ of the area of ​​the electrode coverage area 1215 to the area of ​​the suspended area 122-2 can be in the range of 0.3-1. In some embodiments, to ensure that the speaker 100 has a higher output sound pressure level, the ratio τ of the area of ​​the electrode coverage area 1215 to the area of ​​the suspended area 122-2 can be in the range of 0.5-1.

[0300] In some embodiments, the shape of the electrode covering area 1215 can also be designed to affect the driving force of the driving beam 122, thereby affecting the output sound pressure level of the speaker 100, and adjusting the vibration mode of the driving beam 122 and the speaker 100. The following lists several embodiments in which the electrode covering area 1215 has different shapes, which is not intended to be limiting. It should be noted that the above method of regulating the output sound pressure level of the speaker 100 by adjusting the ratio γ is also applicable to the case where the electrode covering area 1215 has different shapes (such as rectangle, trapezoid or circular chamfer).

[0301] 34A to 34F are projection views of a driving beam along the z direction according to some embodiments of the present specification.

[0302] In some embodiments, as shown in FIG34A , the electrode covering area 1215 is disposed within the suspended area 122-2. The electrode covering area 1215 may be in a trapezoidal shape. The width of the first side 12151 of the electrode covering area 1215 (i.e., the side disposed close to the fixed area 122-1) along the y direction is consistent with the width of the suspended area 122-2 in the y direction. The second side 12152 of the electrode covering area 1215 opposite to the first side is spaced a certain distance b from the side of the suspended area 122-2 away from the fixed area 122-1 (see FIG34A ).

[0303] The electrode covering area 1215 shown in Figure 34B is similar to the electrode covering area 1215 shown in Figure 34A, with the difference that: on the electrode covering area 1215, there is an arc chamfer between the long side of the side close to the suspended area 122-2 and away from the fixed area 122-1 and the short side along the x-direction, that is, it can be considered that on the electrode covering area 1215, the width dimension of the long side away from the fixed area 122-1 along the y-direction is smaller than the width dimension of the long side close to the fixed area 122-1 along the y-direction.

[0304] The electrode coverage area 1215 shown in FIG34C is similar to the electrode coverage area 1215 shown in FIG29 , except that a small rectangular area extends from the original rectangular electrode coverage area 1215 along the x-direction. The width of the small rectangular area along the y-direction is smaller than the width of the original rectangular area. In some embodiments, the small rectangular area can be located in the middle of the electrode coverage area 1215 along the y-direction.

[0305] The electrode coverage area 1215 shown in FIG34D is similar to the electrode coverage area 1215 shown in FIG34C , except that a small area is extended out in a trapezoidal shape, and its long side along the y direction is arranged close to the original rectangular area.

[0306] In some embodiments, the base 126 of the speaker 100 may also be covered with electrodes for the lead-in of electrical signals. In some embodiments, the electrodes on the base 126 may be covered on the end face connected to the drive beam 122. In some embodiments, the electrode on the base 126 may be one piece or multiple electrodes, and multiple electrodes may be distributed arbitrarily, for example, multiple electrodes may be distributed in an array. In some embodiments, the electrode may cover the entire end face where the base 126 is connected to the drive beam 122, or may cover a local area on the end face. In some embodiments, the electrodes may be evenly distributed on the end face where the base 126 is connected to the drive beam 122, or may be unevenly distributed. The following lists several ways of distributing the electrodes on the end face of the base 126, which are not intended to be limiting.

[0307] In addition to the electrode covering area 1215 shown in FIG. 29 , the electrode covering area 1215 shown in FIG. 34E also includes a second covering area 1216 on the end surface of the substrate 126. The second covering area 1216 is rectangular, and its width in the y-direction is consistent with the width of the drive beam 122 in the y-direction. In some embodiments, the second covering area 1216 can be located near the drive beam suspension area.

[0308] In addition to the electrode covering area 1215 shown in FIG. 29 , the electrode covering area 1215 shown in FIG. 34F also includes a second covering area 1216 on the end surface of the substrate 126. The second covering area 1216 includes multiple second electrode regions 12161 spaced apart along the y-direction. The width of the multiple second electrode regions 12161 in the y-direction is consistent with the width of the drive beam 122 in the y-direction. In some embodiments, the second covering area 1216 can be located near the drive beam suspension area.

[0309] In some embodiments, the vibration unit 130 includes a movable region, which is provided with a reinforcement portion. The reinforcement portion at least partially covers the movable region, and the center of the reinforcement portion coincides with the projection of the center of the movable region in the vibration direction of the vibration unit. The reinforcement portion can adjust the stiffness of the vibration unit 130, thereby adjusting the vibration mode of the vibration unit 130, thereby improving the vibration mode of the speaker 100 and enhancing the output performance of the speaker 100.

