Damping alloy vibration reduction method, system and device

Abstract

The present invention discloses a method, system and device for vibration reduction using damping alloys, including: S1, determining the natural frequency and vibration mode of the damped object through modal analysis, and determining the application position of the damping alloy in the damped object according to the natural frequency and vibration mode of the damped object and in combination with the vibration transmission path of the damped object; S2, qualitatively determining the preliminary application plan of the damping alloy for different application positions of the damping alloy through linear modal and harmonious response analysis; S3, optimizing the preliminary application plan of the damping alloy for different application positions through analysis, quantitatively analyzing the vibration reduction effect, and determining the final vibration reduction design plan for each position of the damped object. The present invention takes into account the nonlinear constitutive relationship of the damping alloy, and uses linear modal and harmonious response to preliminarily analyze whether the vibration reduction structure has a vibration reduction effect, saving analysis time and improving calculation efficiency.

Description

Technical Field

[0001] The invention relates to the field of damping alloy design and application, and in particular to a damping alloy vibration reduction method, system and device. Background Art

[0002] The traditional damping alloy vibration reduction design method is to treat the damping alloy as a linear elastic material, only set a constant damping coefficient to reflect its damping capacity, use modal analysis to study the vibration mode and natural frequency of the structure, determine the key modification parts, and then design the vibration reduction structure, and determine the vibration reduction amplitude through harmonic response analysis. However, damping alloys are essentially non-linear elastic materials and their damping capacity is related to the loading conditions. Linear constitutive and constant damping coefficients will cause deviations in the design and optimization of damping structures. Moreover, modal analysis, harmonic response analysis, and rigid-flexible coupling dynamics analysis in traditional vibration reduction design are mainly based on the linear assumption of constant stiffness. Even if the material nonlinearity is defined, it will be ignored, and it is difficult to reflect the nonlinear constitutive relationship of damping alloys. Summary of the invention

[0003] The purpose of the present invention is to provide a method for reducing vibration by using a damping alloy, aiming to solve the problem of reducing vibration by using a damping alloy.

[0004] The present invention provides a method for vibration reduction using a damping alloy, comprising: S1, determining the natural frequency and vibration mode of a damped object through modal analysis, and determining the application position of the damping alloy in the damped object according to the natural frequency and vibration mode of the damped object and in combination with the vibration transmission path of the damped object; S2, qualitatively determining a preliminary application plan of the damping alloy for different application positions of the damping alloy through linear modal and harmonic response analysis; S3, optimizing the design of the preliminary application plan of the damping alloy for different application positions through analysis, quantitatively analyzing the vibration reduction effect, and determining the final vibration reduction design plan for each position of the damped object.

[0005] The present invention also provides a system for reducing vibration using a damping alloy, comprising:

[0006] Modal analysis module: determining the natural frequency and vibration mode of the damped object through modal analysis, and determining the application position of the damping alloy in the damped object according to the natural frequency and vibration mode of the damped object and the vibration transmission path of the damped object;

[0007] Preliminary scheme module: for different application parts of the damping alloy, the preliminary scheme of the damping alloy application is qualitatively determined through linear modal and harmonic response analysis;

[0008] Final solution module: By analyzing the preliminary application solutions of damping alloys in different application parts, the design is optimized, the vibration reduction effect is quantitatively analyzed, and the final vibration reduction design solutions for each part of the damped object are determined.

[0009] An embodiment of the present invention further provides a device for reducing vibration using a damping alloy, comprising: a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the computer program implements the steps of the above method when executed by the processor.

[0010] An embodiment of the present invention further provides a computer-readable storage medium, on which a program for implementing information transmission is stored, and when the program is executed by a processor, the steps of the above method are implemented.

[0011] By adopting the embodiment of the present invention, the nonlinear constitutive relationship of the damping alloy is taken into consideration, and the linear modal and harmonious response are used to preliminarily analyze whether the vibration reduction structure has a vibration reduction effect, thereby saving analysis time and improving calculation efficiency.

