CN113962121A - Damping alloy vibration reduction method, system and device - Google Patents
Damping alloy vibration reduction method, system and device Download PDFInfo
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Abstract
The invention discloses a method, a system and a device for damping vibration by using damping alloy, comprising S1, determining the natural frequency and the vibration mode of a vibration-damped object by modal analysis, and determining the application position of the damping alloy on the vibration-damped object according to the natural frequency and the vibration mode of the vibration-damped object and by combining the vibration transmission path of the vibration-damped object; s2, determining qualitatively the damping alloy application preliminary scheme by the analysis of the harmonic response of the linear mode aiming at different application parts of the damping alloy; and S3, performing optimization design on the damping alloy application preliminary schemes of different application parts through analysis, quantitatively analyzing the damping effect, and determining the final damping design scheme of each part of the object to be damped. The invention considers the nonlinear constitutive relation of the damping alloy, adopts the harmonic response of the linear mode to preliminarily analyze whether the vibration damping structure has the vibration damping effect, saves the analysis time and improves the calculation efficiency.
Description
Technical Field
The invention relates to the field of damping alloy design and application, in particular to a damping alloy vibration reduction method, system and device.
Background
The traditional damping alloy vibration attenuation design method is to process the damping alloy into a linear elastic material, only set a constant damping coefficient to reflect the damping capacity of the linear elastic material, study the vibration mode and the natural frequency of the structure through modal analysis, determine a key transformation part, design a vibration attenuation structure, and determine the vibration attenuation amplitude through harmonic response analysis. However, the damping alloy is essentially a non-linear elastic material, the damping capacity is related to the loading condition, and the linear constitutive and constant damping coefficient can cause the deviation of the damping structure design and optimization. And modal analysis, harmonic response analysis and rigid-flexible coupling dynamics analysis in the traditional vibration damping design are mainly established on the linear assumption that the rigidity is unchanged, and even if material nonlinearity is defined, the material nonlinearity can be ignored, and the nonlinear constitutive relation of the damping alloy is difficult to reflect.
Disclosure of Invention
The invention aims to provide a method for damping vibration by using damping alloy, aiming at solving the problem of damping vibration by using the damping alloy.
The invention provides a method for damping vibration by using damping alloy, which comprises the following steps: s1, determining the natural frequency and the vibration mode of the vibration-damped object through modal analysis, and determining the application part of the damping alloy on the vibration-damped object according to the natural frequency and the vibration mode of the vibration-damped object and by combining the vibration transmission path of the vibration-damped object; s2, determining qualitatively the damping alloy application preliminary scheme by the analysis of the harmonic response of the linear mode aiming at different application parts of the damping alloy; and S3, performing optimization design on the damping alloy application preliminary schemes of different application parts through analysis, quantitatively analyzing the damping effect, and determining the final damping design scheme of each part of the object to be damped.
The present invention also provides a system for damping vibration using a damping alloy, comprising:
a modal analysis module: determining the natural frequency and the vibration mode of a vibration-damped object through modal analysis, and determining the application part of the damping alloy on the vibration-damped object according to the natural frequency and the vibration mode of the vibration-damped object and by combining the vibration transmission path of the vibration-damped object;
a preliminary scheme module: determining a preliminary scheme of the damping alloy application qualitatively through linear mode and harmonic response analysis aiming at different application parts of the damping alloy;
a final scheme module: the damping alloy application preliminary schemes of different application parts are optimized and designed through analysis, the damping effect is quantitatively analyzed, and the final damping design scheme of each part of the object to be damped is determined.
The embodiment of the invention also provides a device for damping vibration by using the damping alloy, which comprises: a memory, a processor and a computer program stored on the memory and executable on the processor, the computer program implementing the steps of the above method when executed by the processor.
The embodiment of the invention also provides a computer readable storage medium, wherein an implementation program for information transmission is stored on the computer readable storage medium, and the implementation program realizes the steps of the method when being executed by a processor.
By adopting the embodiment of the invention, the nonlinear constitutive relation of the damping alloy is considered, and whether the vibration damping structure has the vibration damping effect or not can be preliminarily analyzed by adopting the linear mode and the harmonic response, so that the analysis time is saved, and the calculation efficiency is improved.
The foregoing description is only an overview of the technical solutions of the present invention, and the embodiments of the present invention are described below in order to make the technical means of the present invention more clearly understood and to make the above and other objects, features, and advantages of the present invention more clearly understandable.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the embodiments or the prior art descriptions will be briefly introduced below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and other drawings can be obtained by those skilled in the art without creative efforts.
