Vibration reduction and waveguide device based on bionic nonlinear oscillator superstructure and testing device

Abstract

The invention discloses a vibration reduction and waveguide device based on a bionic nonlinear oscillator superstructure and a testing device, and relates to the technical field of vibration reduction and waveguide testing. A non-linear vibration damping structure at the present stage cannot simulate a more complex wave propagation phenomenon, so that research on non-linear waves is limited. The device comprises a supporting guide rail, N mass blocks and N-1 bionic composite X-type nonlinear oscillators, the N mass blocks are transversely arranged and installed on the supporting guide rail, and each mass block can move along the supporting guide rail; each bionic composite X-type nonlinear vibrator is connected with two adjacent mass blocks and deforms along with the movement of the mass blocks, and the bionic composite X-type nonlinear vibrators and the mass blocks form a nonlinear periodic chain type structure. The device is mainly used for measuring vibration reduction and waveguide.

Description

Technical Field

[0001] The invention relates to the technical field of vibration reduction and waveguide testing, and in particular to a vibration reduction and waveguide device and a testing device based on a bionic nonlinear oscillator superstructure. Background Art

[0002] In many applications of physics and engineering, the propagation characteristics and control mechanisms of waves are an important research direction. Whether it is mechanical waves, sound waves or vibration waves, in the fields of construction, earthquake protection, acoustic engineering, etc., how to effectively control the wave transmission path, energy distribution and attenuation rate are key issues that affect the stability and efficiency of the system. Although the traditional linear wave propagation theory is applicable to some simple systems, when it comes to complex media or large-amplitude vibrations, the nonlinear effect becomes non-negligible. Nonlinear wave propagation exhibits special phenomena in many natural and artificial systems, such as solitons, oscillations, and amplitude amplification. These phenomena provide new ideas for controlling the energy and propagation path of waves, and stimulate a research boom on nonlinear wave propagation devices. The current nonlinear vibration reduction structure cannot simulate more complex wave propagation phenomena, resulting in limitations in the research of nonlinear waves. Summary of the invention

[0003] In view of this, the present invention provides a vibration reduction and waveguide device and a testing device based on a bionic nonlinear oscillator superstructure, in which bionic composite X-type nonlinear oscillators are connected in series into a periodic chain structure, and more complex wave propagation phenomena can be simulated by changing the amplitude and parameters of the bionic composite X-type nonlinear oscillator.

[0004] The technical solution adopted by the present invention to solve the above technical problems is:

[0005] A vibration reduction and waveguide device based on a bionic nonlinear oscillator superstructure comprises a supporting rail, N mass blocks and N-1 bionic composite X-type nonlinear oscillators, wherein the N mass blocks are arranged laterally and installed on the supporting rail, and each mass block can move along the supporting rail; each bionic composite X-type nonlinear oscillator connects two adjacent mass blocks and deforms with the movement of the mass blocks, and the bionic composite X-type nonlinear oscillator and the mass blocks form a nonlinear periodic chain structure.

[0006] Furthermore, each bionic composite X-type nonlinear oscillator includes a retractable hinge and two connecting seats, the two connecting seats correspond to two adjacent mass blocks one by one, and each connecting seat is installed on the corresponding mass block. The retractable hinge is installed between the two connecting seats, and the retractable hinge is stretched or compressed as the distance between the two mass blocks increases or decreases.

[0007] Furthermore, each retractable hinge includes a transverse spring, two longitudinal springs, a small parallelogram linkage structure and a large parallelogram linkage structure, one pair of diagonals of the large parallelogram linkage structure is respectively connected to two adjacent connecting seats, one pair of diagonals of the small parallelogram linkage structure is respectively connected to another pair of diagonals of the large parallelogram linkage structure, both ends of the transverse spring are respectively connected to one pair of diagonals of the small parallelogram linkage structure, two longitudinal springs are symmetrically arranged on both sides of the small parallelogram linkage structure, one end of the longitudinal spring is connected to another diagonal of the small parallelogram linkage structure, and the other end of the longitudinal spring is connected to the connecting seat.