[0012] The above description is only an overview of the technical solution of the present invention. In order to more clearly understand the technical means of the present invention, it can be implemented according to the contents of the specification. In order to make the above and other purposes, features and advantages of the present invention more obvious and easy to understand, the specific implementation methods of the present invention are listed below. BRIEF DESCRIPTION OF THE DRAWINGS

[0013] In order to more clearly illustrate the specific implementation methods of the present invention or the technical solutions in the prior art, the drawings required for use in the specific implementation methods or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are some implementation methods of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0014] Figure 1 is a flow chart of a vibration reduction method using a damping alloy according to an embodiment of the present invention;

[0015] Figure 2 Schematic diagram of the constraint situation of the vibration reduction method using damping alloy according to an embodiment of the present invention;

[0016] Figure 3 is a schematic diagram of the first-order vibration mode of a weapon station using a damping alloy vibration reduction method according to an embodiment of the present invention;

[0017] Figure 4 is a schematic diagram of the second-order vibration mode of a weapon station using a damping alloy vibration reduction method according to an embodiment of the present invention;

[0018] Figure 5 is a schematic diagram of the third-order vibration mode of a weapon station using a damping alloy vibration reduction method according to an embodiment of the present invention;

[0019] Figure 6is a schematic diagram of the fourth-order vibration mode of a weapon station using a damping alloy vibration reduction method according to an embodiment of the present invention;

[0020] Figure 7 is a schematic diagram of the fifth-order vibration mode of a weapon station using a damping alloy vibration reduction method according to an embodiment of the present invention;

[0021] Figure 8 is a schematic diagram of the 6th-order vibration mode of a weapon station using a damping alloy vibration reduction method according to an embodiment of the present invention;

[0022] Fig. 9 Schematic diagram of a manganese-copper-based damping alloy disc spring buffer using a damping alloy vibration reduction method according to an embodiment of the present invention;

[0023] Fig.10 Schematic diagram of a static pressure curve of a buffer spring using a damping alloy vibration reduction method according to an embodiment of the present invention;

[0024] Fig.11 It is a schematic diagram of calculating the load and deformation of the disc spring stack using the damping alloy vibration reduction method according to an embodiment of the present invention;

[0025] Fig.12 It is a schematic diagram of calculating the load and deformation of the disc spring pairing using the damping alloy vibration reduction method according to an embodiment of the present invention;

[0026] Fig.13 It is a schematic diagram of calculating the load and deformation of the composite disc spring using the damping alloy vibration reduction method according to an embodiment of the present invention;

[0027] Fig.14 It is a schematic diagram of the optimization result of the combined disc spring buffer using the damping alloy vibration reduction method according to the embodiment of the present invention;

[0028] Fig.15 It is a schematic diagram of the combination of eight disc springs using the damping alloy vibration reduction method according to an embodiment of the present invention;

[0029] Fig.16 1. It is a schematic diagram of the optimization result of the composite combined disc spring using the damping alloy vibration reduction method according to an embodiment of the present invention;

[0030] Fig.17 It is a schematic diagram of the combination form of 24 composite disc springs using the damping alloy vibration reduction method according to an embodiment of the present invention;

[0031] Fig.18 It is a schematic diagram of a manganese-copper-based damping alloy eight-piece combined disc spring using a damping alloy vibration reduction method according to an embodiment of the present invention;

[0032] Fig.19 It is a composite disc spring of 24 pieces of manganese-copper-based damping alloy using a damping alloy vibration reduction method according to an embodiment of the present invention;

[0033] Fig. 20 1 is a schematic diagram comparing acceleration results of muzzle X-direction harmonic response analysis using a damping alloy vibration reduction method according to an embodiment of the present invention;

[0034] Fig.21 1 is a schematic diagram comparing acceleration results of Y-direction harmonic response analysis of a muzzle using a damping alloy vibration reduction method according to an embodiment of the present invention;

[0035] Fig. 22 1 is a schematic diagram comparing acceleration results of a muzzle Z-direction harmonic response analysis using a damping alloy vibration reduction method according to an embodiment of the present invention;

