Acoustic strengthening system and method

Abstract

Disclosed are an acoustic strengthening system and method, relating to the technical fields of raw material treatment and process strengthening treatment. The acoustic strengthening system comprises an acoustic strengthening cavity, a mechanical resonator, and a pressure control system and / or a temperature control system. The mechanical resonator is a multi-mass vibration system, and forms a mechanical resonance system with the acoustic strengthening cavity, so that the acoustic strengthening cavity can produce mechanical resonance having a frequency in the range of 40Hz-80Hz and an amplitude in the range of 2mm-20mm in the axis direction of a cylindrical inner cavity. The acoustic strengthening cavity is connected with the pressure control system and / or the temperature control system by means of tubing. By controlling the pressure and / or temperature inside the acoustic strengthening cavity, and the excitation force strength and the vibration displacement / speed / acceleration of the acoustic strengthening cavity, various types of treatment may be performed on materials added into the acoustic strengthening cavity, such as raw material mixing, dispersing, coating, grinding, crushing, emulsifying, extracting, dissolving and chemical reaction strengthening.

Description

Acoustic enhancement system and method Technical Field

[0001] The present invention relates to a raw material processing and process intensification processing equipment and method, and in particular to an acoustic enhancement system and method. Background Art

[0002] The elasticity of an object means that a disturbance at one location can be transmitted to other locations in the object in the form of waves. These waves are generally called elastic waves. Elastic waves are a physical phenomenon caused by the elasticity of an object. Depending on the elasticity or compressibility of the object, elastic waves typically manifest in different forms. Because solids are incompressible, elastic waves manifest in solids as shear deformation and vibration. Liquids and gases are both compressible to a certain extent, and elastic waves in these fluids manifest as compression waves or acoustic waves. For liquids and gases, within a certain range of volume compression (often referred to as the linear range), the pressure fluctuations or vibrations caused by acoustic waves are continuous. This means that a unit of mass in the liquid or gas remains stable during compression or vibration, and its original position does not change over time. However, when the pressure or vibration exceeds the compressive deformation tolerance of the liquid or gas, the unit of mass in the liquid or gas will displace while compressing or vibrating, changing its initial position and causing flow. This is the concept of "acoustic streaming," which refers to fluid flow caused by significant compression or vibration. It can be seen that the generation of linear sound waves only requires a small amount of energy, while the generation of acoustic streaming requires a large amount of energy. In order to generate a large amount of energy, the compression or vibration frequency must be high, or the compression or vibration amplitude must be large, or both.

[0003] The most typical application of acoustic streaming is ultrasound, which uses a "high frequency + small amplitude" approach to provide high energy. High-frequency vibrations generate acoustic streaming in liquids, accompanied by high temperatures and dramatic pressure fluctuations. However, due to the high frequency (greater than 20,000 Hz) and small amplitude (micrometer level), ultrasound's energy is too concentrated and dissipates quickly. Acoustic streaming is therefore limited to a localized area, restricted to treating low-viscosity, low-solids liquids, severely restricting its application.

[0004] Summary of the Invention

[0005] In response to the shortcomings of the existing technology, the present invention provides an acoustic enhancement system and method, which uses a "low frequency + large amplitude" method to generate higher energy. The matched acoustic enhancement cavity promotes the raw materials to generate a single vortex acoustic flow motion for mass transfer, heat exchange, interaction / reaction under mechanical resonance conditions. Under the pressure control and / or temperature control inside the acoustic enhancement cavity, it has the characteristics of full-field motion, uniform energy dispersion, controllable and adjustable energy, etc. The maximum volume filling rate of applicable materials can reach 100%, significantly improving production capacity; the parameter-optimized mechanical resonator can almost completely transfer the excitation force to the material in the acoustic enhancement cavity, output sufficient energy to ensure the material acoustic flow motion, and can operate stably for a long time; the enhancement treatment method that uses the excitation force intensity of the mechanical resonator or the pressure and / or temperature inside the acoustic enhancement cavity as the main adjustment parameters to control the vibration acceleration of the acoustic enhancement cavity is suitable for processing a variety of raw materials.

[0006] To achieve the above objectives, the present invention provides the following technical solution: an acoustic enhancement system, comprising:

[0007] The acoustic enhancement chamber is used to accommodate the processed material and generate a sound flow motion with uniform energy distribution and controllable energy throughout the field;

[0008] Mechanical resonator is used to couple the acoustic enhancement cavity to produce mechanical resonance, generate strong vibration, and transfer the excitation energy directly and almost completely to the processed material;

[0009] The acoustic enhancement cavity is fixedly connected to the mechanical resonator;

[0010] The acoustic enhancement cavity includes a cylindrical inner cavity, wherein the diameter D of the cylindrical inner cavity is less than 1200 mm, the ratio of the length L of the cylindrical inner cavity to the diameter D is within the range of 0.5-3, and the bottom and top of the cylindrical inner cavity are both provided with rounded corners, and the ratio of the size R of the rounded corner to the diameter D of the cylindrical inner cavity is within the range of 0.1-0.5. The size and shape of the acoustic enhancement cavity significantly affect the morphology of the first-order acoustic flow. The single acoustic flow morphology facilitates rapid mass transfer, heat transfer, and interaction / reaction between materials at different positions in the acoustic enhancement cavity.

[0011] The cylindrical inner cavity walls are all rigid walls with smooth surfaces and a surface roughness of not less than Ra3.2. Insufficient wall rigidity and rough surface will lead to changes in the internal first-order acoustic flow morphology, and the rough surface will also increase energy consumption.

[0012] The cylindrical inner cavity is provided with a pipeline interface connected to the outside, which can be used to increase the means of strengthening the process or to be used for adding or discharging materials or measuring temperature or pressure.

[0013] The mechanical resonator is a multi-mass vibration system. The mechanical resonator and the acoustic enhancement cavity constitute a mechanical resonance system, so that the acoustic enhancement cavity generates mechanical resonance in the axial direction of the cylindrical inner cavity with a frequency in the range of 40Hz-80Hz and an amplitude in the range of 2mm-20mm. The multi-mass vibration system can output large acceleration vibration under resonance conditions while reducing the vibration of the drive mechanism, protecting the drive mechanism, and minimizing the force transmitted to the equipment foundation. The corresponding wavelength in the frequency range of 40Hz-80Hz can match the size of the acoustic enhancement cavity, and the vibration intensity (energy) when the amplitude reaches 2mm-20mm at this frequency is sufficient to generate the acoustic flow motion required for the material, and the maximum volume filling rate of the material can reach 100%. It is particularly noteworthy that when the mechanical resonator works under resonance conditions, almost all of the input energy is transferred to the material, which is a key parameter of the material processing process.

[0014] After a large number of tests with materials of different densities, different proportions, different filling ratios, different vibration frequencies, different amplitude conditions, and different acoustic enhancement cavity sizes and shapes, the acoustic enhancement system described in the present invention can effectively cause the processed materials to produce a first-order acoustic flow in the form of a polar-symmetrical single vortex distribution. All materials move in the same vortex, and energy is continuously transferred and replenished from the first-order acoustic flow to the higher-order acoustic flow. The micro-vibration or compression effect of the higher-order acoustic flow is further enhanced, and the energy is evenly distributed inside the acoustic enhancement cavity. The efficiency of mass transfer, heat exchange, and interaction / reaction of the processed materials is significantly improved.

[0015] To further optimize this technical solution, the acoustic enhancement system further includes:

[0016] Pressure control system and / or temperature control system;

[0017] The pressure control system is connected to the acoustic enhancement cavity through a pipeline to adjust the pressure in the acoustic enhancement cavity so that the absolute pressure in the acoustic enhancement cavity is between 1 kPa and 60 MPa;

[0018] The temperature control system is connected to the heat exchange interlayer provided on the acoustic enhancement cavity through a pipeline and is used for temperature control of the acoustic enhancement cavity.

[0019] Both pressure and temperature have a significant impact on the acoustic flow characteristics of the material being processed. Controlling the pressure within the acoustic enhancement chamber, on the one hand, affects the compressibility of the fluid within the chamber, effectively pre-compressing the fluid, thereby affecting the acoustic flow characteristics of the fluid within the chamber. On the other hand, it affects the interaction between solid particles and with the walls of the chamber. By regulating and controlling the pressure within the chamber, the effect of the chamber on the material being processed can be effectively controlled, achieving the desired effect on the material being processed. Temperature also affects the compressibility of the fluid within the chamber. Temperature also affects the viscosity of the fluid, affecting the flowability of the material being processed, and thus affecting the acoustic flow characteristics of the fluid within the chamber.

[0020] A further optimization of this technical solution is that the pressure control system is a vacuum system with controllable absolute pressure, with an absolute pressure adjustment range of 1 kPa to standard atmospheric pressure. The vacuum system can reduce the pressure of the gas inside the acoustic enhancement chamber to within the range of 1 kPa to standard atmospheric pressure, thereby reducing the interaction between the materials inside the acoustic enhancement chamber and between the materials and the walls of the acoustic enhancement chamber. The pressure is adjusted and controlled according to the required treatment level of different materials. Materials sensitive to force and heat, such as explosives, biologically active cells, or materials with special structures, can be processed at appropriate pressures within the range of 1 kPa to standard atmospheric pressure.

[0021] To further optimize the present technical solution, the pressure control system is a compressed air source equipped with a pressure regulating valve or a pressure reducing valve, and its absolute pressure adjustment range is standard atmospheric pressure-25MPa. The pressure of the gas inside the acoustic enhancement cavity can be adjusted by the compressed air source and the pressure regulating valve or the pressure reducing valve so that it is within the range of standard atmospheric pressure-25MPa, so as to enhance the interaction between the materials inside the acoustic enhancement cavity and between the materials and the wall surface of the acoustic enhancement cavity. The pressure is adjusted and controlled according to the degree of treatment required for different materials. The treatment of ultrafine materials that are prone to agglomeration, such as nanomaterials, can be carried out at a suitable pressure within the range of standard atmospheric pressure-25MPa. The compressed air source can use gases that participate in the reaction of the materials in the mixed enhancement cavity, such as oxygen or hydrogen, or can use inert argon or nitrogen. The pressure reducing valve or the pressure regulating valve can be manually adjusted or an automatic proportional valve, and closed-loop control and adjustment are performed with the control system.