[0310] Figure 35 is a partial schematic diagram of a vibration unit according to some embodiments of this specification. Figure 36 is a structural schematic diagram of a diaphragm according to some embodiments of this specification. Figure 37 is a schematic diagram of a vibration unit according to some embodiments of this specification.

[0311] As shown in FIG35 , in some embodiments, the vibration unit 130, serving as the load end of the loudspeaker 100, may include a diaphragm 131 and a central reinforcement member 132. In some embodiments, referring to FIG1A and FIG35 , the diaphragm 131 may include an edge fixing portion 1311, a rim portion 1312, and a central portion 1313, wherein the edge fixing portion 1311 may be fixedly connected to the housing 110 of the loudspeaker 100, and the central portion 1313 may be provided with a central reinforcement member 132. The drive unit 120 may be connected to the central reinforcement member 132, or the drive unit 120 may be directly connected to the central portion 1313 of the diaphragm 131, thereby achieving mechanical energy transmission from the drive end (drive unit 120) to the load end (vibration unit 130).

[0312] Referring to Figure 36 , in some embodiments, movable region 1314 is the area of ​​diaphragm 131 excluding the portion connecting diaphragm 131 to housing 110. Specifically, movable region 1314 is the area of ​​diaphragm 131 excluding edge fixing portion 1311. In some embodiments, movable region 1314 may be comprised of surround portion 1312 and center portion 1313.

[0313] In some embodiments, the movable region 1314 is provided with a reinforcement portion 1321. In some embodiments, the reinforcement portion 1321 may be composed of a central reinforcement member 132 and a central portion 1313 corresponding to the central reinforcement member 132. In some embodiments, the reinforcement portion 1321 at least partially covers the movable region 1314, and the center of the reinforcement portion 1321 coincides with the projection of the center of the movable region 1314 in the vibration direction of the vibration unit 130.

[0314] In some embodiments, the area of ​​the movable region 1314 not covered by the reinforcement portion 1321 is the vibration suspension area 1322 of the diaphragm 131 . That is, the vibration suspension area 1322 of the diaphragm 131 refers to the area of ​​the movable region 1314 excluding the reinforcement portion 1321 .

[0315] In some embodiments, as shown in FIG37 , the vibration unit 130 includes a diaphragm 131. The area of ​​the diaphragm 131 covered by the reinforcement 1321 is defined as the reinforcement area Sq, and the area of ​​the movable region 1322 of the diaphragm 131 is defined as Sm. In some embodiments, the ratio of the reinforcement area Sq to the movable region area Sm is 0.5-0.85.

[0316] In some embodiments, the parameter z can be defined as the ratio of the area Sq of the reinforcement portion 1321 to the area Sm of the movable region 1322 of the diaphragm:

[0317] By designing the ratio ζ, the proportion of the area of ​​the vibration suspension area 1322 in the movable area 1314 can be determined, thereby determining the high-order resonance frequency of the mid-high frequency of the speaker 100 and adjusting the local mode of the diaphragm 131.

[0318] In some embodiments, within the mid- and high-frequency range, the driving beam 122 can generate a second-order mode, resulting in very small displacement of the driving unit 120 and the vibration transmission unit 140 of the loudspeaker 100, thereby causing the diaphragm assembly (i.e., the vibration unit 130, including the diaphragm 131 and / or the central reinforcement member 132) to generate small displacements. Furthermore, this can cause the frequency response of the loudspeaker 100 to have a dip within this mid- and high-frequency range. In some embodiments, by designing the size of the vibration suspension area 1322 so that it generates a local mode within the frequency range where the driving beam 122 generates the second-order mode, the dip in the output frequency response of the loudspeaker 100 within this mid- and high-frequency range caused by the small displacement of the diaphragm 131 due to the second-order mode generated by the driving beam 122 can be offset.

[0319] Figure 38A is a deformation contour map of a speaker corresponding to the parameter ζ = 0.5 according to some embodiments of this specification. Figure 38B is a deformation contour map of the speaker corresponding to Figure 38A from another perspective. Figure 39A is a deformation contour map of a speaker corresponding to the parameter ζ = 0.4 according to some embodiments of this specification. Figure 39B is a deformation contour map of the speaker corresponding to Figure 39A from another perspective. Figure 40 is a deformation contour map of a speaker corresponding to ζ = 0.9. Figure 41 is a schematic diagram of frequency response curves of a speaker corresponding to different ζ values ​​according to some embodiments of this specification.