[0036] Fig.23 Schematic diagram of a rectangular cylindrical helical spring buffer using a damping alloy vibration reduction method according to an embodiment of the present invention;

[0037] Fig.24 It is a schematic diagram of a manganese-copper-based damping alloy eight-piece combined disc spring buffer using a damping alloy vibration reduction method according to an embodiment of the present invention;

[0038] Fig.25 Schematic diagram of a 24-piece composite disc spring buffer of manganese-copper-based damping alloy using a damping alloy vibration reduction method according to an embodiment of the present invention;

[0039] Fig.26 Schematic diagram of transient analysis impact load of a buffer using a damping alloy vibration reduction method according to an embodiment of the present invention;

[0040] Fig. 27 1 is a schematic diagram of the acceleration response in the X direction under different buffer impact loads using the damping alloy vibration reduction method according to an embodiment of the present invention;

[0041] Fig.28 is a schematic diagram of a vibration reduction system using a damping alloy according to an embodiment of the present invention;

[0042] Fig.29 Schematic diagram of a vibration reduction device using a damping alloy according to an embodiment of the present invention.

[0043] Description of reference numerals:

[0044] 10: Modal analysis module; 11: Preliminary solution module; 12: Final solution module; 1: Nut; 2: Guide rod; 3: Rectangular spring; 4: Base; 5: Sleeve; 6: Pressing nut. DETAILED DESCRIPTION

[0045] The technical solution of the present invention will be described clearly and completely in conjunction with the embodiments below. Obviously, the embodiments described are part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments in the present invention, all other embodiments obtained by ordinary technicians in the field without creative work belong to the scope of protection of the present invention. In the description of the present invention, it should be understood that the orientation or position relationship indicated by the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise" and the like are based on the orientation or position relationship shown in the drawings, which is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation of the present invention. In addition, the terms "first" and "second" are only used for descriptive purposes, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Therefore, the features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, "multiple" means two or more than two, unless otherwise clearly and specifically defined. In addition, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0046] Method Embodiment

[0047] According to an embodiment of the present invention, a method for reducing vibration using a damping alloy is provided. Figure 1 Flow chart of the vibration reduction method using damping alloy according to an embodiment of the present invention. Figure 1 As shown, specifically including:

[0048] S1. Determine the natural frequency and vibration mode of the object to be damped by modal analysis, and determine the application position of the damping alloy in the object to be damped according to the natural frequency and vibration mode of the object to be damped and in combination with the vibration transmission path of the object to be damped; S1 specifically includes: determine the natural frequency and vibration mode of the object to be damped by performing modal analysis on a finite element model, and determine the application position of the damping alloy in the object to be damped according to the natural frequency and vibration mode of the object to be damped and in combination with the vibration transmission path of the object to be damped.

[0049] S2. For different application parts of the damping alloy, a preliminary application plan of the damping alloy is qualitatively determined through linear modal and harmonic response analysis; S2 specifically includes: by performing finite element modeling on the damping alloy application, the structure of the original damped object is replaced with the damping alloy application to perform modal and harmonic response analysis, and the preliminary application plan of the damping alloy is qualitatively determined.

[0050] S3. Optimize the design of the preliminary damping alloy application scheme for different application parts through analysis, quantitatively analyze the vibration reduction effect, and determine the final vibration reduction design scheme for each part of the damped object. S3 specifically includes: Optimize the design of the preliminary damping alloy application scheme for different application parts through nonlinear transient analysis, quantitatively analyze the vibration reduction effect, and determine the final vibration reduction design scheme for each part of the damped object.

[0051] According to the above method, the specific implementation method is as follows, which can be known from the principles of modal analysis and harmonic response analysis:

[0052] (1) Modal analysis mainly assumes that the stiffness matrix and mass matrix of the structure do not change, and there is no load in the structure that changes with time. Therefore, the modal analysis of traditional manganese-copper-based damping alloys assumes that the stiffness and damping coefficient of the damping alloy are constants, which is inconsistent with the nonlinear constitutive relationship of manganese-copper-based damping alloys - the changing stiffness matrix and damping coefficient, and therefore will produce errors with the actual situation. However, if the changing damping coefficient and stiffness matrix are to be considered, it is equivalent to solving an infinite number of second-order homogeneous linear differential equations with constant coefficients, which will increase the results of modal analysis by many factors, which is not conducive to engineering applications.