[0022] To further optimize this technical solution, the compressed air source is equipped with a gas compressor. The compressed air source's own pressure decreases after use, requiring regular replenishment (pressure recharging). Using a gas compressor allows for on-demand replenishment, reducing the volume of the pressure tank and eliminating the need for offline replenishment (pressure recharging).

[0023] A further optimization of this technical solution involves a pressure control system comprising a liquid booster pump equipped with a pressure regulating valve or a pressure reducing valve, with an absolute pressure adjustment range of 0.01 MPa to 60 MPa. The booster pump and the pressure regulating valve or the pressure reducing valve can be used to adjust the pressure of the liquid within the acoustic enhancement chamber within the range of 0.01 MPa to 60 MPa, thereby enhancing the interaction between the materials within the acoustic enhancement chamber and between the materials and the chamber walls. Pressure adjustment and control are performed based on the degree of treatment required for each material. Ultrafine materials prone to agglomeration, such as nanomaterials, that require processing in a liquid environment can be processed at an appropriate pressure within the range of 0.01 MPa to 60 MPa.

[0024] A further optimization of this technical solution involves the pressure control system comprising at least two of the vacuum system, compressed air source, and liquid booster pump described in any one of claims 3-6. Multiple on-off valves are used to control the operation of one of these devices while the remaining devices are deactivated. To address complex process conditions, the pressure control system is configured based on the pressure and environment requirements of the acoustic enhancement chamber at different stages.

[0025] In a further refinement of this technical solution, the acoustic enhancement chamber includes a piston and a locking nut that slide along the cylindrical inner axis. The volume of the acoustic enhancement chamber is adjusted by moving the piston, and the locking nut rigidly secures the piston to the chamber. Adjusting the volume of the acoustic enhancement chamber via the piston allows for optimized interaction within the chamber and between the material and the chamber walls when processing smaller amounts of material, achieving optimal processing results.

[0026] To further optimize this technical solution, the piston is internally provided with a channel and connector for connecting the acoustic enhancement chamber to an external pipeline. Connecting this to a pressure control system further optimizes the treatment effect and can also be connected to other interfaces for feeding, discharging, temperature measurement, and pressure measurement.

[0027] A further optimization of this technical solution involves including an acoustic flow disruption blade within the acoustic enhancement chamber, rigidly fixed within the chamber. For some special materials, such as non-Newtonian fluids, the acoustic flow vortex structure within the acoustic enhancement chamber can be affected to a certain extent. By increasing the surface area within the acoustic enhancement chamber, the disruption blade can disrupt the acoustic flow distribution, re-forming a better acoustic flow structure and improving the efficiency of mass transfer, heat exchange, and interaction / reaction of the processed materials.

[0028] To further optimize this technical solution, the acoustic flow interference blade is in the shape of a disc or a stirring blade, and is located on the axis of the cylindrical inner cavity. Through experiments, the disc or stirring blade shape can produce a better interference effect, and the form is simple and low-cost.

[0029] Further optimizing the technical solution, the mechanical resonator is a three-mass vibration system, including a frame, mass one, mass two, mass three, spring one, spring two, spring three, spring four and an exciter;

[0030] Mass 1 is the vibration isolation stage, mass 2 is the driving stage, and mass 3 is the load stage. Mass 1 is connected to the frame via spring 1, mass 2 is connected to mass 1 via spring 2, mass 3 is connected to mass 1 via spring 3, and mass 2 and mass 3 are connected via spring 4. The exciter is rigidly fixed to mass 2, and mass 3 is rigidly fixed to the acoustic enhancement cavity, forming a mechanical resonance system. The three-mass vibration system can output high-acceleration vibrations under resonant conditions while reducing the vibration of the drive mechanism, protecting the drive mechanism and minimizing the force transmitted to the equipment foundation. The rotation of the eccentric mass generates centrifugal force. An eccentric mass assembly with an even number of eccentric masses (not less than 4) synthesizes an alternating excitation force that is in phase with the vibration velocity of the acoustic enhancement cavity, driving the mechanical resonance system to resonate and applying the excitation force almost entirely to the material within the acoustic enhancement cavity. Because the mechanical resonance system operates under resonant conditions, the material within the acoustic enhancement cavity is the sole external load to the system. While the material in the mechanical resonance system is an energy-consuming element, it also possesses mass properties. On the basis of a large number of experiments, the mass and damping of the material are correlated with the mass of the acoustic enhancement cavity and the mass of mass body three, and the following results are obtained: the ratio A1 of the sum of the mass of mass body three and the mass of the acoustic enhancement cavity to the mass of the material is 2-10 times; the ratio A2 of the sum of the mass of mass body two and the mass of the exciter to the sum of the mass of mass body three and the acoustic enhancement cavity is 2-10 times; the ratio A3 of the stiffness of spring two to the stiffness of spring three is 2-10 times. Under these conditions, the optimal parameters are obtained, and the total weight and system damping ratio of the resonance system composed of the mechanical resonator, acoustic enhancement cavity and material are optimized, ensuring that the mechanical resonance system can operate stably for a long time at a maximum vibration acceleration of 120g.

[0031] Further optimizing the technical solution, the mechanical resonator is a three-mass vibration system, comprising a frame, mass 1, mass 2, mass 3, spring 1, spring 2, spring 3, spring 4, and an exciter, wherein the exciter includes a magnet assembly and a coil assembly;

[0032] Mass one is the vibration isolation stage, mass two is the driving stage, and mass three is the load stage; mass one is connected to the frame through spring one, mass two is connected to mass one through spring two, mass three is connected to mass one through spring three, and mass two and mass three are connected through spring four; the magnet assembly is rigidly fixed on mass two, and the coil assembly is fixed on mass three, and can generate an interactive excitation force with the magnet assembly after alternating current is passed through; mass three is rigidly fixed to the acoustic enhancement cavity, and together they constitute a mechanical resonance system.

[0033] The three-mass vibration system outputs high-acceleration vibrations under resonant conditions while simultaneously reducing the vibration of the drive mechanism, protecting the drive mechanism and minimizing the forces transmitted to the equipment foundation. The exciter utilizes electromagnetic excitation. When an alternating current with the same phase as the vibration velocity of the acoustic enhancement cavity is applied, the alternating Ampere force exerted on the coil assembly within the magnetic field of the magnet assembly acts as the excitation force, driving the mechanical resonance system to resonate and applying the excitation force almost entirely to the material within the acoustic enhancement cavity. Because the mechanical resonance system operates under resonant conditions, the material within the acoustic enhancement cavity is the sole external load on the system. While the material dissipates energy within the mechanical resonance system, it also possesses mass properties. On the basis of a large number of experiments, the mass and damping of the material are correlated with the mass of the acoustic enhancement cavity and the mass of mass body three, and the following results are obtained: the ratio A1 of the sum of the mass of mass body three and the mass of the acoustic enhancement cavity to the mass of the material is 2-10 times, the ratio A2 of the sum of the mass of mass body two and the mass of the magnet assembly to the sum of the mass of mass body three, the coil assembly and the acoustic enhancement cavity is 2-10 times, and the ratio A3 of the stiffness of spring two to the stiffness of spring three is 2-10 times. Under these conditions, the optimal parameters are obtained, and the total weight and system damping ratio of the resonance system composed of the mechanical resonator, acoustic enhancement cavity and material are optimized, ensuring that the mechanical resonance system can operate stably for a long time at a maximum vibration acceleration of 120g.

[0034] Further optimizing the technical solution, the mechanical resonator is a three-mass vibration system, comprising a frame, mass one, mass two, mass three, spring one, spring two, spring three, spring four, and an exciter; the exciter comprises an exciting force component and a servo drive component, the exciting force component is an eccentric mass component containing an even number of eccentric masses not less than 4, and the servo drive component is a rotary servo motor;

[0035] Mass 1 is the vibration isolation stage, mass 2 is the drive stage, and mass 3 is the load stage. Mass 1 is connected to the frame via spring 1, mass 2 is connected to mass 1 via spring 2, mass 3 is connected to mass 1 via spring 3, and mass 2 and mass 3 are connected via spring 4. The excitation force assembly is rigidly fixed to mass 2, and the servo drive assembly is rigidly fixed to mass 1 and connected to the excitation force assembly via a flexible coupling, driving the eccentric mass to rotate and generate the excitation force. Mass 3 is rigidly fixed to the acoustic enhancement chamber, together forming a mechanical resonance system. The three-mass vibration system can output high acceleration vibration under resonant conditions while reducing the vibration of the drive mechanism, protecting the drive mechanism and minimizing the force transmitted to the equipment foundation. The rotation of the eccentric mass generates centrifugal force. The eccentric mass assembly, which has an even number of eccentric masses (no less than 4), synthesizes and outputs an alternating excitation force with the same phase as the vibration velocity of the acoustic enhancement chamber, driving the mechanical resonance system to resonate and applying the excitation force almost entirely to the material within the acoustic enhancement chamber. Because the mechanical resonance system operates under resonant conditions, the material in the acoustic enhancement cavity is the system's only external load. The material is an energy-consuming element in the mechanical resonance system, but it also has mass properties. Based on a large number of experiments, the mass and damping of the material are correlated with the mass of the acoustic enhancement cavity and mass body 3. The results show that: the ratio A1 of the sum of the mass of mass body 3 and the mass of the acoustic enhancement cavity to the mass of the material is 2-10 times; the ratio A2 of the sum of the mass of mass body 2 and the mass of the excitation force component to the sum of the mass of mass body 3 and the acoustic enhancement cavity is 2-10 times; and the ratio A3 of the stiffness of spring 2 to the stiffness of spring 3 is 2-10 times. Under these conditions, the optimal parameters are obtained, optimizing the total weight and system damping ratio of the resonance system composed of the mechanical resonator, acoustic enhancement cavity, and material, ensuring that the mechanical resonance system can operate stably for a long time at a maximum vibration acceleration of 120g.

