A design method for a compound double vibration absorber, a storage medium and a vehicle

Abstract

The present invention provides a design method for a compound double vibration absorber, comprising a first mass block, a second mass block and an elastic block, the elastic block being a hollow cylinder with an axial centerline, and the inner wall of the elastic block being adapted to the outer surface of the cylindrical rod, the elastic block being covered with the first mass block and the second mass block, and the first mass block and the second mass block being separated by a certain distance, the first mass block and the second mass block both being hollow cylindrical, and the axial centerlines of the first mass block and the second mass block coincide with the axial centerline of the elastic block, the elastic block being provided with a first thin-walled portion on a side close to the inner wall of the first mass block and the second mass block, and the elastic block being provided with a second thin-walled portion on a side away from the outer wall of the first mass block and the second mass block, the present invention provides a compound double vibration absorber structure and a compound double vibration absorber parameter design and matching method, which are helpful to attenuate mechanical system noise vibration and fatigue durability problems caused by system resonance.

Description

Technical Field

[0001] The present invention relates to the technical field of automobile vibration and noise control, and in particular to a design method for a compound double vibration absorber, a storage medium and a vehicle. Background Art

[0002] Component modal resonance is a major cause of noise and vibration issues. Due to structural limitations or development time constraints, some component resonance is unavoidable. Dynamic vibration absorbers are widely used to reduce vibration and noise in aerospace, automotive, marine, and machinery manufacturing equipment.

[0003] The patent "A performance test device and test method for a car drive half-shaft dynamic vibration absorber" (201910195964.9) provides a performance test device and test method for a car drive half-shaft dynamic vibration absorber with a single vibration absorber. The patent "Adjustable dynamic vibration absorber and a tuning method for the dynamic vibration absorber" (202111104293.4) ​​proposes a single vibration absorber with a mass block. In actual use, mass blocks of different weights are installed according to frequency requirements. The vibration absorption frequency range of the transmission single dynamic vibration absorber is relatively narrow. When the external excitation frequency is close to the vibration absorber frequency, the vibration of the main system can be significantly reduced. However, when the excitation frequency shifts, the vibration reduction effect of the vibration absorber drops sharply. For occasions where a wide vibration attenuation frequency range is required, this type of single vibration absorber has poor vibration attenuation uniformity in each frequency range and strong frequency selectivity. Summary of the Invention

[0004] The present invention provides a design method for a compound double vibration absorber, a storage medium and a vehicle, aiming to solve the problems raised in the background technology.

[0005] In order to achieve the above-mentioned purpose, according to the first aspect of the present invention, a compound double vibration absorber is provided, which is used to be installed on a cylindrical rod, including a first mass block, a second mass block and an elastic block, the elastic block is a hollow cylinder with an axial centerline, and the inner wall of the elastic block is adapted to the outer surface of the cylindrical rod, the elastic block is covered with the first mass block and the second mass block, and the first mass block and the second mass block are separated by a certain distance, the first mass block and the second mass block are both hollow cylindrical, and the axial centerlines of the first mass block and the second mass block coincide with the axial centerline of the elastic block, the elastic block is provided with a first thin-walled portion on the side close to the inner wall of the first mass block and the second mass block, and the elastic block is provided with a second thin-walled portion on the side away from the outer wall of the first mass block and the second mass block, and grooves are provided on the outer surfaces of both sides of the elastic block, and the grooves are used to place clamps.

[0006] It can be seen from the above technical solution that the present invention covers the first mass block and the second mass block on the elastic block, and the mass and resonant frequency of the first mass block and the second mass block can be flexibly selected, thereby forming an integrated double vibration absorber with adjustable frequency and mass. The different parts of the double vibration absorber cooperate with each other, so that the vibration absorber of the present invention can be suitable for occasions where a wide frequency range of vibration attenuation is required, and the vibration attenuation uniformity is good in each frequency range. At the same time, the compound double vibration absorber of the present invention is a hollow cylinder with a center line, which is convenient for the compound double vibration absorber to be installed on the cylindrical rod, that is, it is convenient to be installed on the automobile drive half shaft, and is further suitable for vibration attenuation of the automobile drive half shaft.

[0007] A further solution is that the first mass block and the second mass block have different frequencies.

[0008] A further solution is that the elastic block is made of rubber material.

[0009] A further solution is that the cylindrical rod is a car drive half shaft.