FIG. 1 is a flow chart of a method of damping vibration using a damping alloy in an embodiment of the present invention;
FIG. 2 is a schematic diagram of a constraint situation of a damping alloy damping method according to an embodiment of the present invention;
FIG. 3 is a schematic view of weapon station 1 order mode using damping alloy damping method according to an embodiment of the present invention;
FIG. 4 is a schematic diagram of a weapon station 2 order mode using a damping alloy damping method according to an embodiment of the present invention;
FIG. 5 is a schematic diagram of weapon station 3 order mode using damping alloy damping method according to an embodiment of the present invention;
FIG. 6 is a schematic diagram of a weapon station 4 order mode using a damping alloy damping method according to an embodiment of the present invention;
FIG. 7 is a schematic illustration of weapon station 5 order mode using damping alloy damping method according to an embodiment of the present invention;
FIG. 8 is a schematic illustration of weapon station 6 order mode using damping alloy damping method according to an embodiment of the present invention;
FIG. 9 is a schematic view of a manganese-copper-based damping alloy disc spring damper using a damping alloy damping method according to an embodiment of the present invention;
FIG. 10 is a graphical representation of the damper spring static pressure curve using a damping alloy damping method in accordance with an embodiment of the present invention;
FIG. 11 is a schematic view showing calculation of the load and deformation of the disc spring stack using the damping alloy damping method according to the embodiment of the present invention;
FIG. 12 is a schematic view of calculation of load and deformation of a disc spring pairing using a damping alloy damping method according to an embodiment of the present invention;
FIG. 13 is a schematic diagram of the disc spring load and deflection calculation for a composite combination using damping alloy damping methods according to an embodiment of the present invention;
FIG. 14 is a schematic diagram of the optimization result of the involution combined disc spring buffer by using the damping alloy damping method according to the embodiment of the present invention;
FIG. 15 is a schematic view of an assembled form of eight involutory disc springs using a damping alloy damping method according to an embodiment of the present invention;
FIG. 16 is a schematic diagram of the optimization result of the composite combined disc spring using the damping alloy damping method according to the embodiment of the present invention;
FIG. 17 is a schematic diagram of the combination of 24 composite disc springs using damping alloy damping method according to the embodiment of the present invention;
FIG. 18 is a schematic view of an 8-piece involutory combined disc spring of a manganese-copper-based damping alloy using a damping alloy vibration reduction method according to an embodiment of the present invention;
FIG. 19 is a manganese-copper based damping alloy 24-piece composite combined disc spring using a damping alloy vibration reduction method according to an embodiment of the present invention;
FIG. 20 is a schematic diagram comparing the results of the muzzle X-direction harmonic response analysis acceleration using the damping alloy damping method according to the embodiment of the present invention;
FIG. 21 is a schematic diagram comparing the results of the analysis of the acceleration of the muzzle Y-direction harmonic response by the damping alloy damping method according to the embodiment of the present invention;
FIG. 22 is a schematic diagram comparing the results of Z-direction harmonic response analysis of the muzzle with damping alloy damping method according to the embodiment of the present invention;
FIG. 23 is a schematic view of a rectangular cylindrical coil spring damper utilizing a damping alloy damping method according to an embodiment of the present invention;
FIG. 24 is a schematic view of an 8-piece involutory combined disc spring damper made of a manganese-copper-based damping alloy by using a damping alloy vibration reduction method according to an embodiment of the present invention;
FIG. 25 is a schematic view of a manganese-copper-based damping alloy 24-piece composite combined disc spring damper utilizing a damping alloy damping method according to an embodiment of the present invention;
FIG. 26 is a schematic view of a transient analysis shock load of a damper utilizing a damping alloy damping method according to an embodiment of the present invention;
FIG. 27 is a schematic view of the X-direction acceleration response under different bumper shock loads using the damping alloy damping method according to an embodiment of the present invention;
FIG. 28 is a schematic view of a damping system utilizing a damping alloy in accordance with an embodiment of the present invention;
FIG. 29 is a schematic view of a vibration damping device using a damping alloy according to an embodiment of the present invention.
Description of reference numerals:
10: a modal analysis module; 11: a preliminary scheme module; 12: a final solution module; 1: a nut; 2: a guide bar; 3, a rectangular spring; 4, a base; 5: a sleeve; and 6, pressing the nut.
Detailed Description
The technical solutions of the present invention will be described clearly and completely with reference to the following embodiments, and it should be understood that the described embodiments are some, but not all, embodiments of the present invention. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, are within the scope of the present invention. In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", and the like, indicate orientations and positional relationships based on those shown in the drawings, and are used only for convenience of description and simplicity of description, but do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be construed as limiting the present invention. Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, features defined as "first", "second", may explicitly or implicitly include one or more of the described features. In the description of the present invention, "a plurality" means two or more unless specifically defined otherwise. Furthermore, the terms "mounted," "connected," and "connected" are to be construed broadly and may, for example, be fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; either directly or indirectly through intervening media, or may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
Method embodiment
According to an embodiment of the present invention, a method for damping vibration by using a damping alloy is provided, and fig. 1 is a flowchart of the method for damping vibration by using a damping alloy according to an embodiment of the present invention, as shown in fig. 1, specifically including:
s1, determining the natural frequency and the vibration mode of the vibration-damped object through modal analysis, and determining the application part of the damping alloy on the vibration-damped object according to the natural frequency and the vibration mode of the vibration-damped object and the vibration transmission path of the vibration-damped object; s1 specifically includes: the natural frequency and the vibration mode of the vibration-damping object are determined by carrying out modal analysis on the finite element model, and the application position of the damping alloy on the vibration-damping object is determined according to the natural frequency and the vibration mode of the vibration-damping object and the vibration transmission path of the vibration-damping object.
S2, determining qualitatively the damping alloy application preliminary scheme by the analysis of the harmonic response of the linear mode aiming at different application parts of the damping alloy; s2 specifically includes: the method comprises the steps of carrying out finite element modeling on damping alloy application, replacing the structure of the original vibration-damped object with the damping alloy application to carry out modal harmonic response analysis, and qualitatively determining the damping alloy application preliminary scheme.