[0036] Further optimizing the technical solution, the mechanical resonator is a multi-mass vibration system, comprising a frame, mass one, mass two, mass three, spring one, spring two, spring three, spring four, spring five, and an exciter; the exciter comprises an exciting force component and a servo drive component, the exciting force component is an eccentric mass component containing an even number of eccentric masses not less than 4, and the servo drive component is a rotary servo motor;

[0037] Mass 1 is the vibration isolation stage, mass 2 is the drive stage, and mass 3 is the load stage. Mass 1 is connected to the frame via spring 1, mass 2 is connected to mass 1 via spring 2, mass 3 is connected to mass 1 via spring 3, and mass 2 and mass 3 are connected via spring 4. The excitation force assembly is rigidly fixed to mass 2. The servo drive assembly is connected to the frame via spring 5 and to the excitation force assembly via a flexible coupling, driving the eccentric mass to rotate and generate the excitation force. Mass 3 is rigidly fixed to the acoustic enhancement chamber, forming a mechanical resonance system. The three-mass vibration system can output high acceleration vibration under resonant conditions while reducing the vibration of the drive mechanism, protecting the drive mechanism and minimizing the force transmitted to the equipment foundation. The rotation of the eccentric mass generates centrifugal force. The eccentric mass assembly, which has an even number of eccentric masses (no less than 4), synthesizes and outputs an alternating excitation force with the same phase as the vibration velocity of the acoustic enhancement chamber, driving the mechanical resonance system to resonate and applying the excitation force almost entirely to the material within the acoustic enhancement chamber. Because the mechanical resonance system operates under resonant conditions, the material in the acoustic enhancement cavity is the system's only external load. The material is an energy-consuming element in the mechanical resonance system, but it also has mass properties. Based on a large number of experiments, the mass and damping of the material are correlated with the mass of the acoustic enhancement cavity and mass body 3. The results show that: the ratio A1 of the sum of the mass of mass body 3 and the mass of the acoustic enhancement cavity to the mass of the material is 2-10 times; the ratio A2 of the sum of the mass of mass body 2 and the mass of the excitation force component to the sum of the mass of mass body 3 and the acoustic enhancement cavity is 2-10 times; and the ratio A3 of the stiffness of spring 2 to the stiffness of spring 3 is 2-10 times. Under these conditions, the optimal parameters are obtained, optimizing the total weight and system damping ratio of the resonance system composed of the mechanical resonator, acoustic enhancement cavity, and material, ensuring that the mechanical resonance system can operate stably for a long time at a maximum vibration acceleration of 120g.

[0038] To further optimize the technical solution, when the ratios A1, A2, and A3 are all equal, the performance of the resonance system composed of the mechanical resonator, the acoustic enhancement cavity, and the material is further optimized.

[0039] To further optimize this technical solution, the control method of the acoustic enhancement system is as follows:

[0040] Setting the excitation force intensity, adjusting the frequency to place the mechanical resonator in a resonant working condition, and adjusting the pressure and / or temperature of the acoustic enhancement cavity to achieve the desired vibration displacement / velocity / acceleration of the acoustic enhancement cavity;

[0041] The excitation force intensity is the excitation force generated by the exciter included in the mechanical resonator or an intensity value that is mathematically related to the excitation force and represents the magnitude of the excitation force.

[0042] To further optimize this technical solution, the control method of the acoustic enhancement system is as follows:

[0043] Setting the pressure and / or temperature of the acoustic enhancement chamber, adjusting the frequency to place the mechanical resonator in a resonant operating condition, and adjusting the intensity of the excitation force to achieve the desired vibration displacement / velocity / acceleration of the acoustic enhancement chamber;

[0044] The excitation force intensity is the excitation force generated by the exciter included in the mechanical resonator or an intensity value that is mathematically related to the excitation force and represents the magnitude of the excitation force.

[0045] An acoustic enhancement method, based on the above-mentioned acoustic enhancement system, implements the following steps:

[0046] The processed material is placed in the acoustic enhancement cavity, and the material filling volume rate is 50%-100%. Within this filling range, the interaction between the materials and between the materials and the wall of the acoustic enhancement cavity will be enhanced, preferably 90%-100%.

[0047] Adjust the frequency to bring the mechanical resonator into resonant operation. When the system is operating in a resonant state, the excitation force is almost completely transmitted to the material. Otherwise, part of the excitation force is used to balance the system's inertia and elastic forces, reducing system efficiency and making it impossible to control the force transmitted to the material, thus failing to ensure treatment results. This can be achieved by adjusting the frequency to align the phase of the excitation force with the vibration velocity of the acoustic enhancement chamber.

[0048] Adjust the intensity of the exciting force so that the vibration acceleration of the acoustic enhancement cavity reaches 10-150g, 1g = 9.8m / s 2 The excitation force intensity is the excitation force generated by the exciter included in the mechanical resonator, or an intensity value representing the magnitude of the excitation force that is mathematically related to the excitation force. The vibration acceleration is set based on the treatment purpose. Generally, a lower acceleration, preferably 10-40g, is used during the premixing stage, and 40-150g during the stabilization stage. Increasing the acceleration significantly enhances the interactions between materials and between materials and the walls of the acoustic enhancement chamber, significantly improving treatment efficiency.

[0049] An acoustic enhancement method, based on the above-mentioned acoustic enhancement system, implements the following steps:

[0050] The processed material is placed in the acoustic enhancement cavity, and the material filling volume ratio is 50%-100%. Within this filling range, the interaction between materials and between materials and the acoustic enhancement cavity wall will be enhanced, preferably 90%-100%.

[0051] Set the absolute pressure and / or temperature of the acoustic enhancement chamber, where the absolute pressure range of the acoustic enhancement chamber is 1kPa-60MPa. Setting the absolute pressure and / or temperature of the acoustic enhancement chamber can effectively control the interaction between materials and between materials and the walls of the acoustic enhancement chamber. Set the pressure or temperature according to the pressure or temperature required for material processing.

[0052] Adjust the frequency to bring the mechanical resonator into resonant operation. When the system is operating in a resonant state, the excitation force is almost completely transmitted to the material. Otherwise, part of the excitation force is used to balance the system's inertia and elastic forces, reducing system efficiency and making it impossible to control the force transmitted to the material, thus failing to ensure treatment results. This can be achieved by adjusting the frequency to align the phase of the excitation force with the vibration velocity of the acoustic enhancement chamber.

[0053] Adjust the intensity of the exciting force so that the vibration acceleration of the acoustic enhancement cavity reaches 10-150g, 1g = 9.8m / s 2 The excitation force intensity is the excitation force generated by the exciter included in the mechanical resonator, or an intensity value representing the magnitude of the excitation force that is mathematically related to the excitation force. The vibration acceleration is set based on the treatment purpose. Generally, a lower acceleration, preferably 10-40g, is used during the premixing stage, and 40-150g during the stabilization stage. Increasing the acceleration significantly enhances the interactions between materials and between materials and the walls of the acoustic enhancement chamber, significantly improving treatment efficiency.

[0054] An acoustic enhancement method, based on the above-mentioned acoustic enhancement system, implements the following steps:

[0055] The processed material is placed in the acoustic enhancement cavity, and the material filling volume rate is 50%-100%. Within this filling range, the interaction between the materials and between the materials and the wall of the acoustic enhancement cavity will be enhanced, preferably 90%-100%.

[0056] Set the excitation force intensity. This refers to the excitation force generated by the exciter included in the mechanical resonator, or a mathematically related value representing the magnitude of the excitation force. Setting the excitation force intensity effectively controls the interaction between materials and between materials and the walls of the acoustic enhancement cavity. Adjust the excitation force intensity based on the material processing requirements.

[0057] Adjust the frequency to bring the mechanical resonator into resonant operation. When the system is operating in a resonant state, the excitation force is almost completely transmitted to the material. Otherwise, part of the excitation force is used to balance the system's inertia and elastic forces, reducing system efficiency and making it impossible to control the force transmitted to the material, thus failing to ensure treatment results. This can be achieved by adjusting the frequency to align the phase of the excitation force with the vibration velocity of the acoustic enhancement chamber.

[0058] Adjust the absolute pressure and / or temperature of the acoustic enhancement chamber, where the absolute pressure range of the acoustic enhancement chamber is 1kPa-60MPa, so that the vibration acceleration of the acoustic enhancement chamber reaches 10-150g, 1g = 9.8m / s 2 The absolute pressure and / or temperature of the acoustic enhancement chamber are set according to the treatment purpose. Generally, a smaller acceleration, preferably 10-40g, is used in the premixing stage, and 40-150g is used in the stable treatment stage. As the acceleration increases, the interaction between materials and between materials and the walls of the acoustic enhancement chamber will be significantly enhanced, and the treatment efficiency will be significantly increased.

[0059] To further optimize this technical solution, in order to further enhance the effect on the material, grinding beads are added to the acoustic enhancement cavity, and the total filling volume ratio of the grinding beads and the material is 50%-100%; within this filling range, the interaction between the material and the material, the material and the wall of the acoustic enhancement cavity, and the material and the grinding beads will be enhanced, preferably 90%-100%.

[0060] To further optimize this technical solution, in some applications, a liquid solvent is further added to the acoustic enhancement cavity, and the amount of liquid solvent added is 50%-100% of the volume of the remaining space inside the acoustic enhancement cavity (including the space between solid particles); within this filling range, the interaction between the material and the material, the material and the wall of the acoustic enhancement cavity, and the material and the grinding beads will be enhanced, preferably 90%-100%.

[0061] To further optimize this technical solution, the particle size of the grinding beads is in the range of 0.01-2 mm. Smaller grinding bead particle size can enhance the fluidity of the material and ensure the overall acoustic flow characteristics of the material.

[0062] To further optimize the technical solution, in some applications, at least one processed material is rigidly fixedly connected to the acoustic enhancement cavity; the fixed material serves as a new acoustic enhancement cavity wall, interacting with other materials.

[0063] To further optimize the technical solution, the uses of the acoustic enhancement method include but are not limited to fluidization, mixing, dispersion, coating, grinding, crushing, emulsification, extraction, dissolution, and chemical reaction enhancement of raw materials.

[0064] Compared with the prior art, the present invention provides an acoustic enhancement system and method, which has the following beneficial effects:

[0065] 1. It can generate an acoustic flow structure with a single vortex, and the whole field movement and energy are evenly dispersed.

[0066] 2. The material filling volume rate is high, up to 100%, which significantly improves production capacity.

[0067] 3. Working under resonance conditions, the exciting force acts almost entirely on the material, and the quantification of the material action parameters is an important reference for optimizing the process.