[0010] According to a second aspect of the present invention, a design method for a compound double vibration absorber is provided, which specifically includes:

[0011] Obtain the acceleration amplitude frequency response function curve of the main system, and determine the resonant frequency f0, modal mass M0, and damping ratio ξ0 of the main system based on the acceleration amplitude frequency response function curve of the main system, wherein the main system is a system based on cylindrical rods;

[0012] The main system is simplified into a single-degree-of-freedom vibration parameterized model including the main system modal mass M0, the main system stiffness K0, and the main system damping C0; the compound double vibration absorber system is simplified into a double-degree-of-freedom vibration parameterized model, and the compound double vibration absorber system is a system based on the compound double vibration absorber, which includes the modal mass M1 of the first mass block, the modal mass M2 of the second mass block, the stiffness K1 of the elastic block covering the first mass block, the stiffness K2 of the elastic block covering the second mass block, the damping C1 of the elastic block covering the first mass block, and the damping C2 of the elastic block covering the second mass block;

[0013] According to the above single-degree-of-freedom vibration parameter model and double-degree-of-freedom vibration parameter model, the mechanical equilibrium equation is established with the increase of the vibration displacement of the main system after the compound double vibration absorber as the objective function. The formula is:

[0014]

[0015]

[0016]

[0017] in is the second differential of the displacement of the main system, is the first differential of the main system displacement, X0 is the main system displacement, F is the main system excitation force, e is a natural constant, j is an imaginary unit, ω is the angular frequency of the excitation force, and t is time. is the second differential of the displacement of the first mass block, is the first differential of the displacement of the first mass block, X1 is the displacement of the first mass block, is the second differential of the displacement of the second mass block, is the first differential of the displacement of the second mass block, X2 is the displacement of the second mass block;

[0018] Then the vibration displacement of the main system after adding the compound double vibration absorber is:

[0019]

[0020] in

[0021] Angular frequency Mass ratio Frequency ratio Damping ratio

[0022] δ st is the static displacement of the main system, λ is the frequency ratio of the excitation frequency to the resonant frequency of the main system, the value range of i for angular frequency and damping ratio is 0, 1, and 2, and the value range of i for mass ratio and frequency ratio is 1 and 2; f1 and f2 are the natural frequencies of the first mass block and the second mass block respectively, ω is the angular frequency of the excitation force, and f is the frequency of the excitation force;

[0023] According to formula (4), different mass ratios, frequency ratios, and damping ratios are used to obtain different displacement vibration-frequency curves. The displacement vibration-frequency curve with the minimum peak value corresponding to the maximum peak is selected to obtain its corresponding mass ratios μ1 and μ2, frequency ratios α1 and α2, and damping ratios ξ1 and ξ2, which are the optimal mass ratios, frequency ratios, and damping ratios.

[0024] According to the corresponding mass ratio μ1 and μ2, frequency ratio α1 and α2, and damping ratio ξ1 and ξ2, the design parameters of the compound double vibration absorber are determined.

[0025] As can be seen from the above technical solution, the present invention constructs single-degree-of-freedom and dual-degree-of-freedom vibration parameter models, establishes a mechanical equilibrium equation, and uses increasing the vibration displacement of the main system behind the compound dual vibration absorber as the objective function. By selecting and matching the optimal mass ratio, frequency ratio, and damping ratio parameters of the dual vibration absorber and the main system, the peak displacement vibration in the displacement-frequency curve is minimized. Compared to single vibration absorbers and independent, separate dual vibration absorbers, the compound dual vibration absorber designed by this method achieves better vibration attenuation of the main system, with greater attenuation uniformity across all frequency bands, while being less selective in the excitation frequency of the main system.

[0026] A further solution is that obtaining the acceleration amplitude frequency response function curve of the main system and determining the resonant frequency f0, modal mass M0, and damping ratio ξ0 of the main system according to the acceleration amplitude frequency response function curve of the main system specifically includes:

[0027] The hammer frequency response test method is used to obtain the acceleration amplitude frequency response function curve of the main system. The resonant frequency f0 is the frequency at the peak of the amplitude frequency response function curve, H is the peak of the amplitude frequency response function curve, and the frequency width δ f is the difference between the two frequencies at the intersection of the 0.707*H horizontal line and the frequency response function curve, then

[0028] ξ0=δ f / f0; (5)

[0029] M0=1 / (H*2ξ0)=1 / (H*δ f / f0); (6)

[0030] A further solution is to have the mass ratios μ1 and μ2 have the same value, ranging from 0.05 to 0.3; the damping ratios ξ1 and ξ2 have the same value, ranging from 0.02 to 0.09; and the frequency ratios α1 and α2 have a value range of 0.7 to 1.3. It is understood that such a configuration can reduce program design complexity and actual manufacturing costs.