[0008] Furthermore, the support rails include at least two rails and two support plates. At least two rails are inserted into the mass blocks and connect multiple mass blocks in series. A support plate is arranged on both sides of each rail, and the ends of the rails are fixed to the support plates.

[0009] A testing device for vibration reduction and waveguide comprises a signal generator, a power amplifier, an exciter and a bionic composite X-shaped nonlinear oscillator chain superstructure; the signal generator is electrically connected to the power amplifier, the power amplifier is electrically connected to the exciter, the signal generator is used to generate an excitation signal according to a set excitation frequency, the power amplifier is used to adjust the amplitude, and then output the signal to the exciter; the exciter is connected to a first mass block, and the exciter is used to excite the mass block.

[0010] Furthermore, the device also includes a data collector and two acceleration sensors. An acceleration sensor is installed on the first mass block and the Nth mass block respectively. The acceleration sensor is electrically connected to the data collector and transmits the vibration acceleration signal to the data collector.

[0011] Compared with the prior art, the present invention has the following beneficial effects:

[0012] 1. The bionic composite X-type nonlinear oscillator of the present application has the ability to adjust the nonlinearity of the system by changing the material properties, geometric structure and mechanical parameters, and can realize experiments under various conditions on the same experimental platform, providing greater experimental flexibility and operability.

[0013] 2. The bionic composite X-type nonlinear oscillator of the present application has better adaptability. This adaptability enables the system to maintain stable performance under different conditions and ensure the consistency of experimental results.

[0014] 3. The bionic composite X-type nonlinear oscillator of the present application shows higher robustness and anti-interference ability when dealing with external disturbances or system changes. The chain structure connects the oscillators to each other to form a redundant network. When a oscillator is damaged or fails, other oscillators can continue to work to maintain the overall function of the system, thereby improving reliability. The system was designed with various possible external interferences, such as temperature changes, vibration interference, etc. The bionic composite X-type nonlinear oscillator can offset or weaken the effects of these interferences by adjusting its own vibration characteristics, ensuring the stability of the experimental process and making the experimental device more reliable. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] The accompanying drawings are incorporated as part of this application and are used to provide a further understanding of the present invention.

[0016] Figure 1 The figure is a front view of a vibration reduction and waveguide device based on a bionic nonlinear oscillator superstructure according to the present invention.

[0017] Figure 2 It is a side view of a vibration reduction and waveguide device based on a bionic nonlinear oscillator superstructure of the present invention.

[0018] Figure 3 The diagram is a three-dimensional structural diagram of a vibration reduction and waveguide device based on a bionic nonlinear oscillator superstructure of the present invention.

[0019] Figure 4 for Figure 3 A partial enlarged view of point A in the middle.

[0020] Figure 5 The figure is a schematic structural diagram of a testing device for vibration reduction and waveguide according to the present invention.

[0021] Figure 6 When the spring stiffness and assembly angle are fixed, the dispersion relation of the experiment is compared with the theoretical calculation and numerical integration at different amplitudes; (a) is the dispersion relation of the experiment with A1 of 0.002039m, the dispersion relation of the experiment with theoretical calculation and numerical integration is compared with the theoretical calculation and numerical integration; (b) is the dispersion relation of the experiment with A1 of 0.007908m, the dispersion relation of the experiment with theoretical calculation and numerical integration is compared with the theoretical calculation and numerical integration; (c) is the dispersion relation of the experiment with A1 of 0.015744m.

[0022] Figure 7The spring stiffness, amplitude and assembly angle of the small parallelogram linkage structure are fixed, and the dispersion relations of the experiment, theoretical calculation and numerical integration are compared and verified at different assembly angles; (a) is the dispersion relation of the experiment, theoretical calculation and numerical integration when the assembly angle α of the large parallelogram linkage structure is 37°; (b) is the dispersion relation of the experiment, theoretical calculation and numerical integration when the assembly angle α of the large parallelogram linkage structure is 45°; (c) is the dispersion relation of the experiment, theoretical calculation and numerical integration when the assembly angle α of the large parallelogram linkage structure is 53°.