And S3, performing optimization design on the damping alloy application preliminary schemes of different application parts through analysis, quantitatively analyzing the damping effect, and determining the final damping design scheme of each part of the object to be damped. S3 specifically includes: and optimizing and designing the damping alloy application preliminary schemes of different application parts through nonlinear transient analysis, quantitatively analyzing the damping effect, and determining the final damping design scheme of each part of the damped object.
According to the method, the concrete implementation method is as follows, and the principle of modal analysis and harmonic response analysis is known as follows:
(1) the modal analysis mainly assumes that the rigidity matrix and the mass matrix of the structure do not change, and the structure has no load changing along with time. Therefore, in the modal analysis of the conventional manganese-copper-based damping alloy, the rigidity and the damping coefficient of the damping alloy are assumed to be constants, which are not consistent with the variable rigidity matrix and the damping coefficient of the nonlinear constitutive relation of the manganese-copper-based damping alloy, so that errors can be generated with the actual situation. However, if the variable damping coefficient and the stiffness matrix are to be considered, it is equivalent to solving an infinite number of second-order constant coefficient homogeneous linear differential equations, which will increase many considerations for the result of modal analysis, and is not favorable for engineering application.
(2) The harmonic response analysis is also based on linear assumption, only the forced vibration section is analyzed, and the initial vibration section and other nonlinear factors are ignored. The nonlinear constitutive relation of the manganese-copper-based damping alloy cannot be reflected in the conventional harmonic response analysis. If nonlinear harmonic response analysis is to be realized, the simple harmonic load can be represented as a time-course load function only through nonlinear transient analysis, the frequency of the simple harmonic load is continuously changed to carry out nonlinear transient analysis, a series of discrete points are obtained, and the relation between the structural vibration amplitude and the frequency is drawn. However, the nonlinear transient calculation of repeated iteration is not favorable for simulation analysis, and particularly huge calculation cost is paid.
(3) From another point of view, the existing modal analysis and harmonic response analysis is not meaningless, and the linear modal analysis and harmonic response analysis requires less computing resources, is mature in technology and is widely verified. The manganese-copper-based damping alloy indeed belongs to a damping material, and when a fixed damping coefficient and rigidity matrix are set for the manganese-copper-based damping alloy, the manganese-copper-based damping alloy is also one of the manifestations of damping capacity and material characteristics in finite element analysis. The original system without damping alloy accords with the requirements of harmonic response analysis of linear mode and is not affected. The damping alloy structure with the existing fixed damping coefficient and rigidity matrix is adopted, and whether the damping alloy structure has the damping effect or not can be qualitatively analyzed by comparing with the original structure. And the fixed damping coefficient and the rigidity matrix mainly affect the amplitude calculation of the structural vibration, and the influence of the frequency is not large. Because the addition of the damping alloy is mainly to not change the original structural rigidity, the structural rigidity and the natural frequency are approximately considered to be not changed greatly. Therefore, whether the vibration damping structure has a vibration damping effect or not can be preliminarily analyzed by adopting the harmonic response of the linear mode, the analysis time is saved, and the calculation efficiency is improved. But the quantitative analysis of the vibration reduction effect needs to be completed by means of nonlinear transient analysis of the nonlinear constitutive relation of the manganese-copper-based damping alloy.
Considering the above factors comprehensively, the damping design method for the remote control weapon station of the manganese-copper-based damping alloy comprises the steps of firstly determining the natural frequency and the vibration mode through modal analysis, determining the damping alloy application part by combining a vibration transmission path, then performing damping alloy application design, qualitatively determining the damping alloy application preliminary scheme of each part through linear modal harmonic response analysis, finally performing optimization design on the damping alloy application preliminary schemes of different application parts by adopting nonlinear transient analysis, quantitatively analyzing the damping effect and determining the final damping design scheme of each part.
The existing manganese-copper-based damping alloy vibration attenuation design method does not consider the nonlinear constitutive relation of the damping alloy, but simply processes the damping alloy into a linear elastic material, sets a constant damping coefficient to reflect damping capacity, and the stress-strain relation of the manganese-copper-based damping alloy is related to strain amplitude, strain frequency and temperature and changes along with the strain amplitude, the strain frequency and the temperature. Therefore, it is necessary to provide a vibration damping design method suitable for manganese-copper-based damping alloy.
and 3, finally, optimally designing the damping alloy application preliminary schemes of different application parts by adopting nonlinear transient analysis, quantitatively analyzing the damping effect, and determining the final damping design scheme of each part.