[0031] A further solution is that the design parameters of the compound double vibration absorber are determined based on the corresponding mass ratio μ1 and μ2, frequency ratio α1 and α2, and damping ratio ξ1 and ξ2, specifically including:

[0032] According to M1=μ1*M0, determine the modal mass M1 of the first mass block;

[0033] According to M2=μ2*M0;, determine the modal mass M2 of the second mass block;

[0034] According to f1=α1*f0, determine the overall natural frequency f1 of the first mass block and the elastic block covering the first mass block;

[0035] According to f2=α2*f0, the overall natural frequency f2 of the second mass block and the elastic block covering the second mass block is determined.

[0036] According to a third aspect of the present invention, there is provided a storage medium having a computer program stored thereon, wherein the program implements the steps of the method described above when executed by a processor.

[0037] According to a fourth aspect of the present invention, a vehicle is provided, comprising a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the steps of the method described above are implemented when the processor executes the program.

[0038] Compared with the prior art, the beneficial effects of the present invention are: 1) The present invention provides a compound double vibration absorber structure and a compound double vibration absorber parameter design and matching method, which are helpful to attenuate the noise vibration and fatigue durability problems of the mechanical system caused by system resonance; 2) The present invention provides a compound double vibration absorber structure and a parameter design and matching method suitable for cylindrical rods, which can effectively solve the noise vibration and fatigue durability problems caused by the resonance of the driving half-shaft; 3) Since the present method determines the design parameters of the compound double vibration absorber based on the displacement vibration-frequency curve with the optimal morphology, the compound double vibration absorber designed by the present method has a better vibration attenuation effect on the main system, and has better attenuation uniformity in each frequency band, and has weak selectivity for the excitation frequency of the main system. BRIEF DESCRIPTION OF THE DRAWINGS

[0039] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the following briefly introduces the drawings required for use in the embodiments. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0040] Figure 1 Schematic diagram of the cross-sectional structure of a compound double vibration absorber according to an embodiment of the present invention;

[0041] Figure 2 A schematic cross-sectional perspective view of a compound double vibration absorber according to an embodiment of the present invention;

[0042] Figure 3 This is a schematic diagram of the system parameters for estimating the frequency response function of the main system of the present invention;

[0043] Figure 4 This is a vibration parameterized model diagram of the compound double vibration absorber of the present invention;

[0044] Figure 5 The displacement vibration curves of the main system when using the vibration absorber with different mass ratios, frequency ratios and damping ratios of the present invention;

[0045] Figure 6 is the displacement vibration curve of the main system under the optimal parameters of the present invention;

[0046] Figure 7 Comparison of vibration attenuation effects between a compound double vibration absorber and a single vibration absorber of the present invention having the same total mass;

[0047] Figure 8 This is a comparison of the frequency response curves before and after the installation of the compound double vibration absorber on the driving half shaft of vehicle A of the present invention;

[0048] Figure 9 This is a comparison of the frequency response curves before and after the installation of the compound double vibration absorber on the driving half shaft of vehicle B of the present invention;

[0049] Reference numerals: first mass block 1 , second mass block 2 , elastic block 3 , first thin-walled portion 301 , second thin-walled portion 302 , groove 303 . DETAILED DESCRIPTION

[0050] In order to make the objects, features and advantages of the present invention more obvious and easy to understand, the specific embodiments of the present invention are described in detail below with reference to the accompanying drawings.

[0051] It should be noted that when an element is referred to as being “fixed to” another element, it may be directly on the other element or there may be an intermediate element. When an element is referred to as being “connected to” another element, it may be directly connected to the other element or there may be an intermediate element.

[0052] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by those skilled in the art to which this invention pertains. The terms used herein in the specification of the present invention are for the purpose of describing specific embodiments only and are not intended to limit the present invention. The term "and / or" as used herein includes any and all combinations of one or more of the associated listed items.