[0320] As shown in Figures 38A and 38B , the deformation cloud diagram of the loudspeaker when ζ=0.5 shows that within the frequency band where the driving beam 122 generates a second-order mode, the vibration suspension area 1322 can generate a local mode, thereby contributing to the diaphragm assembly pushing the air, corresponding to the absence of a trough or an improvement in the trough in the frequency response curve (as shown in curve L412 in Figure 41 ). However, as shown in Figures 39A and 39B , when ζ=0.4, due to the excessive proportion of the area of ​​the vibration suspension area 1322, different positions of the vibration suspension area 1322 have generated motion modes in different directions within the frequency band, corresponding to the presence of a trough in the frequency response curve (as shown in curve L411 in Figure 41 ). As shown in Figure 40, when ζ=0.9, the area of ​​the vibration suspension area 1322 is too small, resulting in the vibration suspension area 1322 basically not generating local modes in this frequency band, and the corresponding frequency response curve (curve L414 as shown in Figure 41) still has a trough in this frequency band.

[0321] In some embodiments, by adjusting the size of the suspended vibration area 1322, the stiffness of the diaphragm 131 can be adjusted, thereby adjusting the low-frequency resonant frequency f0 of the speaker 100 in the low-frequency range. In some embodiments, by adjusting the size of the suspended vibration area 1322, the local stiffness of the diaphragm 131 can also be adjusted in the mid- and high-frequency ranges to achieve local modal adjustment, further cooperating with the driver unit 120 of the speaker 100 to achieve peak and valley adjustment of the mid- and high-frequency frequency response curve.

[0322] As shown in Figure 41, curve L411 represents the frequency response curve of the speaker 100 when ζ=0.4; curve L412 represents the frequency response curve of the speaker 100 when ζ=0.5; curve L413 represents the frequency response curve of the speaker 100 when ζ=0.85; curve L414 represents the frequency response curve of the speaker 100 when ζ=0.9.

[0323] As can be seen from FIG41 , when ζ = 0.4 or ζ = 0.9, the frequency response curve of speaker 100 (corresponding to curves L411 and L414) has a significant dip in the mid-high frequency band (i.e., the dip within dashed circle P). When ζ = 0.5 to ζ = 0.85, the frequency response curve of speaker 100 (e.g., curves L412 and L413) has no significant dip in the mid-high frequency band. Therefore, in some embodiments, to make the frequency response curve of speaker 100 relatively flat in the mid-high frequency band, ζ may be within the range of 0.5-0.85.

[0324] In some embodiments, the edge of the diaphragm 131 includes a rounded corner, and the movable region 1314 has a length dimension extending from the fixed region 122-1 to the suspended region 122-2. In some embodiments, the ratio of the radius of the rounded corner to half the length dimension of the movable region 1314 is 0-0.7.

[0325] In some embodiments, the edge of the diaphragm 131 is connected to the speaker housing 110. When the speaker housing 110 has a corner (for example, a right angle or an acute angle), the edge of the diaphragm is connected to the housing 110 at the corner. At this time, during the vibration of the diaphragm, stress concentration is easily caused, which causes the diaphragm 131 to wrinkle or even be damaged. It also causes the harmonic distortion of the speaker 100 to increase, affecting the reliability of the speaker 100. Therefore, in some embodiments, the diaphragm edge can be designed with a rounded corner at the corner position, but the diaphragm edge rounded corner will cause the area of ​​the vibration suspension area 1322 of the speaker near this specific position to change, which will affect the local mode of the vibration suspension area 1322 in the medium and high frequencies. Therefore, it is necessary to design the size of the diaphragm edge rounded corner to ensure that the vibration suspension area 1322 can still effectively form a local mode in the medium and high frequencies, thereby offsetting the problem of the speaker output frequency response having a trough in this frequency band due to the small diaphragm displacement caused by the second-order mode generated by the driving beam 122.

[0326] Figure 42 is a schematic diagram of a diaphragm according to some embodiments of the present specification. In some embodiments, the parameter λ can be defined as the radius l of the fillet at the edge of the diaphragm. R The length of the movable area of ​​the diaphragm along the length direction of the driving beam (the x direction shown in FIG42 ) is half l m The ratio between:

[0327] The design parameter λ can be used to determine the area ratio of the vibration suspension region 1322 near the corner position of the loudspeaker, thereby determining the mid- and high-frequency resonance frequencies of the loudspeaker 100 and adjusting the local mode of the diaphragm 131 .