The following takes the damping alloy application design of the weapon station as an example:
the step 1 comprises the following steps: firstly, carrying out modal analysis on a finite element model of the weapon station to determine the inherent frequency and the position with larger vibration and determine a vibration damping design modification component. Setting the lower surface of the seat ring as a fixed constraint, fig. 2 is a constraint situation schematic diagram of the damping alloy damping method according to the embodiment of the invention: as shown in fig. 2. Analyzing the overall first 20-order mode of the weapon station, wherein the result is a mode shape table as shown in table 1;
TABLE 1
As can be seen from table 1, the overall modal frequencies of the station are low, the first order frequency is 46.79Hz, the 20 th order frequency is 437.72Hz, the range is small, which indicates that the overall mass is heavy, and the first order frequencies are far from the machine gun firing frequency (10Hz, 600 shots/min). FIG. 3 is a schematic view of weapon station 1 order mode shape using damping alloy damping method according to an embodiment of the present invention; FIG. 4 is a schematic illustration of a weapon station 2 order mode shape utilizing a damping alloy damping method according to an embodiment of the present invention; FIG. 5 is a schematic diagram of a weapon station 3 order mode shape utilizing a damping alloy damping method according to an embodiment of the present invention; FIG. 6 is a schematic diagram of a weapon station 4 order mode shape utilizing a damping alloy damping method according to an embodiment of the present invention; FIG. 7 is a schematic illustration of weapon station 5 order mode shape using damping alloy damping method according to an embodiment of the present invention; FIG. 8 is a schematic illustration of weapon station 6 order mode shape using damping alloy damping method according to an embodiment of the present invention; it can be seen from fig. 3 to 8 that the modal shape of the low order of the weapon station is mainly bending deformation, the first two orders are mainly focused on the bending vibration of the gun barrel, the last 4 orders are focused on the cradle, the bracket, the magazine and the observing and aiming device, the 3 rd order is left and right bending vibration, the 4 th order is up and down polarization of the observing and aiming device, the 5 th order is up and down bending of the gun barrel, the cradle and the observing and aiming device, and the 6 th order is horizontal bending of the gun barrel and the observing and aiming device. The mode shape change of the race is small due to the fixed constraint between the race and the ground.
The mode results show that the vibration of the gun barrel is large, which is caused by the large length-diameter ratio of the gun barrel, the gun barrel is difficult to change, and the damping alloy is not suitable for coating the periphery of the gun barrel; the vibration of the magazine has little influence on the shooting of the weapon; the vibration of the sighting device belongs to a local mode, because the mass of the sighting device is small, the rigidity of the sighting device can be correspondingly increased, but the sighting device does not have referential property for improving the overall vibration characteristic of the weapon station; less vibration of the bracket portion; therefore, from the view of the mode shape diagram, only the cradle part is suitable for damping alloy vibration reduction application, and the impact on the shooting accuracy of the weapon station is large.
Impact load during shooting at a weapon station is transmitted to a cradle by a gun body through a buffer, the cradle is transmitted to a bracket through a trunnion and a high-low half gear, the load is transmitted to a seat ring through the bracket, the seat ring transmits force to a bearing platform, and meanwhile excitation caused by road excitation or vehicle body vibration is reversely transmitted to a gun muzzle by the seat ring. From the analysis of the vibration transmission path, the cradle half-gear, the buffer and the seat ring are more important links on the vibration transmission path and directly influence the dynamic characteristic of the muzzle.
And (3) determining that the direction of the manganese-copper-based damping alloy modification application is mainly the buffer of the cradle by combining the results of the modal analysis and the vibration transmission path analysis.
The buffer mainly absorbs recoil produced when the machine gun shoots, ensures that the weapon sits stably, buffers and consumes force and energy transmitted to the frame seat, and plays a key role in improving the stability of the frame seat. The buffer of current remote control weapon station mainly uses the spring buffer as the main, and the buffer passes through the mount and links to each other with the machine gun, through pin pole compression spring when the rifle body recoil, recoil partly converts elasticity into, and partly converts heat energy dissipation into to reach the buffering purpose. However, the common spring buffer has the phenomena of low energy absorption rate, secondary impact, overlarge rigidity and the like in the shooting process, so that the muzzle vibration is aggravated, and the shooting precision is influenced. In order to overcome the above problems, a novel manganese copper-based damping alloy disc spring buffer is designed herein, and fig. 9 is a schematic view of a manganese copper-based damping alloy disc spring buffer using a damping alloy damping method according to an embodiment of the present invention; the structural form of the disc spring with high load and small displacement is adopted, and the special vibration absorption capacity of the damping alloy is combined, so that the strength requirement of the buffer can be met, and the damping performance of the buffer can be improved.
The original spring in the buffer is a rectangular spiral spring made of 60Si2Mn, the compressed length of the original buffer spring is 56mm, and the pretightening force is 1848N. In order to obtain accurate mechanical parameters of the original buffer spring, a servo hydraulic testing machine is adopted for static pressure test, the spring is vertically arranged on a platform of the testing machine, the spring is uniformly compressed at the speed of 2mm/s, force and displacement curves are recorded at the same time, and the test is stopped until the spring enters a yield state. Fig. 10 is a schematic diagram of a static pressure curve of a damper spring using a damping alloy damping method according to an embodiment of the present invention, as shown in fig. 10.
As can be seen from FIG. 10, the buffer spring enters a yield state after 3kN, the displacement is 12.98mm, and the equivalent stiffness of the buffer spring is 231N/mm calculated, which shows that the acting force actually applied to the buffer is not more than 3000N, so that the manganese copper-based damping alloy disc spring buffer is designed on the basis.
The standard of disc spring design refers to disc spring standard GB/T1972-.
The load calculation formula of the single disc spring is as follows:
wherein: f is the load of a single disc spring, N; t is the thickness of the disc spring, mm; d is the outer diameter of the disc spring, mm; f is the deformation of the single disc spring, mm; h is0The calculated value of the deformation of the disc spring during flattening is mm; e-the elastic modulus of the disc spring material, MPa; calculating the coefficient
Wherein
The diameter ratio is larger, and d is the inner diameter of the disc spring; for disc spring K without support surface4＝1。
The stress calculation formula of the single disc spring is as follows:
in the formula sigmaOM-stress of the single disc spring, MPa; mu-Poisson's ratio.