[0053] Example 1

[0054] See also Figure 1 and Figure 2 The present invention provides a compound double vibration absorber for installation on a cylindrical rod. In this embodiment, the cylindrical rod is a car drive half shaft. The compound double vibration absorber includes a first mass block 1, a second mass block 2 and an elastic block 3, and the elastic block 3 is made of rubber material. The elastic block 3 is in the shape of a hollow cylinder with an axial centerline, and the inner wall of the elastic block 3 is adapted to the outer surface of the automobile drive half shaft. The elastic block 3 is covered with a first mass block 1 and a second mass block 2, and the first mass block 1 and the second mass block 2 are separated by a certain distance. The first mass block 1 and the second mass block 2 are both hollow cylindrical, and the axial centerlines of the first mass block 1 and the second mass block 2 coincide with the axial centerline of the elastic block 3. The elastic block 3 is provided with a first thin-walled portion 301 on a side close to the inner wall of the first mass block 1 and the second mass block 2, and a second thin-walled portion 302 on a side away from the outer wall of the first mass block 1 and the second mass block 2, and grooves 303 are provided on the outer surfaces of both sides of the elastic block 3. The grooves 303 are used to place clamps, and the clamps are used to fasten the elastic block 3 to the automobile drive half shaft, so that the compound double vibration absorber helps to attenuate the mechanical system noise vibration and fatigue durability problems caused by the resonance of the automobile drive half shaft.

[0055] Furthermore, the first mass block 1 and the second mass block 2 have different frequencies.

[0056] The present invention covers the first mass block 1 and the second mass block 2 on the elastic block 3, and the mass and resonance frequency of the first mass block 1 and the second mass block 2 can be flexibly selected, thereby forming a compound double vibration absorber with adjustable frequency and mass. The double vibration absorber of the present invention is suitable for occasions where a wide frequency range of vibration attenuation is required, and the vibration attenuation uniformity is good in each frequency range. At the same time, the compound double vibration absorber of the present invention is a hollow cylinder with a center line, which facilitates the installation of the compound double vibration absorber on a cylindrical rod, that is, it is convenient to install it on a vehicle drive half shaft, and is further suitable for vibration attenuation of a vehicle drive half shaft.

[0057] Example 2

[0058] The present invention provides a design method for a compound double vibration absorber, which specifically includes:

[0059] Step S1: Obtain the acceleration amplitude frequency response function curve of the main system, and determine the resonant frequency f0, modal mass M0, and damping ratio ξ0 of the main system based on the acceleration amplitude frequency response function curve. The main system is a system based on cylindrical rods. In this embodiment, the cylindrical rods are automobile drive axles, and the main system is a system that requires the addition of vibration absorbers to attenuate vibrations.

[0060] Step S2: simplify the main system into a single-degree-of-freedom vibration parameterized model including the main system modal mass M0, the main system stiffness K0, and the main system damping C0; simplify the compound double vibration absorber system into a double-degree-of-freedom vibration parameterized model, see Figure 4 The compound double vibration absorber system is a system based on a compound double vibration absorber. The structure of the compound double vibration absorber is as described in Example 1. The compound double vibration absorber system includes a modal mass M1 of a first mass block 1, a modal mass M2 of a second mass block 2, a stiffness K1 of an elastic block covering the first mass block 1, a stiffness K2 of an elastic block covering the second mass block 2, a damping C1 of an elastic block covering the first mass block 1, and a damping C2 of an elastic block covering the second mass block 2, that is, the elastic block 3 provides stiffness K1, K2 and damping C1, C2, and the first mass block 1 and the second mass block 2 provide mass. By adjusting the stiffness, damping and mass of the elastic block 3 and the two mass blocks, a compound double vibration absorber with different vibration absorption characteristics can be obtained.

[0061] Step S3: Based on the above single-degree-of-freedom vibration parameter model and the double-degree-of-freedom vibration parameter model, a mechanical equilibrium equation is established with the objective function of increasing the vibration displacement of the main system after the compound double vibration absorber. The formula is:

[0062]

[0063]

[0064]

[0065] in is the second differential of the displacement of the main system (acceleration), The first differential of the displacement of the main system (velocity), X0 is the displacement of the main system, F is the excitation force of the main system, e is a natural constant, j is an imaginary unit, ω is the angular frequency of the excitation force, and t is time. is the second differential of the displacement of the first mass block, is the first differential of the displacement of the first mass block, X1 is the displacement of the first mass block, is the second differential of the displacement of the second mass block, is the first differential of the displacement of the second mass block, X2 is the displacement of the second mass block;