[0328] Figure 43 is a diagram illustrating frequency response curves of a speaker corresponding to different values ​​of λ according to some embodiments of this specification. As shown in Figure 43, curve L431 represents the frequency response curve of speaker 100 when λ = 0; curve L432 represents the frequency response curve of speaker 100 when λ = 0.17; curve L433 represents the frequency response curve of speaker 100 when λ = 0.33; curve L434 represents the frequency response curve of speaker 100 when λ = 0.7; and curve L435 represents the frequency response curve of speaker 100 when λ = 0.8.

[0329] As can be seen from Figure 43, when λ is small, for example, λ = 0 (corresponding to a square speaker), there is no trough on the speaker frequency response curve near the frequency of the second-order mode generated by the driving beam. As λ gradually increases, the area of ​​the vibration suspension area 1322 near the four corners of the speaker gradually decreases, and the local deformation of the diaphragm assembly in the mid- and high-frequency bands (for example, 7kHz-8kHz) decreases, which will cause the speaker to produce corresponding troughs in the mid- and high-frequency bands. For example, when λ increases to 0.8, an obvious trough is generated on the corresponding curve L435. In addition, as λ gradually increases, the diaphragm stiffness gradually increases, and the low-frequency resonance peak of the speaker gradually moves to high frequency.

[0330] In some embodiments, to ensure that the speaker 100 has a relatively flat frequency response curve in the mid-high frequency band, the value of λ may be in the range of 0-0.7. In some embodiments, the value of λ may be in the range of 0.2-0.6. In some embodiments, the value of λ may be in the range of 0.3-0.5.

[0331] In some embodiments, the structure of the reinforcement portion 1321 can be designed to adjust the stiffness of the connection area between the speaker drive unit 120 and the diaphragm assembly, thereby adjusting the mode of the diaphragm assembly.

[0332] In some embodiments, the reinforcing portion 1321 is hollowed out; or, a notch is provided on the circumference of the reinforcing portion 1321 .

[0333] 44A , 44B and 44C are partial schematic diagrams of speakers according to some embodiments of the present specification.

[0334] As shown in Figures 44A and 44B, in some embodiments, the central reinforcement member 132 may have a notch 1323 in the connection area between the drive unit 120 and the diaphragm assembly to effectively adjust the stiffness of the connection area between the speaker drive unit 120 and the diaphragm assembly, thereby adjusting the mode of the diaphragm assembly. In some embodiments, the notch 1323 may be located in the middle of the connection area between the drive unit 120 and the diaphragm assembly. In some embodiments, the notch 1323 may be located at the edge of the connection area between the drive unit 120 and the diaphragm assembly (as shown in Figure 44A).

[0335] In some embodiments, when the notch 1323 is located in the middle of the connection area between the driver unit 120 and the diaphragm assembly, the shape of the notch 1323 may be circular, elliptical, quadrilateral (including but not limited to square, rectangle, diamond, etc.), pentagon, hexagon, octagon, or other polygonal shapes. In some embodiments, when the notch 1323 is located at the edge of the connection area between the driver unit 120 and the diaphragm assembly, the outline of the notch 1323 may be composed of a straight line (as shown in FIG. 44A ) or an arc (as shown in FIG. 44C ).

[0336] In some embodiments, the driving unit 120 and the vibration unit 130 of the speaker 100 can be an integrated structure. For example, the driving unit 120 and the vibration unit 130 can be an integrated structure both prepared using a microelectromechanical systems (MEMS) process. In some embodiments, the vibration unit 130 can be made of semiconductor materials, polymer materials, etc. Exemplary semiconductor materials may include silicon (Si), silicon dioxide (SiO2), silicon nitride (SiNx), silicon carbide (SiC), etc. Exemplary polymer materials may include polyimide (PI), parylene, polydimethylsiloxane (PDMS), hydrogel, photoresist, silica gel, silicone gel, silicone sealant, etc. In some embodiments, the driving unit 120, the vibration unit 130 and the housing 110 are connected by assembly.

[0337] In some embodiments, the drive unit 120 and the vibration unit 130 of the speaker 100 can be separate structures. For example, the drive unit 120 can be manufactured using a MEMS process, and the vibration unit 130 can be manufactured using a traditional process such as die casting, vacuum forming, hot pressing or injection molding. In some embodiments, the vibration unit 130 can be made of a rigid material. Exemplary rigid materials may include aluminum alloy, carbon fiber, magnesium-lithium alloy, stainless steel, plastic, etc. In some embodiments, the drive unit 120 and the vibration unit 130 can be assembled using bonding or other methods.