[0068] 4. The interaction strength between materials, materials and the wall of the acoustic enhancement cavity, and materials and grinding beads can be adjusted and controlled, adapting to a wide range of materials.

[0069] 5. The total weight and system damping ratio of the resonance system composed of the mechanical resonator, acoustic reinforcement cavity, and materials have been optimized to ensure that the mechanical resonance system can operate stably for a long time at a maximum vibration acceleration of 120g.

[0070] 6. The acoustic enhancement method with the acoustic enhancement chamber pressure and / or temperature, exciting force intensity and vibration acceleration as the main parameters is suitable for the processing of raw materials for various purposes. BRIEF DESCRIPTION OF THE DRAWINGS

[0071] FIG1 is a schematic diagram of an acoustic enhancement system according to an embodiment of the present application;

[0072] FIG2 is a three-dimensional and planar schematic diagram of the first-order acoustic flow in the form of a polar axisymmetric single vortex distribution according to an embodiment of the present application;

[0073] FIG3 is a schematic diagram of a first-order acoustic flow plane outside the polar axisymmetric single vortex distribution form described in the embodiment of the present application;

[0074] FIG4 is a schematic diagram of a mechanical resonator structure according to an embodiment of the present application;

[0075] FIG5 is a schematic diagram of a mechanical resonator structure according to an embodiment of the present application;

[0076] FIG6 is a schematic diagram of a mechanical resonator structure according to an embodiment of the present application;

[0077] FIG7 is a schematic diagram of the structure of a mechanical resonator according to an embodiment of the present application;

[0078] FIG8 is a flow chart of an acoustic enhancement method according to an embodiment of the present application;

[0079] FIG9 is a flow chart of an acoustic enhancement method according to an embodiment of the present application.

[0080] In the figure: 1. Acoustic enhancement cavity; 2. Mechanical resonator; 201. Frame; 202. Mass one; 203. Mass two; 204. Mass three; 205. Spring one; 206. Spring two; 207. Spring three; 208. Spring four; 209. Exciter; 20901. Magnet assembly; 20911. Excitation force assembly; 20902. Coil assembly; 20912. Servo drive assembly; 210. Spring five; 3. Pressure control system; 4. Temperature control system. DETAILED DESCRIPTION

[0081] The following will be combined with the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the embodiments described are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0082] Example 1:

[0083] An acoustic enhancement system comprising:

[0084] The acoustic enhancement chamber 1 is used to accommodate the processed material and generate an acoustic flow movement with uniform energy distribution and controllable energy throughout the field.

[0085] The mechanical resonator 2 is used to couple the acoustic enhancement cavity 1 to produce mechanical resonance, generate strong vibration, and transmit the excitation energy directly and almost completely to the processed material.

[0086] The acoustic enhancement chamber 1 has a cylindrical inner cavity with a diameter D less than 1200 mm. Within this range, it can be infinitely small within the range of existing manufacturing technology, and there is no lower limit on the sample volume that can be processed. The ratio of the cylindrical inner cavity length L to the diameter D is in the range of 0.5-3, preferably 0.8-1.5. The bottom and top of the cylindrical inner cavity are both rounded, and the ratio of the rounded corner size R to the cylindrical inner cavity diameter D is in the range of 0.1-0.5, preferably 0.1-0.25 for materials with good fluidity, and preferably 0.25-0.5 for materials with poor fluidity or materials with high acoustic flow velocity requirements. The size and shape of the acoustic enhancement chamber 1 significantly affect the morphology of the first-order acoustic flow. The single acoustic flow morphology facilitates rapid mass transfer, heat transfer, and interaction / reaction between materials at different locations within the acoustic enhancement chamber 1. The acoustic enhancement cavity 1 can be made into a split type or an integrated type. When making a split type, the joint parts should be reliably sealed and pressure-resistant, and the joint surfaces should be smooth; when making an integrated type, automatic feeding and discharging pipe interfaces should be added.

[0087] The cylindrical inner cavity walls are all rigid walls with smooth surfaces and a surface roughness of not less than Ra3.2. They can be made of stainless steel. Materials with special requirements should be made of specific materials, but it is necessary to ensure that the container walls have a certain thickness or reinforced ribs to ensure sufficient rigidity. At the same time, in order to ensure wear resistance, the walls should also have a high hardness and can be surface hardened, such as spraying tungsten carbide or surface carburizing; the inner surface in contact with the material can be ground and polished to ensure the smoothness of the inner wall; insufficient wall rigidity and rough surface will lead to changes in the internal first-order acoustic flow morphology, and the rough surface will also increase energy consumption.

[0088] The cylindrical inner cavity is provided with a pipe interface connected to the outside, which can be used to increase the means of strengthening the process or for feeding or discharging materials or measuring temperature or pressure.

[0089] The acoustic enhancement cavity 1 is fixedly connected to the mechanical resonator 2 .

[0090] The mechanical resonator 2 is a multi-mass vibration system, which constitutes a mechanical resonance system with the acoustic enhancement cavity 1, and can make the acoustic enhancement cavity 1 generate mechanical resonance with a frequency in the range of 40Hz-80Hz and an amplitude in the range of 2mm-20mm in the axial direction of the cylindrical inner cavity. The multi-mass vibration system can output large acceleration vibration under resonance conditions while reducing the vibration of the drive mechanism, protecting the drive mechanism, and minimizing the force transmitted to the equipment foundation. The corresponding wavelength in the frequency range of 40Hz-80Hz can match the size of the acoustic enhancement cavity 1, and the vibration intensity (energy) when the amplitude reaches 2mm-20mm at this frequency is sufficient to generate the acoustic flow motion required for the material, and the maximum volume filling rate of the material can reach 100%. It is particularly noteworthy that when the mechanical resonator 2 works under resonance conditions, almost all of the input energy is transferred to the material, which is a key parameter of the material processing process.

[0091] After extensive testing with materials of varying densities, proportions, filling ratios, vibration frequencies, amplitudes, and acoustic enhancement chamber sizes and shapes, the acoustic enhancement system of the present invention has demonstrated that it effectively generates a first-order acoustic flow in the treated material in a polar-symmetrical, single-vortex distribution. All materials move within the same vortex, and energy continuously migrates from the first-order acoustic flow to higher-order acoustic flows. This further enhances the microvibration or compression effects of the higher-order acoustic flow, evenly distributing energy within the acoustic enhancement chamber. This significantly improves the efficiency of mass transfer, heat exchange, and interactions / reactions within the treated material. A schematic diagram of a first-order acoustic flow with a single-vortex distribution is shown in Figure 2, while a schematic diagram of a first-order acoustic flow with multiple-vortex distributions is shown in Figure 3.

[0092] Example 2:

[0093] As shown in FIG1 , an acoustic enhancement system, based on the first embodiment, further includes:

[0094] Pressure control system 3 and / or temperature control system 4;

[0095] The pressure control system 3 is connected to the acoustic enhancement chamber 1 through a pipeline and can adjust the pressure in the acoustic enhancement chamber 1 so that the absolute pressure in the acoustic enhancement chamber 1 is between 1 kPa and 60 MPa.

[0096] The temperature control system 4 is connected to the heat exchange interlayer provided on the acoustic enhancement cavity 1 through a pipeline, and is used for temperature control of the acoustic enhancement cavity 1 .

[0097] Both pressure and temperature have a significant impact on the acoustic flow characteristics of the material being processed. Controlling the internal pressure of the acoustic enhancement chamber 1 affects the compressibility of the fluid within the chamber, effectively pre-compressing it and thus affecting the acoustic flow characteristics of the fluid within the chamber. It also influences the interactions between solid particles and with the walls of the chamber. By regulating and controlling the internal pressure of the acoustic enhancement chamber 1, the effect of the chamber on the material being processed can be effectively controlled, achieving the desired effect on the material being processed. Temperature also affects the compressibility of the fluid within the chamber 1. Temperature also affects the viscosity of the fluid, affecting the flowability of the material being processed and thus the acoustic flow characteristics of the fluid within the chamber.

[0098] The pressure control system 3 is a vacuum system with controllable absolute pressure, with an absolute pressure adjustment range of 1 kPa to standard atmospheric pressure. This vacuum system reduces the pressure of the gas within the acoustic enhancement chamber 1 to within the range of 1 kPa to standard atmospheric pressure, thereby minimizing interactions between materials within the chamber 1 and between materials and the walls of the chamber 1. Pressure is adjusted and controlled based on the desired level of treatment required for each material. Materials sensitive to force or heat, such as explosives, biologically active cells, or materials with specialized structures, can be processed at pressures within the range of 1 kPa to standard atmospheric pressure.

[0099] The pressure control system 3 is a compressed air source equipped with a pressure regulating valve or a pressure reducing valve, with an absolute pressure adjustment range of standard atmospheric pressure to 25 MPa. The compressed air source and the pressure regulating valve or the pressure reducing valve can be used to adjust the pressure of the gas inside the acoustic enhancement chamber 1 to within the range of standard atmospheric pressure to 25 MPa, thereby enhancing the interaction between the materials inside the acoustic enhancement chamber 1 and between the materials and the walls of the acoustic enhancement chamber 1. The pressure is adjusted and controlled according to the degree of treatment required for different materials. Ultrafine materials that are prone to agglomeration, such as nanomaterials, can be treated at an appropriate pressure within the range of standard atmospheric pressure to 25 MPa. The compressed air source can be a gas that participates in the reaction of mixing the materials in the enhancement chamber, such as oxygen or hydrogen, or an inert gas such as argon or nitrogen. The pressure reducing valve or the pressure regulating valve can be manually adjusted or an automatic proportional valve, and closed-loop control and adjustment are performed with the control system.

[0100] The compressed gas source is equipped with a gas compressor. After use, the compressed gas source will reduce its own pressure, and it needs to be replenished (pressurized) regularly. However, the use of a gas compressor can achieve replenishment as needed, reducing the volume of the pressure tank and eliminating the step of offline replenishment (pressurization).

[0101] The pressure control system 3 is a liquid booster pump equipped with a pressure regulating valve or a pressure reducing valve, with an absolute pressure adjustment range of 0.01 MPa to 60 MPa. The booster pump and the pressure regulating valve or the pressure reducing valve adjust the pressure of the liquid within the acoustic enhancement chamber 1 to within the range of 0.01 MPa to 60 MPa, thereby enhancing the interaction between the materials within the acoustic enhancement chamber 1 and between the materials and the walls of the acoustic enhancement chamber 1. Pressure adjustment and control are performed based on the required degree of treatment for each material. Ultrafine materials prone to agglomeration, such as nanomaterials, that need to be processed in a liquid environment can be processed at a suitable pressure within the range of 0.01 MPa to 60 MPa.