Since it is generally difficult for a single disc spring to satisfy the requirements of load and deformation, the disc springs are generally used in combination. The main application forms comprise modes of superposition, involution, composite combination and the like, wherein superposition means that a plurality of disc springs are superposed together in the same direction, involution means that the plurality of disc springs are combined together in opposite directions sequentially, and composite combination means that the disc springs are superposed and then involuted, so that load and deformation are shared together. FIG. 11 is a schematic view showing calculation of the load and deformation of the disc spring stack using the damping alloy damping method according to the embodiment of the present invention, as shown in FIG. 11, the load F of the stacked n disc springs of the same specification is calculated without the frictional forceZN × F, but the deformation amount is the same as that of the single sheet.
FIG. 12 is a schematic view showing calculation of load and deformation of the involution of disc springs by damping alloy damping method according to the embodiment of the present invention, as shown in FIG. 12, i deformation f of involution of disc springs is calculated without frictional forceZI × f, the load is the same as a single sheet.
FIG. 13 is a schematic diagram of the calculation of the load and deformation of the disc spring using the damping alloy damping method according to the embodiment of the present invention, and as shown in FIG. 13, the deformation f of the disc spring is calculated without the frictional forceZ＝i×f，FZThe nxf load is the same as a single sheet.
When dish spring adopts dish spring combination, frictional force exists in dish spring contact conical surface and bears the weight of the edge, makes dish spring load increase during the loading, makes dish spring load reduce during the uninstallation, and dish spring load when considering the frictional force influence is according to the following formula calculation:
wherein: f-load of a single disc spring, FMCoefficient of friction between conical surfaces of disc spring, fRThe friction coefficient at the edge is taken as-when the disc spring is loaded and + when the disc spring is unloaded, and the friction coefficient f between conical surfaces of the disc spring is obtained according to the characteristics of the manganese-copper-based damping alloyMTaking 0.02, coefficient of friction at the bearing edge fR0.03 is taken.
Because the manganese-copper-based damping alloy buffer needs a certain deformation amount to increase to achieve the buffering and energy absorbing effects, the disc spring cannot be too thick, the size limitation of the original buffer is combined, the thickness of a single disc needs to be smaller than 6mm, the load is large, and the single disc spring cannot meet the requirement, the form of combining the disc spring without a supporting surface is selected according to the disc spring standard GB/T1972 plus 2005, and the optimization design of the disc spring parameters is carried out by adopting a Matlab genetic algorithm tool box.
Designing variables: the main parameters related to the design of the disc spring comprise the thickness (t) of the disc spring, the outer diameter (D) of the disc spring, the inner diameter (D) of the disc spring, the deformation (f) of the single disc spring and the deformation (h) of the disc spring when the disc spring is flattened0). According to the original structural size limitation of the buffer, a certain gap (determined as 0.5mm by a table lookup) is required to be reserved when the size of the inner diameter and the outer diameter of the disc spring is changed when the disc spring is deformed, and the outer diameter D of the disc spring and the inner diameter D of the disc spring can be determined to be 32mm and 13 mm. The residual unknown variables are the thickness (t) of the disc spring, the deformation (f) of the single disc spring and the deformation (h) of the disc spring when being pressed0) Determining the initial range of each parameter according to engineering experience by combining the group number i and the lamination number n as follows: 0<t<4，0<f<2，0<h0<10，1≤i≤5，1≤n≤10。
An objective function: height H of single disc spring0The expression is as follows:
wherein
The included angle between the lower surface of the disc spring and the horizontal plane and the total height of the disc spring in a free state are Hz＝i*H0. Considering that the original damper spring has an installation length of 56mm and a precompression of 0.3mm is required for the disc spring, an objective function f (x) can be defined to minimize the difference between the total height of the disc spring and 56.3 mm.
f(x)＝min(Hz-56.3) formula four;
constraint conditions are as follows: the single group load Fz is more than 3000N;
in order to obtain a larger safety factor, the stress of the single sheet is less than 180 MPa;
σOMless than or equal to 180 formula six;
parameters of two forms of involution combined disc springs and composite combined disc springs are obtained through optimization, fig. 14 is a schematic diagram of an optimization result of the involution combined disc spring buffer utilizing the damping alloy vibration reduction method according to the embodiment of the invention, and as shown in fig. 14, table 2 is design parameters of involution combined disc springs.
TABLE 2
From table 2, it can be seen that the optimization result of the pair-disc-spring type manganin-based damping alloy buffer is that 8 disc springs are placed in a pair, and the single-piece load of the 8 pair-disc-spring buffer is 3365.05N by substituting the parameters into the formula one, and the stress of the single-piece disc spring is 114.25Mpa, which is smaller than the damping alloy yield strength 240Mpa, thereby satisfying the strength requirement. FIG. 15 shows eight involutions using damping alloy damping method according to an embodiment of the present invention
TABLE 3
FIG. 16 is a schematic diagram of the optimization result of the composite combined disc spring using the damping alloy damping method according to the embodiment of the present invention; it can be known from the table that the optimization result of the composite disc spring type manganin-based damping alloy buffer is 3 disc springs are overlapped, 8 groups of disc springs are oppositely arranged, fig. 17 is a schematic diagram of the combination form of 24 composite combined disc springs by using the damping alloy vibration reduction method in the embodiment of the invention, and the single load of the 24 composite disc spring buffer is F-1058.03N, the stress of the single disc spring is 178.68Mpa, the overall load is 3413N, the strength is 178.68Mpa, and the total deformation amount is 0.27 x 2 x 4-2.16 mm by substituting the parameters into the formula one.