[0338] FIG45 is a schematic diagram of the internal structure of a speaker with a slit structure according to some embodiments of this specification.

[0339] In some embodiments, as shown in FIG45 , the vibration unit 130 is not directly connected to the housing 110, and a slit structure 150 is provided between the vibration unit 130 and the inner wall of the housing 110. In some embodiments, the slit structure 150 is a 360° annular structure. Providing the slit structure 150 between the vibration unit 130 and the housing 110 can reduce the restraining force on the vibration unit 130 during movement, thereby increasing the range of motion (vibration amplitude) of the vibration unit 130 and improving the output sound pressure level of the speaker 100.

[0340] At the same time, by setting the slit width, in some embodiments, to prevent acoustic leakage from the front cavity 111 and the rear cavity 112 when the vibration unit 130 moves, resulting in an acoustic short circuit and reduced output of the speaker 100, the width of the slit structure 150 can be 5 μm-30 μm. In some embodiments, to further prevent acoustic short circuits from reducing the output of the speaker 100, the width of the slit structure 150 can be 10 μm-20 μm.

[0341] In some embodiments, in order to ensure that the vibration direction of the vibration unit 130 (such as the diaphragm 131) remains unchanged and does not deflect during movement, the shape structure of the vibration transfer unit 140 can be designed to increase the contact area between the vibration transfer unit 140 and the vibration unit 130.

[0342] Figures 46A and 46B are schematic diagrams of partial structures of speakers according to some embodiments of this specification. In some embodiments, the speaker shown in Figure 46A is similar to the speaker shown in Figure 1A, except that the vibration transmission unit of the speaker shown in Figure 46A has a trapezoidal structure. In some embodiments, the speaker shown in Figure 46B is similar to the speaker shown in Figure 1A, except that the vibration transmission unit of the speaker shown in Figure 46B has an I-shaped structure.

[0343] In some embodiments, in order to avoid local deformation modes of the vibration unit 130 of the speaker 100 , the stiffness / mass ratio of the vibration unit 130 may be increased.

[0344] FIG47 is a schematic diagram of a partial structure of a speaker according to some other embodiments of the present specification.

[0345] In some embodiments, the speaker shown in FIG47 is similar to the speaker shown in FIG1A , except that the vibration unit 130 of the speaker shown in FIG47 has a stepped structure. For example, as shown in FIG47 , the stepped vibration unit 130 may include an additional diaphragm (not shown) at the center of the diaphragm 131. The area of ​​the newly added diaphragm is smaller than that of the original diaphragm 131.

[0346] FIG48 is a projection diagram of the vibration unit along the vibration direction of the diaphragm according to some embodiments of the present specification.

[0347] In some embodiments, the speaker shown in FIG48 is similar to the speaker shown in FIG1A , except that the diaphragm 131 of the vibration unit 130 shown in FIG48 includes a reinforcement 1321. As shown in FIG48 , the reinforcement 1321 can be arranged along the length and width of the diaphragm 131, and the projection pattern formed by the reinforcement 1321 can include one or more hollow structures. For more information about the reinforcement, please refer to the relevant sections above, such as FIG35 to FIG37 .

[0348] In some embodiments of the present specification, by designing a vibration unit 130 with a stepped structure or a vibration unit 130 with a reinforced portion, the stiffness / mass ratio of the vibration unit 130 can be further increased, ensuring that the diaphragm is always in the vibration direction (i.e., the z direction) during movement, thereby avoiding the occurrence of local deformation modes of the vibration unit 130.

[0349] In some embodiments, the drive beam 122 has a drive beam reinforcement layer.

[0350] FIG49A is a schematic diagram of a speaker according to some embodiments of the present specification.

[0351] In some embodiments, the speaker shown in FIG49A is similar to the speaker shown in FIG1A , except that the drive beam 122 of the speaker shown in FIG49A includes a drive beam reinforcement layer 122-3. The drive beam reinforcement layer 122-3 can be disposed on the side of the drive beam 122 away from the vibration unit 130 to reinforce the drive beam 122. The drive beam reinforcement layer 122-3 can connect the suspended regions 122-2 of different drive beams 122, and multiple drive beams 122 are transmission-connected to the vibration transmission unit 140 or the vibration unit 130 via the drive beam reinforcement layer 122-3. In some embodiments, the drive beam reinforcement layer 122-3 can be composed of a polymer material or a semiconductor material. Exemplary polymer materials include polyimide, photoresist, parylene, hydrogel, etc. Exemplary semiconductor materials include one or more composite materials selected from silicon, silicon nitride, silicon oxide, silicon carbide, etc.