[0066] Taking X0, X1, and X2 in formulas (1), (2), and (3) as unknown quantities, and solving the differential equations, the vibration displacement of the main system after adding the compound double vibration absorber is:

[0067]

[0068] in

[0069] Angular frequency Mass ratio Frequency ratio Damping ratio

[0070] δ st is the static displacement of the main system, λ is the frequency ratio of the excitation frequency to the resonant frequency of the main system, the value range of i for angular frequency and damping ratio is 0, 1, and 2, and the value range of i for mass ratio and frequency ratio is 1 and 2; f1 is the overall natural frequency of the first mass block and the elastic block covering the first mass block; f2 is the overall natural frequency of the second mass block and the elastic block covering the second mass block, ω is the angular frequency of the excitation force, and f is the frequency of the excitation force;

[0071] Step S4: According to formula (4), different mass ratios, frequency ratios, and damping ratios are used to obtain different displacement vibration-frequency curves. Figure 5 The smaller the displacement vibration of the main system after adding the compound double vibration absorber, the better the vibration attenuation effect of the compound double vibration absorber. The displacement vibration-frequency curve with the minimum peak corresponding to the maximum peak and the gentle peak is selected as the displacement vibration-frequency curve with the optimal shape. The corresponding mass ratio μ1 and μ2, frequency ratio α1 and α2, and damping ratio ξ1 and ξ2 are obtained, which are the optimal mass ratio, frequency ratio, and damping ratio.

[0072] It should be noted that, considering the design complexity and physical limitations, the mass ratios μ1 and μ2 have the same value, ranging from 0.05 to 0.3; the damping ratios ξ1 and ξ2 have the same value, ranging from 0.02 to 0.09; and the frequency ratios α1 and α2 have a value range of 0.7 to 1.3.

[0073] Step S5: Determine the design parameters of the compound double vibration absorber according to the corresponding mass ratios μ1 and μ2, frequency ratios α1 and α2, and damping ratios ξ1 and ξ2.

[0074] Specifically, according to M1=μ1*M0, the modal mass M1 of the first mass block is determined;

[0075] According to M2=μ2*M0;, determine the modal mass M2 of the second mass block;

[0076] According to f1=α1*f0, determine the overall natural frequency f1 of the first mass block and the elastic block covering the first mass block;

[0077] According to f2=α2*f0, the overall natural frequency f2 of the second mass block and the elastic block covering the second mass block is determined.

[0078] In addition, it should be noted that the acquisition of the acceleration amplitude frequency response function curve of the main system in step S1 and the determination of the resonant frequency f0, modal mass M0, and damping ratio ξ0 of the main system according to the acceleration amplitude frequency response function curve of the main system specifically include:

[0079] The hammer frequency response test method is used to obtain the main system acceleration amplitude frequency response function curve, see Figure 3 , the resonant frequency f0 is the frequency at the peak of the amplitude frequency response function curve, H is the peak of the amplitude frequency response function curve, and the frequency width δ f is the difference between the two frequencies at the intersection of the 0.707*H horizontal line and the frequency response function curve, then

[0080] ξ0=δ f / f0; (5)

[0081] M0=1 / (H*2ξ0)=1 / (H*δ f / f0); (6).

[0082] It should be noted that, in addition to the above-mentioned integrated double-compound vibration absorber, two separate single vibration absorbers can also be combined into a split double-compound vibration absorber. For two separate single vibration absorbers, the frequency and mass of the double-compound vibration absorber matching method are designed, such as Figure 6 and Figure 7As shown in the figure, under the condition of the same total mass, it can also achieve better vibration absorption effect than the single vibration absorber method. Compared with two separate single vibration absorbers, the compound dual-mass vibration absorber designed by this method has a more balanced vibration absorption effect in each frequency band and a better vibration attenuation effect.

[0083] In summary, this invention constructs single-degree-of-freedom and dual-degree-of-freedom vibration parameter models, establishes a mechanical equilibrium equation, and uses increasing the vibration displacement of the primary system behind the compound dual vibration absorber as the objective function. By selecting and matching the optimal mass ratio, frequency ratio, and damping ratio of the dual vibration absorber to the primary system, the peak displacement vibration in the displacement-frequency curve is minimized. Compared to single vibration absorbers and independent, separate dual vibration absorbers, the compound dual vibration absorber designed using this method achieves better vibration attenuation of the primary system, with greater attenuation uniformity across all frequency bands, while exhibiting less selectivity for the excitation frequency of the primary system.