finite element modeling is carried out on the manganese-copper-based damping alloy disc spring structure, and the original rectangular spring structure is replaced. And (3) carrying out modal analysis on weapon stations provided with different manganin-based damping alloy disc spring structures, wherein the table 4 shows the comparison result of the natural frequencies of the weapon stations provided with different buffers. FIG. 18 is a schematic view of an 8-piece involutory combined disc spring made of a manganese-copper-based damping alloy by using a damping alloy damping method according to an embodiment of the present invention; FIG. 19 is a manganese-copper based damping alloy 24-piece composite disc spring using a damping alloy damping method according to an embodiment of the present invention;
TABLE 4
As can be seen from the table, the inherent frequency of the first six orders of the whole weapon station provided with the manganese-copper-based damping alloy disc spring buffer is basically unchanged, so that the inherent vibration characteristic of the original weapon station is basically not changed by the proposed structural scheme.
In order to determine the response amplitude of a weapon station equipped with different damping alloy disc spring dampers in a frequency domain range, harmonic response analysis is performed.
FIG. 20 is a schematic diagram comparing the results of the muzzle X-direction harmonic response analysis acceleration using the damping alloy damping method according to the embodiment of the present invention; FIG. 21 is a schematic diagram comparing the results of the analysis of the acceleration of the muzzle Y-direction harmonic response by the damping alloy damping method according to the embodiment of the present invention; FIG. 22 is a schematic diagram comparing the results of Z-direction harmonic response analysis of the muzzle with damping alloy damping method according to the embodiment of the present invention; as can be seen from fig. 20 to 22, the weapon station using the buffer in the form of the manganin-based damping alloy disc spring has better vibration suppression effect in three directions, and the acceleration amplitude reduction effect of the 8-piece involutory combined manganese-copper-based damping alloy disc spring buffer is better than that of the 24-piece composite combined manganese-copper-based damping alloy disc spring buffer. Vibration acceleration levels of different buffer vibration reduction schemes in the frequency domain range of 0-150Hz, and vibration acceleration levels (dB) of different manganin-based damping alloy buffer structure vibration reduction schemes in a table 5;
TABLE 5
As can be seen from the table, the average reduction of the manganin-based damping alloy disc spring buffer in the X direction is 14.08dB, the average reduction of the Z direction is 12.47dB and the average reduction of the Y direction is 2.21dB compared with the original weapon station, and the vibration acceleration response of the manganin-based damping alloy disc spring buffer during muzzle shooting can be determined to be reduced within 0-150 Hz. The specific damping effect of both dampers still needs to be determined by nonlinear transient analysis.
The step 3 comprises the following steps: and finally, optimally designing the primary damping alloy application schemes of different application parts by adopting nonlinear transient analysis, quantitatively analyzing the damping effect, and determining the final damping design scheme of each part. The method specifically comprises the following steps: nonlinear transient analysis is carried out on the manganese-copper-based damping alloy disc spring buffer, and boundary conditions and loading conditions are determined;
in order to reduce the workload of nonlinear analysis, the buffer is taken as an analysis object. The buffer mainly bears recoil force generated when the machine gun shoots, the recoil force compresses the rectangular cylindrical spring to do work, one part of the recoil force is converted into elastic potential energy, the other part of the recoil force is converted into internal energy to be dissipated, and the working environment of the buffer is simply related to the gun body and the cradle. Therefore, the buffers can be simplified to be fixed on a rectangular steel plate by combining the structural distribution of the buffers on the cradle, the guide rod is subjected to recoil transmitted by the gun body, finite element models of different buffer structures are established and gridded, and fig. 23 is a schematic diagram of a rectangular cylindrical spiral spring buffer by using a damping alloy vibration reduction method in the embodiment of the invention; the rectangular cylindrical spiral spring buffer is divided into 233724 grids with 130792 cells, and FIG. 24 is a schematic diagram of a manganese-copper-based damping alloy 8-piece involutory combined disc spring buffer utilizing a damping alloy damping method in the embodiment of the invention;
the 8-piece involution combined disc spring buffer of the manganese-copper-based damping alloy is divided into 175140 nodes of grids and 66831 units, and fig. 25 is a schematic diagram of a 24-piece composite combined disc spring buffer of the manganese-copper-based damping alloy by using a damping alloy vibration reduction method in the embodiment of the invention; the manganese-copper-based damping alloy 24-piece composite combined disc spring buffer is divided into 221910 nodes of grid and 73329 units.