[0352] In some embodiments, in order to allow the driving beam 122 to have a larger displacement, a slit structure 150 may be designed between the driving beam 122 and the base 126 of the driving unit 120 of the speaker, or between different driving beams 122 .

[0353] FIG49B is a projection diagram of the driving beam and the diaphragm along the vibration direction of the vibration unit according to some embodiments of this specification.

[0354] In some embodiments, the speaker shown in FIG. 49B is similar to the speaker shown in FIG. 49A , except that a slit structure 150 exists between the driving beam 122 and the base 126 of the speaker shown in FIG. 49B .

[0355] In some embodiments, there is also a slit structure between adjacent driving beams. Referring to FIG. 21I , there is a slit structure 150 between adjacent driving beams 122 .

[0356] In some embodiments, the speaker 100 may include a plurality of drive units 120 arranged in parallel.

[0357] 50A-50B are schematic diagrams of a loudspeaker including a plurality of parallel driving units according to some embodiments of the present specification.

[0358] As shown in FIG50A , the loudspeaker 100 may include multiple parallel drive units (e.g., drive units 120-1, 120-2, 120-n, etc.). The multiple drive units are respectively connected to a vibration unit 130 through corresponding vibration transmission units 140. The multiple drive units jointly provide sufficient power for the vibration of the vibration unit 130 to increase the vibration amplitude of the vibration unit 130 and enhance the output of the loudspeaker 100. The drive beams of the multiple drive units can be connected to the bottom wall of the housing 110 through the base 126. The portion between adjacent bases 126 can serve as a drive unit, and the corresponding portion of the housing 110 is correspondingly provided with an acoustic hole for sound output.

[0359] The speaker shown in Figure 50B is similar to the speaker shown in Figure 50A, with the difference being that the speaker 100 shown in Figure 50B does not include a vibration transfer unit 140, and a plurality of parallel drive units (such as drive units 120-1, 120-2, 120-n, etc.) are directly connected to the vibration unit 130 (such as the diaphragm 131).

[0360] In some embodiments of the present specification, providing multiple parallel drive units in a speaker can increase the distribution range of the sound output by the speaker and enhance the volume; in addition, different drive units can also adapt to the conversion of electrical signals and sound signals of different frequencies respectively, making the audio performance more comprehensive.

[0361] The basic concepts have been described above. It will be apparent to those skilled in the art that the detailed disclosure above is merely illustrative and does not limit the present application. Although not explicitly stated herein, those skilled in the art may make various modifications, improvements, and amendments to the present application. Such modifications, improvements, and amendments are suggested in the present application and remain within the spirit and scope of the exemplary embodiments of the present application.

[0362] At the same time, this application uses specific terms to describe the embodiments of this application. For example, "one embodiment," "an embodiment," and / or "some embodiments" refer to a certain feature, structure, or characteristic related to at least one embodiment of this application. Therefore, it should be emphasized and noted that "one embodiment," "an embodiment," or "an alternative embodiment" mentioned twice or multiple times in different locations in this specification does not necessarily refer to the same embodiment. In addition, certain features, structures, or characteristics in one or more embodiments of this application may be appropriately combined.

[0363] Similarly, it should be noted that, in order to simplify the presentation of this application and thus facilitate understanding of one or more embodiments of the invention, the foregoing descriptions of the embodiments of this application sometimes combine multiple features into a single embodiment, figure, or description thereof. However, this disclosure method does not mean that the subject matter of this application requires more features than those recited in the claims. In fact, an embodiment may have fewer features than all of the features of a single embodiment disclosed above.

[0364] In some embodiments, numbers are used to describe the quantity of components and attributes. It should be understood that such numbers used in the description of the embodiments are modified by the modifiers "about", "approximately" or "substantially" in some examples. Unless otherwise stated, "about", "approximately" or "substantially" indicate that the numbers are allowed to vary by ±20%. Accordingly, in some embodiments, the numerical parameters used in the description and claims are approximate values, which may change according to the required features of individual embodiments. In some embodiments, the numerical parameters should take into account the specified significant digits and adopt the general method of retaining digits. Although the numerical domains and parameters used to confirm the breadth of their range in some embodiments of the present application are approximate values, in specific embodiments, the settings of such numerical values ​​are as accurate as possible within the feasible range.

[0365] Each patent, patent application, patent application disclosure, and other materials, such as articles, books, specifications, publications, documents, etc., cited in this application is hereby incorporated by reference in its entirety. This includes application history documents that are inconsistent with or conflict with the content of this application, as well as documents (currently or subsequently attached to this application) that limit the broadest scope of the claims of this application. It should be noted that if the descriptions, definitions, and / or use of terms in the accompanying materials of this application are inconsistent or conflicting with the content of this application, the descriptions, definitions, and / or use of terms in this application shall prevail.