[0102] The pressure control system 3 also includes the aforementioned absolute pressure-controllable vacuum system, a compressed air source equipped with a pressure-regulating or pressure-reducing valve, a gas compressor, a compressed air source equipped with a pressure-regulating or pressure-reducing valve, and a liquid booster pump equipped with a pressure-regulating or pressure-reducing valve. Multiple on-off valves control one of these valves to control the pressure in the acoustic enhancement chamber 1, while the remaining pressure control systems 3 are deactivated. To address complex process conditions, the pressure control system 3 is configured based on the pressure and environment required by the acoustic enhancement chamber 1 at different stages.

[0103] Example 3:

[0104] Acoustic enhancement chamber 1 includes a piston and a locking nut that slide along the cylindrical inner axis. The volume of acoustic enhancement chamber 1 can be adjusted by moving the piston, and the locking nut rigidly secures the piston to the acoustic enhancement chamber 1. Adjusting the volume of acoustic enhancement chamber 1 via the piston optimizes the interaction between the material within chamber 1 and between the material and the walls of chamber 1 when processing smaller amounts of material, achieving optimal processing results.

[0105] The piston is internally provided with a channel and a joint for connecting the acoustic enhancement chamber 1 to an external pipeline. Connecting it to the pressure control system 3 further optimizes the treatment effect; it can also be connected to other interfaces such as feeding, discharging, temperature measurement, and pressure measurement.

[0106] The acoustic enhancement chamber 1 includes an acoustic flow interference vane rigidly fixed within the chamber. For some special materials, such as non-Newtonian fluids, the acoustic flow vortex structure within the acoustic enhancement chamber 1 may be affected to a certain extent. By installing the interference vane within the acoustic enhancement chamber 1, the internal surface area of ​​the chamber is increased, disrupting the acoustic flow distribution and re-forming a better acoustic flow structure, thereby improving the efficiency of mass transfer, heat exchange, and interaction / reaction of the processed materials.

[0107] The acoustic flow interference blade is in the shape of a disc or a stirring blade, rigidly fixed inside the acoustic enhancement cavity 1 and located on the axis of the cylindrical cavity. Through experiments, the disc or stirring blade shape can produce a good interference effect, and the form is simple and low-cost.

[0108] Example 4:

[0109] As shown in Figure 5, the mechanical resonator 2 is a three-mass vibration system, including a frame 201, mass one 202, mass two 203, mass three 204, spring one 205, spring two 206, spring three 207, spring four 208, and an exciter 209; the exciter 209 includes an exciting force component 20911 and a servo drive component 20912. The exciting force component 20911 is an eccentric block component containing an even number of eccentric blocks of not less than 4, and the servo drive component 20912 is a rotary servo motor; mass one 202 is a vibration isolation stage, mass two 203 is a drive stage, and mass three 204 is a vibration isolation stage. Mass 3 204 is the load-bearing stage; mass 1 202 is connected to the frame 201 via spring 1 205, mass 2 203 is connected to mass 1 202 via spring 2 206, mass 3 204 is connected to mass 1 202 via spring 3 207, and mass 2 203 is connected to mass 3 204 via spring 4 208. The excitation force assembly 20911 and servo drive assembly 20912 are rigidly fixed to mass 2 203 and connected via a rigid coupling, driving the eccentric mass to rotate and generate the excitation force. Mass 3 204 is rigidly fixed to the acoustic enhancement cavity 1, together forming a mechanical resonance system. This three-mass vibration system can output high-acceleration vibrations under resonant conditions while reducing the vibration of the drive mechanism, protecting the drive mechanism and minimizing the force transmitted to the equipment foundation. The rotation of the eccentric mass generates centrifugal force. Through an eccentric mass assembly consisting of an even number of eccentric masses (no less than four), an alternating excitation force with the same phase as the vibration velocity of the acoustic enhancement cavity 1 is synthesized. This drives the mechanical resonance system to resonate and applies the excitation force almost entirely to the material within the acoustic enhancement cavity 1. Because the mechanical resonance system operates under resonant conditions, the material within the acoustic enhancement cavity 1 is the sole external load on the system. While the material dissipates energy within the mechanical resonance system, it also possesses mass properties. On the basis of a large number of experiments, the mass and damping of the material are correlated with the mass of the acoustic enhancement cavity 1 and the mass of the mass body 3 204, and the following results are obtained: the ratio A1 of the sum of the mass of the mass body 3 204 and the mass of the acoustic enhancement cavity 1 to the mass of the material is 2-10 times, the ratio A2 of the sum of the mass of the mass body 203 and the mass of the exciter 209 to the sum of the mass of the mass body 3 204 and the acoustic enhancement cavity 1 is 2-10 times, and the ratio A3 of the stiffness of the spring 2 206 to the stiffness of the spring 3 207 is 2-10 times. Under these conditions, the optimal parameters are obtained, and the total weight and system damping ratio of the resonance system composed of the mechanical resonator 2, the acoustic enhancement cavity 1 and the material are optimized, ensuring that the mechanical resonance system can operate stably for a long time at a maximum vibration acceleration of 120g.

[0110] As shown in FIG4 , the mechanical resonator 2 is a three-mass vibration system, comprising a frame 201, mass one 202, mass two 203, mass three 204, spring one 205, spring two 206, spring three 207, spring four 208, and an exciter 209; the exciter 209 comprises a magnet assembly 20901 and a coil assembly 20902; mass one 202 is a vibration isolation stage, mass two 203 is a driving stage, and mass three 204 is a load stage; mass one 202 is connected to the frame 201 via spring one 205, mass two is a driving stage, and mass three 204 is a load stage; Mass 203 is connected to mass 1 202 via spring 2 206, mass 3 204 is connected to mass 1 202 via spring 3 207, and mass 2 203 and mass 3 204 are connected via spring 4 208. The magnet assembly 20901 is rigidly fixed to mass 2 203, and the coil assembly 20902 is fixed to mass 3 204. When alternating current is applied, it generates an interactive excitation force with the magnet assembly 20901. Mass 3 204 is rigidly fixed to the acoustic enhancement cavity 1, together forming a mechanical resonance system. This three-mass vibration system can output high-acceleration vibration under resonant conditions while reducing the vibration of the drive mechanism, protecting the drive mechanism and minimizing the force transmitted to the device foundation. Exciter 209 employs electromagnetic excitation. When an alternating current with the same phase as the vibration velocity of acoustic enhancement chamber 1 is introduced, the alternating Ampere force exerted on coil assembly 20902 within the magnetic field of magnet assembly 20901 acts as the excitation force, driving the mechanical resonance system to resonate and applying the excitation force almost entirely to the material within acoustic enhancement chamber 1. Because the mechanical resonance system operates under resonant conditions, the material within acoustic enhancement chamber 1 is the sole external load on the system. While the material dissipates energy within the mechanical resonance system, it also possesses mass properties. Based on a large number of experiments, the mass and damping of the material are correlated with the mass of the acoustic enhancement cavity 1 and the mass of the mass body 3 204, and the following results are obtained: the ratio A1 of the sum of the mass of the mass body 3 204 and the mass of the acoustic enhancement cavity 1 to the mass of the material is 2-10 times; the ratio A2 of the sum of the mass of the mass body 203 and the mass of the magnet assembly 20901 to the sum of the mass of the mass body 3 204, the coil assembly 20902 and the acoustic enhancement cavity 1 is 2-10 times; the ratio A3 of the stiffness of the spring 2 206 to the stiffness of the spring 3 207 is 2-10 times. Under these conditions, the optimal parameters are obtained, and the total weight and system damping ratio of the resonance system composed of the mechanical resonator 2, the acoustic enhancement cavity 1 and the material are optimized, ensuring that the mechanical resonance system can operate stably for a long time at a maximum vibration acceleration of 120g.

[0111] As shown in FIG6 , the mechanical resonator 2 is a three-mass vibration system, comprising a frame 201, mass 1 202, mass 2 203, mass 3 204, spring 1 205, spring 2 206, spring 3 207, spring 4 208, and an exciter 209; the exciter 209 comprises an exciting force component 20911 and a servo drive component 20912, wherein the exciting force component 20911 is an eccentric block component containing an even number of eccentric blocks not less than 4, and the servo drive component 20912 is a rotary servo motor; mass 1 202 is a vibration isolation stage, mass 2 203 is a driving stage, and mass 3 204 is a load stage; Mass 1 202 is connected to the frame 201 via spring 1 205, mass 2 203 is connected to mass 1 202 via spring 2 206, mass 3 204 is connected to mass 1 202 via spring 3 207, and mass 2 203 and mass 3 204 are connected via spring 4 208. The excitation force assembly 20911 is rigidly fixed to mass 2 203, and the servo drive assembly 20912 is rigidly fixed to mass 1 202 and connected to the excitation force assembly 20911 via a flexible coupling, driving the eccentric mass to rotate and generate an excitation force. Mass 3 204 is rigidly fixed to the acoustic enhancement cavity 1, together forming a mechanical resonance system. This three-mass vibration system can output high acceleration vibration under resonant conditions while reducing the vibration of the drive mechanism, protecting the drive mechanism and minimizing the force transmitted to the equipment foundation. The rotation of the eccentric mass generates centrifugal force. Through an eccentric mass assembly consisting of an even number of eccentric masses (no less than four), an alternating excitation force with the same phase as the vibration velocity of the acoustic enhancement cavity 1 is synthesized. This drives the mechanical resonance system to resonate and applies the excitation force almost entirely to the material within the acoustic enhancement cavity 1. Because the mechanical resonance system operates under resonant conditions, the material within the acoustic enhancement cavity 1 is the sole external load on the system. While the material dissipates energy within the mechanical resonance system, it also possesses mass properties. On the basis of a large number of experiments, the mass and damping of the material are correlated with the mass of the acoustic enhancement cavity 1 and the mass of the mass body 3 204, and the following results are obtained: the ratio A1 of the sum of the mass of the mass body 3 204 and the mass of the acoustic enhancement cavity 1 to the mass of the material is 2-10 times; the ratio A2 of the sum of the mass of the mass body 203 and the mass of the exciting force component 20911 to the sum of the mass of the mass body 3 204 and the acoustic enhancement cavity 1 is 2-10 times; the ratio A3 of the stiffness of the spring 2 206 to the stiffness of the spring 3 207 is 2-10 times. Under these conditions, the optimal parameters are obtained, and the total weight and system damping ratio of the resonance system composed of the mechanical resonator 2, the acoustic enhancement cavity 1 and the material are optimized, ensuring that the mechanical resonance system can operate stably for a long time at a maximum vibration acceleration of 120g.