[0023] Figure 8 The dispersion relation comparison and verification results of the experimental, theoretical and numerical integration under different spring stiffnesses are shown in Figure 2 for the assembly angle, amplitude and longitudinal spring fixation; (a) is the lateral spring stiffness k s The dispersion relation comparison and verification results of the experiment, theoretical calculation and numerical integration when the spring stiffness is 5680N / m; (b) is the lateral spring stiffness k s The dispersion relation comparison and verification results of the experiment, theoretical calculation and numerical integration when the load is 11000N / m; (c) is the lateral spring stiffness k s The dispersion relation of the experiment at 52000N / m is compared and verified with the theoretical calculation and numerical integration.

[0024] Explanation of the reference numerals: 1-support rail; 11-rail; 12-support plate; 2-mass block; 3-bionic composite X-type nonlinear oscillator; 31-retractable hinge; 311-lateral spring; 312-longitudinal spring; 313-large parallelogram connecting rod structure; 314-small parallelogram connecting rod structure; 32-connecting seat; 4-signal generator, 5-power amplifier, 6-exciter, 7-data collector, 8-acceleration sensor. DETAILED DESCRIPTION

[0025] In order to make the purpose, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. The following embodiments are used to illustrate the present invention but are not used to limit the scope of the present invention.

[0026] Embodiment 1:

[0027] See also Figures 1 to 3The embodiment of the present application provides a vibration reduction and waveguide device based on a bionic nonlinear oscillator superstructure, including a supporting rail 1, N mass blocks 2 and N-1 bionic composite X-type nonlinear oscillators 3, the N mass blocks 2 are arranged laterally and installed on the supporting rail 1, and each mass block 2 can move along the supporting rail 1; each bionic composite X-type nonlinear oscillator 3 connects two adjacent mass blocks 2 and deforms with the movement of the mass block 2, and the bionic composite X-type nonlinear oscillator 3 and the mass block 2 form a nonlinear periodic chain structure.

[0028] Among them, Figure 2 As shown, each bionic composite X-type nonlinear oscillator 3 includes a retractable hinge 31 and two connecting seats 32. The two connecting seats 32 correspond to two adjacent mass blocks 2 one by one, and each connecting seat 32 is installed on the corresponding mass block 2. The retractable hinge 31 is installed between the two connecting seats 32. As the distance between the two mass blocks 2 increases or decreases, the retractable hinge 31 is stretched or compressed.

[0029] Furthermore, if Figure 4 As shown, each retractable hinge 31 includes a transverse spring 311, two longitudinal springs 312, a small parallelogram linkage structure 314 and a large parallelogram linkage structure 313, one pair of diagonals of the large parallelogram linkage structure 313 is respectively connected to two adjacent connecting seats 32, one pair of diagonals of the small parallelogram linkage structure 314 is respectively connected to the other pair of diagonals of the large parallelogram linkage structure 313, both ends of the transverse spring 311 are respectively connected to one pair of diagonals of the small parallelogram linkage structure 314, two longitudinal springs 312 are symmetrically arranged on both sides of the small parallelogram linkage structure 314, one end of the longitudinal spring 312 is connected to the other diagonal of the small parallelogram linkage structure 314, and the other end of the longitudinal spring 312 is connected to the connecting seat.

[0030] Among them, Figures 1 to 3 As shown, the support guide rail 1 includes at least two guide rails 11 and two support plates 12. At least two of the guide rails 11 are inserted into the mass blocks 2 and multiple mass blocks 2 are connected in series. A support plate 12 is arranged on both sides of each guide rail 11, and the ends of the guide rails 1 are fixed to the support plates 12.