[0366] Finally, it should be understood that the embodiments described in this application are merely illustrative of the principles of the embodiments of this application. Other variations may also fall within the scope of this application. Therefore, by way of example and not limitation, alternative configurations of the embodiments of this application may be considered consistent with the teachings of this application. Accordingly, the embodiments of this application are not limited to the embodiments explicitly introduced and described in this application.

Claims

1. A loudspeaker, comprising: A housing, a driving unit and a vibration unit, wherein the driving unit is fixed to the housing, and the driving unit is transmission-connected to the vibration unit; wherein, The driving unit includes a plurality of driving beams, any one of which includes a fixed area and a suspended area, any one of which is connected to the shell via the fixed area, and any one of which is transmission-connected to the vibration unit via the suspended area.

2. The loudspeaker according to claim 1, wherein For any one of the driving beams, the suspended area has a length dimension in the direction extending from the fixed area to the suspended area; the suspended area has a thickness dimension in the vibration direction of the vibration unit; and the value range of the power of half of the ratio of the thickness dimension of the suspended area to the square of the length dimension of the suspended area is 0.01-0.

3.

3. The loudspeaker according to claim 1 or 2, wherein: The driving beam includes a substrate layer, a first electrode layer, a piezoelectric layer, a second electrode layer and a reinforcement layer stacked along a vibration direction of the vibration unit, and a ratio of a thickness of the substrate layer to a thickness of the piezoelectric layer is 0-2.

4. The loudspeaker according to claim 1, wherein: The driving beam includes a piezoelectric structure and one or more reinforcement layers stacked along the vibration direction of the vibration unit, and a groove structure is provided on the reinforcement layer farthest from the piezoelectric structure.

5. The loudspeaker according to claim 4, wherein: In a direction extending from the fixed area to the suspended area, the groove structure includes a plurality of grooves, and a size of the groove close to the fixed area is larger than a size of the groove far from the fixed area.

6. The loudspeaker according to claim 4, wherein: In the direction extending from the fixed area to the suspended area, the groove structure includes a plurality of reinforcing components arranged at intervals, a groove is provided between any two adjacent reinforcing components, and the width of the reinforcing component away from the fixed area is greater than the width of the reinforcing component close to the fixed area.

7. The loudspeaker according to any one of claims 1 to 4, wherein: The any one of the driving beams is respectively connected to a vibration transmission unit, the vibration transmission unit is connected to the vibration unit, and the any one of the driving beams transmits vibration to the vibration unit through the vibration transmission unit.

8. The loudspeaker according to claim 7, wherein: The driving unit includes two groups of driving beams located at opposite sides of the shell, each of the two groups of driving beams includes one or more driving beams, and the shape of the driving beams includes rectangle, trapezoid or circular chamfer.

9. The loudspeaker according to claim 8, wherein: The driving unit further includes two sets of driving beams located on another opposite side of the housing.

10. The loudspeaker according to claim 9, wherein The vibration transfer unit comprises an annular structure, and any set of driving beams are connected to different areas of the vibration transfer unit.

11. The loudspeaker according to claim 10, wherein: The vibration transmission unit is connected to a second driving beam, and the second driving beam is indirectly connected to the shell.

12. The loudspeaker according to claim 11, wherein The vibration unit further includes a mass element, and one end of the second driving beam away from the vibration transmission unit is directly connected to the mass element; or one end of the second driving beam away from the vibration transmission unit is connected to the mass element via a coupling elastic structure.

13. The loudspeaker according to claim 10, wherein: The vibration unit further includes a mass element, and the vibration transfer unit is connected to the mass element via a coupling elastic structure.

14. The loudspeaker according to claim 8, wherein The two groups of driving beams extend alternately, the vibration transmission unit comprises a folding structure, and any group of driving beams is connected to different areas of the vibration transmission unit.

15. The loudspeaker of claim 14, wherein: Any one of the groups of driving beams is directly connected to the vibration transfer unit; or, any one of the groups of driving beams is connected to the vibration transfer unit via a coupling elastic structure.

16. The loudspeaker according to claim 8, wherein Each group of driving beams includes a driving beam with a bending structure, and one end of each of the two driving beams with the bending structure in the two groups of driving beams, which is away from the corresponding fixed area, is coupled to the same vibration transmission unit.