The method comprises the following steps that a rectangular plate simulates a buffer fixing surface on a cradle, the head of a guide rod loads horizontal backward inner ballistic force, four fixing bolts fix a buffer base on the rectangular plate, the pretightening force is 11712N, the guide rod of the buffer, a spring and a disc spring are defined to be in friction contact, the disc spring and the disc spring are defined to be in friction contact, 4 calculation steps are divided into 1.05s, the first calculation step 1s is a static loading step, the precompression amount and the bolt pretightening force of each buffer structure are mainly loaded, the precompression amount of the spring is 8mm, the precompression amount of a manganese-copper-based damping alloy disc spring buffer is 0.3mm, and the bolt pretightening force is 11712N; and the subsequent three time steps are transient analysis time steps, stress loading of the impact load is carried out, and the dynamic response condition of the structure is resolved. FIG. 26 is a schematic diagram of a transient analysis impact load of a damper using a damping alloy damping method according to an embodiment of the present invention, as shown in FIG. 26: as the static pressure test result of the spring shows that the impact load actually borne by the spring is not more than 3000N, the impact load is defined as a force with the size of 3000N and the duration of 0.002s in combination with the internal ballistic force peak value of 0.002 s;
obtaining non-linear transientsAnd (3) analysis results: firstly, whether the strength of the manganese-copper-based damping alloy disc spring buffer under 3000N impact load meets the requirement is checked. The position of the disc spring structure of the manganese-copper-based damping alloy with larger strain is mainly concentrated on the outer diameter edge and the inner diameter upper end of the disc spring, which is consistent with the actual situation, and the maximum strain of 8 involutory combined disc springs of the manganese-copper-based damping alloy can reach 1.197x10-3The maximum strain of the 24 composite disc springs can reach 1.853x10-3And the strain is in the elastic range, which indicates that the scheme design meets the structural strength requirement. Selecting the rear end face of the buffer as an acceleration acquisition face, and only comparing acceleration values of different buffers in the X direction because the buffer switches off the acceleration attenuation value in the loading direction of the injection impact load;
FIG. 27 is a schematic view of the X-direction acceleration response under different bumper shock loads using the damping alloy damping method according to an embodiment of the present invention; the rectangular cylindrical spring buffer of the original weapon station has large vibration and small acceleration amplitude attenuation after being impacted, which indicates that the damping energy consumption effect is poor. The acceleration amplitude attenuation of the novel manganese-copper-based damping alloy disc spring buffer is larger than that of the original spring buffer, but the acceleration attenuation capacity of the 24 composite combined manganese-copper-based damping alloy disc springs is better than that of the 8 involutory combined disc springs, and the result of the harmonic response analysis is opposite. The reason is that the harmonic response cannot reflect the nonlinear condition of the damping alloy, the strain amplitude of the manganese-copper-based damping alloy 24 composite combined disc spring is large, the damping performance of the manganese-copper-based damping alloy is in positive correlation with the strain amplitude, and the vibration energy is absorbed by the friction force between the sheets in the superposition mode. The vibration acceleration levels of different damping alloy disc spring buffers are expressed as nonlinear transient analysis vibration acceleration levels (dB) under the impact load action of different buffers.
TABLE 6
As can be seen from the table, the vibration acceleration level of the original rectangular cylindrical spring buffer in the X direction is 172.74dB, the manganese-copper-based damping alloy 8-piece involution combined disc spring buffer is 166.13dB and can be relatively reduced by 6.61dB, the manganese-copper-based damping alloy 24-piece composite combined disc spring buffer is 163.27dB and can be relatively reduced by 9.47dB, and the reduction amplitude is relatively large.
In order to reflect the vibration reduction effect more vividly, the vibration acceleration level can be converted into an acceleration effective value, the acceleration effective value of the original rectangular cylindrical spring buffer in the X direction is 433.72m/s2, the manganese-copper-based damping alloy 8-piece oppositely-combined disc spring buffer is 202.60m/s2 and can be relatively reduced by 53.29%, and the manganese-copper-based damping alloy 24-piece composite combined disc spring buffer is 145.64m/s2 and can be relatively reduced by 66.42%.
Therefore, the novel manganese-copper-based damping alloy disc spring buffer can effectively buffer impact load, and the damping effect of the 24-piece composite combined disc spring buffer is superior to that of the 8-piece involutory combined disc spring buffer.
By considering the nonlinear constitutive relation of the damping alloy, whether the vibration damping structure has the vibration damping effect or not can be preliminarily analyzed by adopting the harmonic response of the linear mode, the analysis time is saved, and the calculation efficiency is improved. But the quantitative analysis of the vibration reduction effect needs to be completed by means of nonlinear transient analysis of nonlinear constitutive relation of the manganese-copper-based damping alloy.
System embodiment
According to an embodiment of the present invention, there is provided a system for damping vibration by using a damping alloy, and fig. 28 is a schematic view of the system for damping vibration by using a damping alloy according to an embodiment of the present invention, as shown in fig. 28, specifically including:
the modal analysis module 10: determining the natural frequency and the vibration mode of a vibration-damped object through modal analysis, and determining the application part of the damping alloy on the vibration-damped object according to the natural frequency and the vibration mode of the vibration-damped object and by combining the vibration transmission path of the vibration-damped object;
the modality analysis module 10 is specifically configured to: and determining the natural frequency and the vibration mode of the vibration-damped object by carrying out modal analysis on the finite element model, and determining the application part of the damping alloy on the vibration-damped object according to the natural frequency and the vibration mode of the vibration-damped object and the vibration transmission path of the vibration-damped object.
Preliminary scheme module 11: determining a damping alloy application preliminary scheme qualitatively through a harmonic response analysis of a linear mode aiming at different application parts of the damping alloy;
the preliminary scheme module 11 is specifically configured to: the method comprises the steps of carrying out finite element modeling on damping alloy application, replacing the structure of the original vibration-damped object with the damping alloy application to carry out modal harmonic response analysis, and qualitatively determining the damping alloy application preliminary scheme.
Final scenario module 12: the damping alloy application preliminary schemes of different application parts are optimally designed through analysis, the damping effect is quantitatively analyzed, and the final damping design scheme of each part of the object to be damped is determined.