[0084] Example 3

[0085] The drive half shaft is an important transmission component of the car. The bending resonance of the drive half shaft can cause the half shaft to fail or the whole car to roar or whistle. The bending frequency of the drive half shaft of car A is 400Hz. Excited by the gear meshing order of the transmission, the half shaft resonance causes the whole car to whistle. Car A is designed and matched with a compound double vibration absorber installed on the drive half shaft according to the method described in this article. One vibration absorber has a frequency of 337Hz and a mass of 180g, and the other vibration absorber has a frequency of 414Hz and a mass of 180g. Figure 8 As shown, after the driving half shaft is equipped with the double vibration absorber designed by the compound double vibration absorber method, the vibration response of the driving half shaft is attenuated by more than 70%.

[0086] Example 4

[0087] The bending frequency of the drive half shaft of vehicle B is 129Hz. Under the second-order excitation of the engine, the half shaft resonates violently, causing the whole vehicle to roar. Vehicle B is designed and matched with a double vibration absorber installed on the drive half shaft according to the method described in this article. One vibration absorber has a frequency of 97Hz and a mass of 300g, and the other vibration absorber has a frequency of 134Hz and a mass of 300g. Figure 9 As shown, after the drive half shaft is equipped with the compound double vibration absorber, the vibration response of the drive half shaft is attenuated by more than 50%.

[0088] Example 5

[0089] The present invention provides a storage medium having a computer program stored thereon, which implements the steps of the method described in Example 2 when the program is executed by a processor.

[0090] Example 6

[0091] A vehicle includes a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the processor implements the steps of the method described in Example 2 when executing the program.

[0092] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like to indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operate in a specific orientation, and therefore should not be understood as a limitation to the invention.

[0093] Throughout this specification, reference to terms such as "one embodiment," "some embodiments," "illustrative embodiments," "example," "specific example," or "some examples" means that a specific feature, structure, material, or characteristic described in conjunction with the embodiment or example is included in at least one embodiment or example of the present invention. In this specification, illustrative expressions of the above terms do not necessarily refer to the same embodiment or example.

[0094] Obviously, the described embodiments are only some of the embodiments of the present application, rather than all of the embodiments. Mentioning "embodiment" in this article means that the specific features, structures or characteristics described in conjunction with the embodiment may be included in at least one embodiment of the present embodiment application. The appearance of this phrase in various positions in the specification does not necessarily mean that they are all the same embodiments, nor are they independent or alternative embodiments that are mutually exclusive with other embodiments. It can be understood explicitly and implicitly by those skilled in the art that the embodiments described herein can be combined with other embodiments. Based on the embodiments in this application, all other embodiments obtained by those of ordinary skill in the art without making creative work are within the scope of protection of this application.

[0095] While embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions, and variations may be made to the embodiments without departing from the principles and spirit of the invention, and that the scope of the invention is defined by the claims and their equivalents.