[0031] The N mass blocks 2 and N-1 bionic composite X-type nonlinear oscillators 3 of this embodiment are connected into a periodic chain structure, forming a highly flexible propagation path, and the transmission of waves can be controlled by adjusting the mass and connection mode of the nodes. For example, consider a network composed of multiple mass blocks 2 and elastic connections. By increasing the mass of certain nodes, the propagation speed of the wave can be reduced; and by changing the connection mode, such as using rigid or flexible connections, the wave can be guided to propagate in a specific direction. This design allows accurate fluctuation control in the field of acoustic and vibration control. The bionic composite X-type nonlinear oscillator 3 can be regarded as a bionic X-type, which is a special geometric design that can effectively disperse stress and energy through intersections (nodes or areas where different fluctuation paths intersect or connect). Combining the chain structure with the bionic X-type bionic composite X-type nonlinear oscillator 3 can provide complex and diverse propagation paths for wave propagation. When the wave propagates in the chain structure, the wave can be reflected and refracted multiple times through different mass blocks 2 and connections, thus forming multiple propagation paths. For example, when a wave encounters a connection with different stiffness at a certain node (intersection), it can choose a different path to propagate, effectively absorbing and dissipating energy and avoiding excessive concentration of local stress.

[0032] The bionic composite X-type nonlinear oscillator of this embodiment adopts an inner and outer two-layer parallelogram linkage structure. Compared with the traditional single-layer structure, this bionic composite X-type nonlinear oscillator can provide support and constraints in multiple directions, thereby achieving a multi-degree-of-freedom vibration reduction effect, which is suitable for coping with complex multi-directional vibration environments. At the same time, a longitudinal spring is arranged between the inner parallelogram linkage structure and the outer parallelogram linkage structure, and a transverse spring is arranged in the inner parallelogram linkage structure. The overall stiffness can be precisely adjusted by adjusting the stiffness of different springs. The double-layer design helps to provide strong support in both the transverse and longitudinal directions, and is suitable for application scenarios with higher stability requirements.

[0033] The bionic composite X-type nonlinear oscillator of this embodiment can show nonlinear characteristics under large deformation, which helps to provide stronger restoring force during large vibrations, prevent the system from entering an excessively large vibration amplitude range, and thus achieve a better vibration reduction effect. The bionic composite X-type nonlinear oscillator can effectively disperse the load, improve the stability of the system when subjected to force, and reduce the instability caused by uneven force.

[0034] The bionic composite X-type nonlinear oscillator 3 of this embodiment has the ability to adjust the nonlinearity of the system by changing the material properties, geometric structure and mechanical parameters, and can realize experiments under a variety of different conditions on the same experimental platform, providing greater experimental flexibility and operability. For the material properties of the bionic composite X-type nonlinear oscillator 3, different materials can be selected or the composition of the materials can be adjusted to change its nonlinear behavior, thereby affecting the propagation characteristics of the wave. For the geometric structure of the bionic composite X-type nonlinear oscillator 3, the geometric shape of the oscillator can be adjusted, such as changing the connection method or node layout, to achieve different waveguide effects and vibration reduction performance. For the mechanical parameters of the bionic composite X-type nonlinear oscillator 3, the rigidity, mass distribution or external force of the connection can be changed to achieve precise adjustment of the dynamic response of the system. In addition, the bionic composite X-type nonlinear oscillator 3 has better adaptability. Due to the nonlinear characteristics of the oscillator, they can automatically adjust their own vibration mode according to the intensity and frequency of the external disturbance. This adaptive ability enables the system to maintain stable performance under different conditions and ensure the consistency of the experimental results. Moreover, it shows higher robustness and anti-interference ability when dealing with external disturbances or system changes. The chain structure connects the oscillators to each other to form a redundant network. When a oscillator is damaged or fails, other oscillators can continue to work to maintain the overall function of the system, thereby improving reliability. The system was designed with various possible external interferences, such as temperature changes and vibration interference. The bionic composite X-type nonlinear oscillator 3 can offset or weaken the effects of these interferences by adjusting its own vibration characteristics, ensuring the stability of the experimental process and making the experimental device more reliable.