The final scenario module 12 is specifically configured to: and optimally designing the damping alloy application preliminary schemes of different application parts through nonlinear transient analysis, quantitatively analyzing the damping effect, and determining the final damping design scheme of each part of the damped object.
The embodiment of the present invention is a system embodiment corresponding to the above method embodiment, and specific operations of each module may be understood with reference to the description of the method embodiment, which is not described herein again.
Apparatus embodiment one
An embodiment of the present invention provides a damping alloy for damping vibration, as shown in fig. 29, including: a memory 200, a processor 220 and a computer program stored on the memory 200 and executable on the processor 220, the computer program, when executed by the processor, implementing the steps of the above-described method embodiments.
Device embodiment II
The embodiment of the present invention provides a computer-readable storage medium, on which an implementation program for information transmission is stored, and when the program is executed by the processor 220, the steps in the above method embodiment are implemented.
The computer-readable storage medium of this embodiment includes, but is not limited to: ROM, RAM, magnetic or optical disks, and the like. It will be apparent to those skilled in the art that the modules or steps of the invention described above may be implemented by a general purpose computing device, they may be centralized on a single computing device or distributed across a network of multiple computing devices, and alternatively, they may be implemented by program code executable by a computing device, such that they may be stored in a storage device and executed by a computing device, and in some cases, the steps shown or described may be performed in an order different than that described herein, or they may be separately fabricated into individual integrated circuit modules, or multiple ones of them may be fabricated into a single integrated circuit module. Thus, the present invention is not limited to any specific combination of hardware and software. Finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention, and not to limit the same; although the present invention has been described in detail with reference to the foregoing embodiments, it should be understood by those skilled in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; the modifications or the replacement of the technical solutions of the embodiments of the present invention do not make the essence of the corresponding technical solutions depart from the scope of the present invention.
Claims (10)
1. A method for reducing vibration by using damping alloy is characterized by comprising the following steps,
s1, determining the natural frequency and the vibration mode of the vibration-damped object through modal analysis, and determining the application part of the damping alloy on the vibration-damped object according to the natural frequency and the vibration mode of the vibration-damped object and the vibration transmission path of the vibration-damped object;
s2, determining a preliminary scheme of the damping alloy application by analyzing and qualitatively the harmonic response of the linear mode of the damping alloy according to different application parts of the damping alloy;
and S3, performing optimization design on the damping alloy application preliminary schemes of different application parts through analysis, quantitatively analyzing the damping effect, and determining the final damping design scheme of each part of the object to be damped.
2. The method according to claim 1, wherein the S1 specifically includes: and determining the natural frequency and the vibration mode of the vibration-damped object by carrying out modal analysis on the finite element model, and determining the application part of the damping alloy on the vibration-damped object according to the natural frequency and the vibration mode of the vibration-damped object and the vibration transmission path of the vibration-damped object.
3. The method according to claim 2, wherein the S2 specifically includes: the method comprises the steps of carrying out finite element modeling on damping alloy application, replacing the structure of the original vibration-damped object with the damping alloy application to carry out modal harmonic response analysis, and qualitatively determining the damping alloy application preliminary scheme.
4. The method according to claim 3, wherein the S3 specifically comprises: and optimally designing the damping alloy application preliminary schemes of different application parts through nonlinear transient analysis, quantitatively analyzing the damping effect, and determining the final damping design scheme of each part of the damped object.
5. A system for damping vibration with a damping alloy, comprising:
a modal analysis module: the device comprises a vibration damping alloy, a vibration absorption body and a vibration absorption body, wherein the vibration absorption body is used for absorbing vibration of the vibration absorption body;
a preliminary scheme module: the preliminary scheme is used for qualitatively determining the damping alloy application by the analysis of the harmonic response of the linear mode aiming at different application parts of the damping alloy;
a final scheme module: the method is used for carrying out optimization design on the damping alloy application preliminary schemes of different application parts through analysis, quantitatively analyzing the damping effect and determining the final damping design scheme of each part of the damped object.
6. The system of claim 5, wherein the modality analysis module is specifically configured to: and determining the natural frequency and the vibration mode of the vibration-damped object by carrying out modal analysis on the finite element model, and determining the application part of the damping alloy on the vibration-damped object according to the natural frequency and the vibration mode of the vibration-damped object and the vibration transmission path of the vibration-damped object.
7. The system of claim 6, wherein the preliminary solution module is specifically configured to: the method comprises the steps of carrying out finite element modeling on damping alloy application, replacing the structure of the original vibration-damped object with the damping alloy to carry out modal harmonic response analysis, and qualitatively determining the damping alloy application preliminary scheme.
8. The system of claim 7, wherein the final solution module is specifically configured to: and optimally designing the damping alloy application preliminary schemes of different application parts through nonlinear transient analysis, quantitatively analyzing the damping effect, and determining the final damping design scheme of each part of the damped object.
9. A device for damping vibration using a damping alloy, comprising: memory, a processor and a computer program stored on the memory and executable on the processor, the computer program, when executed by the processor, implementing the steps of the method of damping vibration with a damping alloy as claimed in any one of claims 1 to 4.
10. A computer-readable storage medium, characterized in that the computer-readable storage medium has stored thereon an information transfer implementing program which, when being executed by a processor, implements the steps of the method for damping vibration with a damping alloy according to any one of claims 1 to 4.
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