[0112] As shown in FIG7 , the mechanical resonator 2 is a multi-mass vibration system, comprising a frame 201, mass 1 202, mass 2 203, mass 3 204, spring 1 205, spring 2 206, spring 3 207, spring 4 208, spring 5 210, and an exciter 209; the exciter 209 comprises an exciting force component 20911 and a servo drive component 20912. The exciting force component 20911 is an even number of eccentric blocks not less than 4. Eccentric block assembly, the servo drive assembly 20912 is a rotary servo motor; mass one 202 is the vibration isolation stage, mass two 203 is the drive stage, and mass three 204 is the load stage; mass one 202 is connected to the frame 201 through spring one 205, mass two 203 is connected to mass one 202 through spring two 206, mass three 204 is connected to mass one 202 through spring three 207, and mass two 203 is connected to mass three 204 through spring four 208; the exciting force assembly 20911 is rigidly fixed on mass two 203; the servo drive assembly 20912 is connected to the frame 201 through spring five 210, and is connected to the exciting force assembly 20911 through a flexible coupling, which can drive the eccentric block to rotate and generate exciting force; mass three 204 is rigidly fixed to the acoustic enhancement cavity 1, together forming a mechanical resonance system. The three-mass vibration system delivers high-acceleration vibrations under resonant conditions while simultaneously reducing the vibration of the drive mechanism, protecting it and minimizing the forces transmitted to the equipment foundation. The rotation of the eccentric mass generates centrifugal force. Through an eccentric mass assembly consisting of an even number of eccentric masses (at least four), an alternating excitation force is synthesized, in phase with the vibration velocity of the acoustic enhancement chamber 1. This drives the mechanical resonance system into resonance and applies the excitation force almost entirely to the material within the acoustic enhancement chamber 1. Because the mechanical resonance system operates under resonant conditions, the material within the acoustic enhancement chamber 1 is the sole external load on the system. While the material dissipates energy within the mechanical resonance system, it also possesses mass properties. On the basis of a large number of experiments, the mass and damping of the material are correlated with the mass of the acoustic enhancement cavity 1 and the mass of the mass body 3 204, and the following results are obtained: the ratio A1 of the sum of the mass of the mass body 3 204 and the mass of the acoustic enhancement cavity 1 to the mass of the material is 2-10 times; the ratio A2 of the sum of the mass of the mass body 203 and the mass of the exciting force component 20911 to the sum of the mass of the mass body 3 204 and the acoustic enhancement cavity 1 is 2-10 times; the ratio A3 of the stiffness of the spring 2 206 to the stiffness of the spring 3 207 is 2-10 times. Under these conditions, the optimal parameters are obtained, and the total weight and system damping ratio of the resonance system composed of the mechanical resonator 2, the acoustic enhancement cavity 1 and the material are optimized, ensuring that the mechanical resonance system can operate stably for a long time at a maximum vibration acceleration of 120g.

[0113] The above-mentioned method of synthesizing the exciting force by using an even number of eccentric blocks not less than 4 can be carried out according to a mature method. The number of eccentric blocks can be 4 or 6 or 8 or more, which are placed symmetrically, as shown in FIG5 . The symmetrical positions on both sides form a group, and the eccentric blocks in the group are installed in opposite directions. The positions of the eccentric blocks are symmetrical, and the horizontal exciting forces are offset, and only the vertical exciting forces are synthesized. By controlling the synthesis of the vertical exciting forces between the groups, the size of the final synthesized exciting force can be adjusted.

[0114] When the ratios A1, A2, and A3 are equal, the performance of the resonant system composed of the mechanical resonator 2, acoustic enhancement cavity 1, and material is further optimized. To reduce overall weight, A1, A2, and A3 are preferably 2-5. To improve stability, A1, A2, and A3 are preferably 5-10.

[0115] The control method for the aforementioned acoustic enhancement system involves setting the excitation force intensity, adjusting the frequency to place the mechanical resonator 2 in a resonant operating condition, and adjusting the pressure and / or temperature of the acoustic enhancement chamber 1 to achieve the desired vibration displacement / velocity / acceleration of the acoustic enhancement chamber 1. For some materials, the excitation force intensity is the dominant factor influencing the interaction between materials and between materials and the walls of the acoustic enhancement chamber 1. The vibration displacement / velocity / acceleration of the acoustic enhancement chamber 1 can be adjusted by setting the excitation force intensity and adjusting the pressure and / or temperature. The excitation force intensity is the excitation force generated by the exciter 209 included in the mechanical resonator 2, or an intensity value representing the magnitude of the excitation force that is mathematically related to the excitation force.

[0116] The control method for the above-mentioned acoustic enhancement system involves setting the pressure and / or temperature of the acoustic enhancement chamber 1, adjusting the frequency to place the mechanical resonator 2 in a resonant operating condition, and adjusting the excitation force intensity to achieve the desired vibration displacement / velocity / acceleration of the acoustic enhancement chamber 1. For some materials, the pressure and / or temperature of the acoustic enhancement chamber 1 are the dominant factors affecting the interaction between materials and between materials and the walls of the acoustic enhancement chamber 1. The vibration displacement / velocity / acceleration of the acoustic enhancement chamber 1 can be adjusted by setting the pressure and / or temperature of the acoustic enhancement chamber 1 and adjusting the excitation force intensity. The excitation force intensity is the excitation force generated by the exciter 209 included in the mechanical resonator 2, or an intensity value representing the magnitude of the excitation force that is mathematically related to the excitation force.

[0117] Embodiment 5:

[0118] An acoustic enhancement method, comprising performing the following steps on the above-mentioned acoustic enhancement system:

[0119] The material to be processed is placed in the acoustic enhancement chamber 1, and the material filling volume ratio is 50%-100%. Within this filling range, the interaction between the materials and between the materials and the wall surface of the acoustic enhancement chamber 1 will be enhanced, preferably 90%-100%. This can further increase the frequency and intensity of the interaction between the materials and between the materials and the wall surface of the acoustic enhancement chamber 1, further enhancing the treatment process.

[0120] Adjust the frequency to bring the mechanical resonator 2 into resonant operation. When the system is operating in this resonant state, the excitation force is almost completely transmitted to the material. Otherwise, part of the excitation force is used to balance the system's inertia and elastic forces, reducing system efficiency and making it impossible to control the force transmitted to the material, thus failing to ensure effective treatment. The frequency is adjusted to align the phase of the excitation force with the vibration velocity of the acoustic enhancement chamber 1.

[0121] Adjust the intensity of the exciting force so that the vibration acceleration of the acoustic enhancement cavity 1 reaches 10-150g, 1g = 9.8m / s 2 The excitation force intensity is the excitation force generated by the exciter 209 included in the mechanical resonator 2, or an intensity value that is mathematically related to the excitation force and represents the magnitude of the excitation force. The vibration acceleration is set based on the treatment purpose. Generally, a lower acceleration, preferably 10-40g, is used in the premixing stage, and 40-150g is used in the stabilization stage. As the acceleration increases, the interaction between materials and between materials and the walls of the acoustic enhancement chamber 1 will be significantly enhanced, and the treatment efficiency will be significantly increased. The time required for the premixing and stabilization stages is directly related to the vibration acceleration, excitation force intensity, pressure, and / or temperature. The specific time required for different types of materials can be determined through several experiments.

[0122] The uses of the above-mentioned acoustic enhancement method include, but are not limited to, fluidization, mixing, dispersion, coating, grinding, crushing, emulsification, extraction, dissolution, and chemical reaction enhancement of raw materials.

[0123] Example 6:

[0124] As shown in FIG8 , an acoustic enhancement method is implemented on the above-mentioned acoustic enhancement system by performing the following steps:

[0125] The material to be processed is placed in the acoustic enhancement chamber 1, and the material filling volume ratio is 50%-100%. Within this filling range, the interaction between the materials and between the materials and the wall surface of the acoustic enhancement chamber 1 will be enhanced, preferably 90%-100%. This can further increase the frequency and intensity of the interaction between the materials and between the materials and the wall surface of the acoustic enhancement chamber 1, further enhancing the treatment process.

[0126] The absolute pressure and / or temperature of the acoustic enhancement chamber 1 is set, wherein the absolute pressure range of the acoustic enhancement chamber 1 is 1 kPa-60 MPa. Setting the absolute pressure and / or temperature of the acoustic enhancement chamber 1 can effectively control the interaction between materials and between materials and the wall of the acoustic enhancement chamber 1. The pressure or temperature is set according to the pressure or temperature required for material processing.

[0127] Adjust the frequency to bring the mechanical resonator 2 into resonant operation. When the system is operating in this resonant state, the excitation force is almost completely transmitted to the material. Otherwise, part of the excitation force is used to balance the system's inertia and elastic forces, reducing system efficiency and making it impossible to control the force transmitted to the material, thus failing to ensure effective treatment. The frequency is adjusted to align the phase of the excitation force with the vibration velocity of the acoustic enhancement chamber 1.

[0128] Adjust the intensity of the exciting force so that the vibration acceleration of the acoustic enhancement cavity 1 reaches 10-150g, 1g = 9.8m / s 2 The excitation force intensity is the excitation force generated by the exciter 209 included in the mechanical resonator 2, or an intensity value that is mathematically related to the excitation force and represents the magnitude of the excitation force. The vibration acceleration is set based on the treatment purpose. Generally, a lower acceleration, preferably 10-40g, is used in the premixing stage, and 40-150g is used in the stabilization stage. As the acceleration increases, the interaction between materials and between materials and the walls of the acoustic enhancement chamber 1 will be significantly enhanced, and the treatment efficiency will be significantly increased. The time required for the premixing and stabilization stages is directly related to the vibration acceleration, excitation force intensity, pressure, and / or temperature. The specific time required for different types of materials can be determined through several experiments.