[0035] Embodiment 2:

[0036] See also Figure 5 The present embodiment provides a testing device for vibration reduction and waveguide, the device comprising a signal generator 4, a power amplifier 5, an exciter 6, a data collector 7, two acceleration sensors 8 and a bionic composite X-type nonlinear oscillator chain superstructure; the signal generator 4 is electrically connected to the power amplifier 5, the power amplifier 5 is electrically connected to the exciter 6, the signal generator 4 is used to generate an excitation signal according to a set excitation frequency, the power amplifier 5 is used to adjust the amplitude, and then output the signal to the exciter 6; the exciter 6 is connected to the first mass block 2, the exciter 6 is used to excite the mass block 2; an acceleration sensor 8 is respectively installed on the first mass block 2 and the Nth mass block 2, the acceleration sensor 8 is electrically connected to the data collector 7, and transmits the vibration acceleration signal to the data collector 7, and the data collector 7 transmits the vibration acceleration signal to the computer.

[0037] In this embodiment, a chain structure is formed by interconnected bionic composite X-type nonlinear oscillators. Under external excitation, these units interact through hinge points or elastic elements to form a propagation channel for nonlinear waves. When the excitation energy is applied to one end of the device, the energy is transmitted along the chain structure, and the speed, amplitude and frequency of the wave are changed due to the nonlinear characteristics of the bionic composite X-type nonlinear oscillator. Each X-type unit absorbs and disperses part of the energy during the propagation process, gradually weakens the intensity of the wave, effectively prevents energy concentration, and reduces system fatigue damage. The nonlinear characteristics of the device enable it to cope with complex excitation conditions and show wave propagation behaviors different from those of linear systems. It is particularly suitable for studying phenomena such as nonlinear wave propagation, energy absorption and dispersion. This design has a wide range of experimental application value in the fields of mechanics, vibration control and materials science.

[0038] The vibration and waveguide testing process is as follows:

[0039] S1, build the test platform, such as Figure 5 As shown, the nonlinear oscillator chain superstructure is installed on the test platform, the first mass block 2 in the nonlinear oscillator 3 chain superstructure is connected to the exciter 6, an acceleration sensor 8 is installed on the first mass block 2 and the Nth mass block 2, and the data collector 7 collects the vibration acceleration signal and transmits it to the computer;

[0040] S2, verify the influence of the amplitude and parameters of the bionic composite X-type nonlinear oscillator 3 on the dimensionless frequency.

[0041] 1) Determine the influence of amplitude on dimensionless frequency: When the spring stiffness ks = 11000N / m and the assembly angle α = π / 4 are fixed, the frequency sweep test results of the nonlinear chain structure are compared with the dispersion curve solved by the perturbation method and the results of numerical integration. The data marked in the box diagram in the figure are the medians of the 10 sets of dimensionless wave numbers obtained after the experimental samples are processed, and the rest of the data are processed according to the basic box diagram format. Figure 6 It can be seen that the experimental data are in good agreement with the wave numbers at the same frequency obtained by theoretical derivation and numerical integration calculation. The amount of experimental data is sufficient and the error is within an acceptable range. The accuracy of the dispersion relation derived from this theory is verified, and elastic wave propagation is strictly dependent on the amplitude. The larger the amplitude, the larger the frequency corresponding to the same wave value.

[0042] 2) Determine the effect of the assembly angle on the dimensionless frequency: fix the amplitude and spring stiffness, change the assembly angle of the parallelogram frame, solve the dispersion curve of the falling wave based on the sweep frequency experimental results of the nonlinear chain structure and the perturbation method, compare the dispersion curve with the results of numerical integration, and determine the effect of the assembly angle on the dimensionless frequency. Figure 7It can be seen that the wave number calculated at the given frequency in the experiment is in good agreement with the theoretical derivation and numerical integration, so the correctness of the theoretically derived effect of the assembly angle on the dispersion relation of wave propagation is verified. Under the condition of fixing the other parameters, the larger the assembly angle, the larger the cutoff frequency of elastic wave propagation, and the corresponding wave propagation range is larger.