17. The loudspeaker according to any one of claims 1 to 4, wherein: The any one driving beam is stacked in different areas of the vibration unit respectively.

18. The loudspeaker of claim 17, wherein: The driving unit includes two groups of driving beams located at opposite sides of the shell, each of the two groups of driving beams includes one or more driving beams, and the shape of the driving beams includes rectangle, trapezoid or circular chamfer.

19. The loudspeaker of claim 17, wherein: The driving unit further includes two sets of driving beams located on another opposite side of the housing.

20. The loudspeaker of claim 17, wherein: The vibration unit further comprises a mass element, wherein the mass element comprises an annular structure, and any set of driving beams are connected to different regions of the mass element.

21. The loudspeaker of claim 17, wherein: The vibration unit further includes a second driving beam, and the second driving beam is indirectly connected to the housing.

22. The loudspeaker of claim 21, wherein The vibration unit further includes a mass element, and the second driving beam is connected to the mass element.

23. The loudspeaker of claim 21, wherein: Any one of the driving beams is connected to different regions of the second driving beam via a coupling elastic structure.

24. The loudspeaker of claim 18, wherein: The two groups of driving beams extend alternately.

25. The loudspeaker of claim 18, wherein: Each set of driving beams includes a driving beam with a bending structure.

26. The loudspeaker of claim 17, wherein: The vibration unit includes a hollow area not covered by the driving beam. The suspended area has a length dimension in a direction extending from the fixed area to the suspended area. The sum of the length of the driving beam and half of the length of the hollow area is defined as a first parameter. The ratio of the length dimension of the suspended area to the first parameter is 0.7-1.

27. The loudspeaker of claim 17, wherein: The vibration unit includes a hollow area not covered by the driving beam, and in a direction perpendicular to a direction extending from the fixed area to the suspended area, a ratio of a width dimension of the suspended area to a width dimension of the hollow area is 0.5-0.

95.

28. The loudspeaker of claim 17, wherein: Different driving beams are connected via coupling elastic structures.

29. The loudspeaker according to any one of claims 1 to 28, wherein: The suspended area of ​​any one of the driving beams includes a non-electrode covering area, and the non-electrode covering area is at least partially located at an end of the driving beam away from the fixed area.

30. The loudspeaker of claim 29, wherein: The suspended area of ​​any one of the driving beams includes an electrode covering area, and in a direction extending from the fixed area to the suspended area, a ratio of a length dimension of the electrode covering area to a length dimension of the suspended area is 0.3-1.

31. A loudspeaker as claimed in claim 29 or 30, wherein: The ratio of the area of ​​the electrode covering region to the area of ​​the suspended region is 0.3-1.

32. A loudspeaker as claimed in any one of claims 29 to 31, wherein: The electrode coverage area has a shape including a rectangle, a trapezoid or a circular chamfer.

33. The loudspeaker of claim 7, wherein: Any one of the driving beams is connected to the vibration transfer unit via a coupling elastic structure.

34. The loudspeaker of claim 33, wherein: In the vibration direction of the vibration unit, the ratio of the thickness of the coupling elastic structure to the thickness of the driving beam is 0.65-1.

35. A loudspeaker as claimed in claim 33 or 34, wherein: The driving beam includes a piezoelectric structure and one or more reinforcement layers stacked along the vibration direction of the vibration unit, and the reinforcement layer farthest from the piezoelectric structure is connected to the coupling elastic structure.

36. The loudspeaker of claim 33, wherein: The coupling elastic structure is provided with a hollow structure.

37. The loudspeaker of claim 33, wherein: The coupling elastic structure includes a bending structure.

38. A loudspeaker as claimed in any one of claims 1 to 37, wherein: The vibration unit includes a movable area, the movable area is provided with a reinforcement portion, the reinforcement portion at least partially covers the movable area, and the center of the reinforcement portion coincides with the projection of the center of the movable area in the vibration direction of the vibration unit.

39. The loudspeaker of claim 38, wherein: The vibration unit includes a diaphragm, and the area of ​​the region on the diaphragm covered by the reinforcement portion is defined as the reinforcement portion area. The ratio of the reinforcement portion area to the area of ​​the movable region is 0.5-0.

85.

40. The loudspeaker of claim 38, wherein: The edge of the diaphragm includes an edge fillet, and the movable area has a length dimension in a direction extending from the fixed area to the suspended area. The ratio of the radius of the edge fillet to half of the length dimension of the movable area is 0-0.

7.

41. The loudspeaker of claim 38, wherein: The reinforcing portion is provided with a hollowing out; or, a peripheral side of the reinforcing portion is provided with a notch.

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