[0129] The uses of the above-mentioned acoustic enhancement method include, but are not limited to, fluidization, mixing, dispersion, coating, grinding, crushing, emulsification, extraction, dissolution, and chemical reaction enhancement of raw materials.

[0130] Embodiment seven:

[0131] As shown in FIG9 , an acoustic enhancement method is implemented on the above-mentioned acoustic enhancement system by performing the following steps:

[0132] The processed material is placed in the acoustic enhancement cavity 1, and the material filling volume rate is 50%-100%. Within this filling range, the interaction between the materials and between the materials and the wall of the acoustic enhancement cavity 1 will be enhanced, preferably 90%-100%.

[0133] Set the excitation force intensity. The excitation force intensity is the excitation force generated by the exciter 209 included in the mechanical resonator 2, or a value representing the magnitude of the excitation force that is mathematically related to the excitation force. Setting the excitation force intensity effectively controls the interactions between materials and between materials and the walls of the acoustic enhancement chamber 1. The excitation force intensity should be set based on the material processing requirements.

[0134] Adjust the frequency to bring the mechanical resonator 2 into resonant operation. When the system is operating in this resonant state, the excitation force is almost completely transmitted to the material. Otherwise, part of the excitation force is used to balance the system's inertia and elastic forces, reducing system efficiency and making it impossible to control the force transmitted to the material, thus failing to ensure effective treatment. The frequency is adjusted to align the phase of the excitation force with the vibration velocity of the acoustic enhancement chamber 1.

[0135] Adjust the absolute pressure and / or temperature of the acoustic enhancement chamber 1, wherein the absolute pressure range of the acoustic enhancement chamber 1 is 1kPa-60MPa, so that the vibration acceleration of the acoustic enhancement chamber 1 reaches 10-150g, 1g = 9.8m / s 2 The absolute pressure and / or temperature of acoustic enhancement chamber 1 are set based on the treatment objectives. Generally, a lower acceleration, preferably 10-40g, is used during the premixing phase, and 40-150g during the stabilization phase. Increasing the acceleration significantly enhances the interactions between materials and between materials and the walls of acoustic enhancement chamber 1, significantly increasing treatment efficiency. The time required for the premixing and stabilization phases is directly related to the vibration acceleration, excitation force intensity, pressure, and / or temperature. This can be determined through trial and error for different materials.

[0136] The uses of the above-mentioned acoustic enhancement method include, but are not limited to, fluidization, mixing, dispersion, coating, grinding, crushing, emulsification, extraction, dissolution, and chemical reaction enhancement of raw materials.

[0137] Embodiment 8:

[0138] In order to further enhance the effect on the material, grinding beads are also added to the acoustic enhancement chamber 1, and the total filling volume ratio of the grinding beads and the material is 50%-100%. Within this filling range, the interaction between the material and the material, the material and the wall of the acoustic enhancement chamber 1, and the material and the grinding beads will be enhanced, preferably 90%-100%.

[0139] In some applications, a liquid solvent is further added to the acoustic enhancement cavity 1 , and the amount of liquid solvent added is 50%-100% of the volume of the remaining space inside the acoustic enhancement cavity 1 (including the interstitial space between solid particles); within this filling range, the interaction between materials and materials, materials and the walls of the acoustic enhancement cavity 1 , and materials and grinding beads will be enhanced, preferably 90%-100%.

[0140] The particle size of the grinding beads is in the range of 0.01-2mm. The smaller particle size of the grinding beads can enhance the fluidity of the material and ensure the overall acoustic flow characteristics of the material.

[0141] In some applications, at least one processed material is rigidly fixed to the acoustic enhancement cavity 1 ; the fixed material serves as a new wall surface of the acoustic enhancement cavity 1 and interacts with other materials.

[0142] The uses of the above-mentioned acoustic enhancement method include, but are not limited to, fluidization, mixing, dispersion, coating, grinding, crushing, emulsification, extraction, dissolution, and chemical reaction enhancement of raw materials.

[0143] The beneficial effects of the present invention are:

[0144] 1. It can generate an acoustic flow structure with a single vortex, and the whole field movement and energy are evenly dispersed.

[0145] 2. The material filling volume rate is high, up to 100%, which significantly improves production capacity.

[0146] 3. Working under resonance conditions, the exciting force acts almost entirely on the material, and the quantification of the material action parameters is an important reference for optimizing the process.

[0147] 4. The interaction strength between materials, materials and the wall of the acoustic enhancement cavity, and materials and grinding beads can be adjusted and controlled, adapting to a wide range of materials.

[0148] 5. The total weight and system damping ratio of the resonance system composed of the mechanical resonator, acoustic reinforcement cavity, and materials have been optimized to ensure that the mechanical resonance system can operate stably for a long time at a maximum vibration acceleration of 120g.

[0149] 6. The acoustic enhancement method with the acoustic enhancement chamber pressure and / or temperature, exciting force intensity and vibration acceleration as the main parameters is suitable for the processing of raw materials for various purposes.

[0150] In the description of this application and its embodiments, it should be understood that the terms "top," "bottom," "height," and the like, indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings and are intended only to facilitate the description of this application and simplify the description. They do not indicate or imply that the devices or components referred to must have a specific orientation, be constructed, or operate in a specific orientation. Therefore, they should not be construed as limiting this application. In this application and its embodiments, unless otherwise expressly specified or limited, the terms "disposed," "installed," "connected," "connected," and "fixed" should be understood in a broad sense. For example, they can refer to fixed connections, detachable connections, or integration; mechanical connections, electrical connections, or communication; direct connections, indirect connections through an intermediate medium, internal connections between two components, or interactions between two components. A person of ordinary skill in the art can understand the specific meanings of the above terms in this application based on the specific circumstances. In this application and its embodiments, unless otherwise expressly specified or limited, a first feature being "above" or "below" a second feature can include the first and second features being in direct contact, or the first and second features not being in direct contact but contacting through another feature between them. Moreover, a first feature being "above", "above" and "above" a second feature includes the first feature being directly above and diagonally above the second feature, or simply means that the first feature is at a higher level than the second feature. A first feature being "below", "below" and "below" a second feature includes the first feature being directly above and diagonally above the second feature, or simply means that the first feature is at a lower level than the second feature. The above disclosure provides many different embodiments or examples for implementing different structures or methods of the present application. In order to simplify the disclosure of the present application, the components and settings of specific examples are described above. Of course, they are merely examples and are not intended to limit the present application. In addition, the present application may repeat reference numbers and / or reference letters in different examples. Such repetition is for the purpose of simplicity and clarity and does not itself indicate the relationship between the various embodiments and / or settings discussed.

[0151] Although preferred embodiments of the present application have been described, those skilled in the art may make additional changes and modifications to these embodiments once they are aware of the basic inventive concepts. Therefore, the appended claims are intended to be interpreted as including the preferred embodiments and all changes and modifications that fall within the scope of this application. Obviously, those skilled in the art may make various changes and modifications to this application without departing from the spirit and scope of this application. Thus, if such changes and modifications fall within the scope of the claims of this application and their equivalents, then this application is intended to include such changes and modifications.

Claims

1. An acoustic enhancement system, characterized in that, Comprising: An acoustic enhancement cavity; A mechanical resonator; The acoustic enhancement cavity is fixedly connected to the mechanical resonator; The acoustic enhancement cavity includes a cylindrical inner cavity, the diameter D of the cylindrical inner cavity is less than 1200 mm, the ratio of the length L to the diameter D of the cylindrical inner cavity is in the range of 0.5 - 3, both the bottom and the top of the cylindrical inner cavity are provided with rounded corners, the ratio of the size R of the rounded corners to the diameter D of the cylindrical inner cavity is in the range of 0.1 - 0.5; the wall surface of the cylindrical inner cavity is a rigid wall surface and is smooth, and the surface roughness is not less than Ra3.2; the cylindrical inner cavity is provided with a pipeline interface for external connection; The mechanical resonator is a multi - mass vibration system, and the mechanical resonator and the acoustic enhancement cavity form a mechanical resonance system, so that the acoustic enhancement cavity generates mechanical resonance in the axial direction of the cylindrical inner cavity with a frequency in the range of 40 Hz - 80 Hz and an amplitude in the range of 2 mm - 20 mm.

2. An acoustic enhancement system according to claim 1, wherein The acoustic enhancement system further includes: A pressure control system and / or a temperature control system; The pressure control system is connected to the acoustic enhancement cavity through a pipeline to adjust the pressure in the acoustic enhancement cavity, so that the absolute pressure in the acoustic enhancement cavity is between 1 kPa and 60 MPa; The temperature control system is connected to a heat exchange sandwich layer provided on the acoustic enhancement cavity through a pipeline for temperature control of the acoustic enhancement cavity.

3. An acoustic enhancement system according to claim 2, characterized in that, The pressure control system is a vacuum system with controllable absolute pressure, and its absolute pressure adjustment range is 1 kPa - standard atmospheric pressure.

4. An acoustic enhancement system according to claim 2, wherein The pressure control system is a compressed gas source configured with a pressure regulating valve or a pressure reducing valve, and its absolute pressure adjustment range is standard atmospheric pressure - 25 MPa.

5. An acoustic enhancement system according to claim 4, characterized in that, The compressed gas source is configured with a gas compressor.

6. An acoustic enhancement system according to claim 2, characterized in that, The pressure control system is a liquid booster pump configured with a pressure regulating valve or a pressure reducing valve, and its absolute pressure adjustment range is 0.01 Mpa - 60 MPa.

7. An acoustic enhancement system according to claim 2, wherein The pressure control system simultaneously has at least two of the vacuum system, the compressed gas source and the liquid booster pump described in any one of claims 3 - 6, and controls one of the devices to work through multiple switching valves, and the rest of the devices stop working.

8. An acoustic enhancement system according to any one of claims 1-7, characterized in that, The acoustic enhancement cavity includes a piston and a locking nut that slide along the axial direction of the cylindrical inner cavity. The volume of the acoustic enhancement cavity is adjusted by moving the piston, and the piston is rigidly and fixedly connected to the acoustic enhancement cavity through the locking nut.