Claims

1. A design method for a compound double vibration absorber, characterized in that: Specifically include: Obtain the acceleration amplitude frequency response function curve of the main system, and determine the resonance frequency f0, modal mass M0 and damping ratio of the main system according to the acceleration amplitude frequency response function curve of the main system , where the main system is a system based on cylindrical bars; The main system is simplified into a single-degree-of-freedom vibration parameterized model including the main system modal mass M0, the main system stiffness K0, and the main system damping C0; the compound double vibration absorber system is simplified into a double-degree-of-freedom vibration parameterized model, and the compound double vibration absorber system is a system based on the compound double vibration absorber, which includes the modal mass M1 of the first mass block, the modal mass M2 of the second mass block, the stiffness K1 of the elastic block covering the first mass block, the stiffness K2 of the elastic block covering the second mass block, the damping C1 of the elastic block covering the first mass block, and the damping C2 of the elastic block covering the second mass block; According to the above single-degree-of-freedom vibration parameter model and double-degree-of-freedom vibration parameter model, the mechanical equilibrium equation is established with the increase of the vibration displacement of the main system after the compound double vibration absorber as the objective function. The formula is: （1） （2） （3） in is the second differential of the displacement of the main system, is the first differential of the displacement of the main system, is the displacement of the main system, F is the excitation force of the main system, e is a natural constant, j is an imaginary unit, is the angular frequency of the excitation force, t is the time, is the second differential of the displacement of the first mass block, is the first differential of the displacement of the first mass block, is the displacement of the first mass block, is the second differential of the displacement of the second mass block, is the first differential of the displacement of the second mass block, is the displacement of the second mass block; Then the vibration displacement of the main system after adding the compound double vibration absorber is: （4） is the static displacement of the main system, is the frequency ratio of the excitation frequency to the main system resonant frequency, the value range of i for angular frequency and damping ratio is 0, 1, 2, and the value range of i for mass ratio and frequency ratio is 1, 2; f1 and f2 are the natural frequencies of the first mass block and the second mass block respectively, is the angular frequency of the excitation force, and f is the frequency of the excitation force; According to formula (4), different mass ratios, frequency ratios and damping ratios are used to obtain different displacement vibration-frequency curves. The optimal displacement vibration-frequency curve is selected to obtain its corresponding mass ratio. and , frequency ratio and , damping ratio and , which is the optimal mass ratio, frequency ratio and damping ratio; According to the above corresponding mass ratio and , frequency ratio and , damping ratio and , determine the design parameters of the compound double vibration absorber.

2. A design method for a compound double vibration absorber according to claim 1, characterized in that: The main system acceleration amplitude frequency response function curve is obtained, and the resonance frequency f0, modal mass M0, and damping ratio of the main system are determined according to the main system acceleration amplitude frequency response function curve. Specifically include: The hammer frequency response test method is used to obtain the acceleration amplitude frequency response function curve of the main system. The resonant frequency f0 is the frequency at the peak of the amplitude frequency response function curve, H is the peak of the amplitude frequency response function curve, and the frequency width is the difference between the two frequencies at the intersection of the 0.707*H horizontal line and the frequency response function curve, then （5） （6）。 3. The design method of a compound double vibration absorber according to claim 2, characterized in that: The mass ratio and The value is the same, ranging from 0.05 to 0.3; the damping ratio and The values ​​are the same and range from 0.02 to 0.

09.

4. The design method of a compound double vibration absorber according to claim 3, characterized in that: The frequency ratio and The value range is 0.7-1.

3.

5. The design method of a compound double vibration absorber according to claim 3, characterized in that: The corresponding mass ratio and , frequency ratio and , damping ratio and , the design parameters of the compound double vibration absorber are determined as follows: according to , determine the modal mass M1 of the first mass block; according to , determine the modal mass M2 of the second mass block; according to , determine the overall natural frequency f1 of the first mass block and the elastic block covering the first mass block; according to , determine the overall natural frequency f2 of the second mass block and the elastic block covering the second mass block.

6. The design method of a compound double vibration absorber according to claim 1, characterized in that: The compound double vibration absorber includes a first mass block, a second mass block and an elastic block. The elastic block is a hollow cylinder with an axial line, and the inner wall of the elastic block is adapted to the outer surface of the cylindrical rod. The elastic block is covered with the first mass block and the second mass block, and the first mass block and the second mass block are separated by a certain distance. The first mass block and the second mass block are both hollow cylindrical, and the axial line of the first mass block and the second mass block coincides with the axial line of the elastic block. The elastic block is provided with a first thin-walled portion on a side close to the inner wall of the first mass block and the second mass block, and a second thin-walled portion is provided on a side away from the outer wall of the first mass block and the second mass block, and grooves are provided on the outer surfaces of both sides of the elastic block, and the grooves are used to place clamps.

7. The design method of a compound double vibration absorber according to claim 6, characterized in that: The first mass block and the second mass block have different frequencies, the elastic block is made of rubber material; and the cylindrical rod is a car drive half shaft.

8. The design method of a compound double vibration absorber according to claim 1, characterized in that: The optimal displacement vibration-frequency curve is selected by selecting the displacement vibration-frequency curve with the minimum peak value corresponding to the maximum peak.

9. A computer-readable storage medium having a computer program stored thereon, characterized in that: When the program is executed by a processor, the steps of the method according to any one of claims 1 to 8 are implemented.

10. A vehicle, characterized in that: The method comprises a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the steps of the method according to any one of claims 1 to 8 are implemented when the processor executes the program.

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