[0043] 3) Determine the influence of spring stiffness on dimensionless frequency: fix the assembly angle and amplitude of the parallelogram frame, change the spring stiffness, solve the dispersion curve of the falling wave based on the sweep frequency experimental results of the nonlinear chain structure and the perturbation method, compare the dispersion curve with the results of numerical integration, and determine the influence of spring stiffness on dimensionless frequency. Figure 8 It can be seen that the wave number calculated at the given frequency in the experiment is in good agreement with the theoretical derivation and numerical integration, so the correctness of the theoretically derived influence of spring stiffness on the dispersion relation of wave propagation is verified. Under the condition of fixing other parameters, the larger the spring stiffness, the smaller the cutoff frequency of elastic wave propagation, and the smaller the corresponding wave propagation range.

[0044] The embodiments described above are merely descriptions of preferred implementation modes of the present invention and are not intended to limit the scope of the present invention. Without departing from the concept of the present invention, various modifications and improvements made to the technical solutions of the present invention by ordinary technicians in this field should fall within the scope of protection determined by the claims of the present invention.

Claims

1. A vibration reduction and waveguide device based on a bionic nonlinear oscillator superstructure, characterized in that: The invention comprises a supporting guide rail, N mass blocks and N-1 bionic composite X-type nonlinear oscillators. The N mass blocks are arranged transversely and installed on the supporting guide rail, and each mass block can move along the supporting guide rail. Each bionic composite X-type nonlinear oscillator connects two adjacent mass blocks and deforms with the movement of the mass blocks. The bionic composite X-type nonlinear oscillator and the mass blocks form a nonlinear periodic chain structure.

2. The vibration reduction and waveguide device based on the bionic nonlinear oscillator superstructure according to claim 1, characterized in that: Each bionic composite X-type nonlinear oscillator includes a retractable hinge and two connecting seats. The two connecting seats correspond to two adjacent mass blocks one by one, and each connecting seat is installed on the corresponding mass block. The retractable hinge is installed between the two connecting seats. As the distance between the two mass blocks increases or decreases, the retractable hinge is stretched or compressed.

3. The vibration reduction and waveguide device based on the bionic nonlinear oscillator superstructure according to claim 2, characterized in that: Each retractable hinge includes a transverse spring, two longitudinal springs, a small parallelogram linkage structure and a large parallelogram linkage structure, one pair of diagonals of the large parallelogram linkage structure is respectively connected to two adjacent connecting seats, one pair of diagonals of the small parallelogram linkage structure is respectively connected to the other pair of diagonals of the large parallelogram linkage structure, the two ends of the transverse spring are respectively connected to the one pair of diagonals of the small parallelogram linkage structure, the two longitudinal springs are symmetrically arranged on both sides of the small parallelogram linkage structure, one end of the longitudinal spring is connected to the other diagonal of the small parallelogram linkage structure, and the other end of the longitudinal spring is connected to the connecting seat.

4. The vibration reduction and waveguide device based on the bionic nonlinear oscillator superstructure according to claim 1, characterized in that: The support rails include at least two rails and two support plates. At least two rails are inserted into the mass blocks and connect multiple mass blocks in series. A support plate is arranged on both sides of each rail, and the ends of the rails are fixed to the support plates.

5. A test device for vibration reduction and waveguide, characterized in that: The device includes a signal generator, a power amplifier, an exciter, and a vibration reduction and waveguide device based on a bionic nonlinear oscillator superstructure as described in any one of claims 1 to 4; the signal generator is electrically connected to the power amplifier, the power amplifier is electrically connected to the exciter, the signal generator is used to generate an excitation signal according to a set excitation frequency, the power amplifier is used to adjust the amplitude, and then output the signal to the exciter; the exciter is connected to the first mass block, and the exciter is used to excite the mass block.

6. A testing device for vibration reduction and waveguide according to claim 5, characterized in that: The device also includes a data collector and two acceleration sensors. An acceleration sensor is installed on the first mass block and the Nth mass block respectively. The acceleration sensor is electrically connected to the data collector and transmits the vibration acceleration signal to the data collector.

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