9. An acoustic enhancement system according to claim 8, wherein A channel and a joint are provided inside the piston for connecting the acoustic enhancement cavity to an external pipeline.

10. An acoustic enhancement system according to any one of claims 1-9, characterized in that, The acoustic enhancement cavity contains acoustic flow motion interference vanes, and the acoustic flow motion interference vanes are rigidly fixed inside the acoustic enhancement cavity.

11. An acoustic enhancement system according to claim 10, characterized in that, The acoustic flow motion interference vanes are in the shape of a disc or a stirring paddle, and the acoustic flow motion interference vanes are located on the axis of the cylindrical inner cavity.

12. An acoustic enhancement system according to any one of claims 1-11, characterized in that, The mechanical resonator is a three - mass vibration system, including a frame, mass one, mass two, mass three, spring one, spring two, spring three, spring four, and an exciter; Mass one is an isolation stage, mass two is a driving stage, and mass three is a load stage; mass one is connected by a spring One is connected to the frame. The second mass body is connected to the first mass body through the second spring. The third mass body is connected to the first mass body through the third spring. The second mass body and the third mass body are connected through the fourth spring. The vibrator is rigidly fixed on the second mass body. The third mass body is rigidly fixed to the acoustic enhancement cavity, jointly constituting a mechanical resonance system. The ratio A1 of the sum of the mass of the third mass body and the mass of the acoustic enhancement cavity to the mass of the material is 2 - 10 times. The ratio A2 of the sum of the mass of the second mass body and the mass of the vibrator to the sum of the mass of the third mass body and the mass of the acoustic enhancement cavity is 2 - 10 times. The ratio A3 of the stiffness of the second spring to the stiffness of the third spring is 2 - 10 times.

13. An acoustic enhancement system according to any one of claims 1-11, characterized in that, The mechanical resonator is a three-mass-body vibration system, including a frame, a first mass body, a second mass body, a third mass body, a first spring, a second spring, a third spring, a fourth spring, and a vibrator. The vibrator includes a magnet assembly and a coil assembly. The first mass body is an isolation stage, the second mass body is a driving stage, and the third mass body is a load stage. The first mass body is connected to the frame through the first spring. The second mass body is connected to the first mass body through the second spring. The third mass body is connected to the first mass body through the third spring. The second mass body and the third mass body are connected through the fourth spring. The magnet assembly is rigidly fixed on the second mass body. The coil assembly is fixed on the third mass body. After alternating current is passed through, an exciting force that can interact with the magnet assembly is generated. The third mass body is rigidly fixed to the acoustic enhancement cavity, jointly constituting a mechanical resonance system. The ratio A1 of the sum of the mass of the third mass body and the mass of the acoustic enhancement cavity to the mass of the material is 2 - 10 times. The ratio A2 of the sum of the mass of the second mass body and the mass of the magnet assembly to the sum of the mass of the third mass body, the mass of the coil assembly, and the mass of the acoustic enhancement cavity is 2 - 10 times. The ratio A3 of the stiffness of the second spring to the stiffness of the third spring is 2 - 10 times.

14. An acoustic enhancement system according to any one of claims 1-11, characterized in that, The mechanical resonator is a three-mass-body vibration system, including a frame, a first mass body, a second mass body, a third mass body, a first spring, a second spring, a third spring, a fourth spring, and a vibrator. The vibrator includes an exciting force assembly and a servo drive assembly. The exciting force assembly is an eccentric block assembly containing an even number of eccentric blocks not less than 4. The servo drive assembly is a rotary servo motor. The first mass body is an isolation stage, the second mass body is a driving stage, and the third mass body is a load stage. The first mass body is connected to the frame through the first spring. The second mass body is connected to the first mass body through the second spring. The third mass body is connected to the first mass body through the third spring. The second mass body and the third mass body are connected through the fourth spring. The exciting force assembly is rigidly fixed on the second mass body. The servo drive assembly is rigidly fixed on the first mass body and is connected to the exciting force assembly through a flexible coupling, and can drive the eccentric block to rotate to generate an exciting force. The third mass body is rigidly fixed to the acoustic enhancement cavity, jointly constituting a mechanical resonance system. The ratio A1 of the sum of the mass of the third mass body and the mass of the acoustic enhancement cavity to the mass of the material is 2 - 10 times. The ratio A2 of the sum of the mass of the second mass body and the mass of the exciting force assembly to the sum of the mass of the third mass body and the mass of the acoustic enhancement cavity is 2 - 10 times. The ratio A3 of the stiffness of the second spring to the stiffness of the third spring is 2 - 10 times.

15. An acoustic enhancement system according to any one of claims 1-11, characterized in that, The mechanical resonator is a multi-mass vibration system, including a frame, mass one, mass two, mass three, spring one, spring two, spring three, spring four, spring five, and an exciter; the exciter includes an exciting force component and a servo drive component, the exciting force component is an eccentric block component containing an even number of eccentric blocks not less than 4, and the servo drive component is a rotary servo motor; Mass one is the vibration isolation stage, mass two is the drive stage, and mass three is the load stage; mass one is connected to the frame through spring one, mass two is connected to mass one through spring two, mass three is connected to mass one through spring three, and mass two and mass three are connected through spring four; the exciting force component is rigidly fixed on mass two; the servo drive component is connected to the frame through spring five and is connected to the exciting force component through a flexible coupling, and can drive the eccentric block to rotate to generate an exciting force; mass three is rigidly fixed to the acoustic strengthening cavity to jointly form a mechanical resonance system; The ratio A1 of the sum of the mass of mass three and the mass of the acoustic strengthening cavity to the material mass is 2 - 10 times; the ratio A2 of the sum of the mass of mass two and the mass of the exciting force component to the sum of the mass of mass three and the mass of the acoustic strengthening cavity is 2 - 10 times; the ratio A3 of the stiffness of spring two to the stiffness of spring three is 2 - 10 times.

16. An acoustic enhancement system according to any one of claims 12-15, characterized in that, The ratios A1, A2, and A3 are all equal.

17. An acoustic enhancement system according to any one of claims 1-16, characterized in that, The control method of the acoustic strengthening system is as follows: Set the exciting force intensity, make the mechanical resonator in the resonance working condition by adjusting the frequency, and adjust the pressure and / or temperature of the acoustic strengthening cavity to make the vibration displacement / velocity / acceleration of the acoustic strengthening cavity reach the expected value; The exciting force intensity is the exciting force generated by the exciter included in the mechanical resonator or the intensity value that has a mathematical relationship with the exciting force and represents the magnitude of the exciting force.

18. An acoustic enhancement system according to any one of claims 1-16, characterized in that, The control method of the acoustic strengthening system is as follows: Set the pressure and / or temperature of the acoustic strengthening cavity, make the mechanical resonator in the resonance working condition by adjusting the frequency, and adjust the exciting force intensity to make the vibration displacement / velocity / acceleration of the acoustic strengthening cavity reach the expected value; The exciting force intensity is the exciting force generated by the exciter included in the mechanical resonator or the intensity value that has a mathematical relationship with the exciting force and represents the magnitude of the exciting force.

19. An acoustic strengthening method, based on the acoustic strengthening system described in claim 1, implementing the following steps: Place the material to be processed in the acoustic strengthening cavity, and the material filling volume ratio is 50% - 100%; Adjust the frequency to make the mechanical resonator in the resonance working condition; Adjust the excitation force intensity so that the vibration acceleration of the acoustic strengthening cavity reaches 10 - 150 g, where 1 g = 9.8 m / s 2 , and the excitation force intensity is the excitation force generated by the exciter included in the mechanical resonator or the intensity value that has a mathematical relationship with the excitation force and represents the magnitude of the excitation force.

20. An acoustic strengthening method, based on the acoustic strengthening system described in any one of claims 2 - 18, implementing the following steps: Place the material to be processed in the acoustic strengthening cavity, and the material filling volume ratio is 50% - 100%; Set the absolute pressure and / or temperature of the acoustic strengthening cavity, where the absolute pressure range of the acoustic strengthening cavity is 1 kPa - 60 MPa; Adjust the frequency to make the mechanical resonator in the resonance working condition; Adjust the excitation force intensity so that the vibration acceleration of the acoustic enhancement cavity reaches 10 - 150 g, where 1 g = 9.8 m / s² 2 , and the excitation force intensity is the excitation force generated by the exciter included in the mechanical resonator or the intensity value that has a mathematical relationship with the excitation force and represents the magnitude of the excitation force.

21. An acoustic strengthening method, based on the acoustic strengthening system described in any one of claims 2 - 18, implementing the following steps: Place the material to be processed in the acoustic strengthening cavity, and the material filling volume ratio is 50% - 100%; Set the excitation force intensity, where the excitation force intensity is the excitation force generated by the exciter included in the mechanical resonator or an intensity value representing the magnitude of the excitation force that has a mathematical relationship with the excitation force; Adjust the frequency to make the mechanical resonator operate under resonance conditions; Adjust the absolute pressure and / or temperature of the acoustic enhancement cavity, where the absolute pressure range of the acoustic enhancement cavity is 1 kPa - 60 MPa, so that the vibration acceleration of the acoustic enhancement cavity reaches 10 - 150 g, and 1 g = 9.8 m / s 2 .

22. An acoustic enhancement method according to any one of claims 19-22, characterized in that Abrasive beads are also added to the acoustic intensification chamber, and the total filling volume ratio of the abrasive beads and the material is 50%-100%.

23. An acoustic enhancement method according to claim 22, characterized in that, A liquid solvent is also added to the acoustic intensification chamber, and the addition amount of the liquid solvent is 50%-100% of the remaining internal space volume of the acoustic intensification chamber, and the remaining internal space of the acoustic intensification chamber includes the interstitial space of solid particles.

24. An acoustic enhancement method according to any one of claims 22-23, characterized in that The particle size of the abrasive beads is in the range of 0.01-2 mm.

25. An acoustic enhancement method according to any one of claims 22-24, characterized in that, At least one material to be processed is rigidly fixedly connected to the acoustic intensification chamber.

26. An acoustic enhancement method according to any one of claims 19-25, characterized in that, The uses of the acoustic intensification method include but are not limited to fluidization, mixing, dispersion, coating, polishing, crushing, emulsification, extraction, dissolution, and chemical reaction intensification of raw materials.

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