[0053] (2) Harmonic response analysis is also based on the linear assumption. It only analyzes the forced vibration section and ignores the initial vibration section and other nonlinear factors. The nonlinear constitutive relationship of manganese-copper-based damping alloy cannot be reflected in the existing harmonic response analysis. If nonlinear harmonic response analysis is to be realized, it can only be achieved through nonlinear transient analysis, expressing the simple harmonic load as a time-history load function, and continuously changing the frequency of the simple harmonic load for nonlinear transient analysis to obtain a series of discrete points and draw the relationship between the structural vibration amplitude and frequency. However, repeated iterative nonlinear transient calculations will incur a particularly huge computational cost, which is not conducive to simulation analysis.

[0054] (3) From another perspective, the existing modal analysis and harmonic response analysis are not meaningless. The linear modal and harmonic response analysis requires less computing resources, is mature in technology, and has been widely verified. Manganese-copper-based damping alloy is indeed a damping material. When a fixed damping coefficient and stiffness matrix are set for it, it is also a manifestation of its damping capacity and material properties in finite element analysis. The original system without adding damping alloy meets the requirements of linear modal and harmonic response analysis and is not affected. The damping alloy structure set with the existing fixed damping coefficient and stiffness matrix can be compared with the original structure to qualitatively analyze whether it has a vibration reduction effect. Moreover, the fixed damping coefficient and stiffness matrix mainly affect the amplitude calculation of structural vibration, and the frequency has little effect. Because the addition of damping alloy is mainly to not change the stiffness of the original structure, it can be approximately considered that the structural stiffness and natural frequency do not change much. Therefore, the use of linear modal and harmonious response can preliminarily analyze whether the vibration reduction structure has a vibration reduction effect, saving analysis time and improving calculation efficiency. However, the quantitative analysis of the vibration reduction effect needs to be completed by nonlinear transient analysis including the nonlinear constitutive relationship of manganese-copper-based damping alloy.

[0055] Taking the above factors into consideration, the vibration reduction design method of the remote control weapon station containing manganese-copper based damping alloy should first determine the natural frequency and vibration mode through modal analysis, determine the application part of the damping alloy in combination with the vibration transmission path, and then carry out the damping alloy application design. The preliminary application scheme of the damping alloy for each component is qualitatively determined through linear modal and harmonious response analysis. Finally, nonlinear transient analysis is used to optimize the preliminary application scheme of the damping alloy for different application parts, quantitatively analyze the vibration reduction effect, and determine the final vibration reduction design scheme for each part.

[0056] The existing vibration reduction design method for manganese-copper-based damping alloys does not consider the nonlinear constitutive relationship of damping alloys, but simply treats them as linear elastic materials and sets a constant damping coefficient to reflect the damping capacity. However, the stress-strain relationship of manganese-copper-based damping alloys is related to strain amplitude, strain frequency and temperature, and changes accordingly. Therefore, it is very necessary to propose a vibration reduction design method suitable for manganese-copper-based damping alloys.

[0057] Step 1: First, determine the natural frequency and vibration mode of the damped object through modal analysis, and determine the application location of the damping alloy in combination with the vibration transmission path;

[0058] Step 2: Then carry out damping alloy application design, and qualitatively determine the preliminary damping alloy application plan for each component through linear modal and harmonic response analysis;

[0059] Step 3. Finally, nonlinear transient analysis is used to optimize the preliminary application scheme of damping alloys in different application parts, quantitatively analyze the vibration reduction effect, and determine the final vibration reduction design scheme for each part.

[0060] The following is an example of the damping alloy application design of the weapon station:

[0061] Step 1 includes: firstly, performing modal analysis on the finite element model of the weapon station to determine its natural frequency and the location of the largest vibration, and determining the vibration reduction design modification parts. Set the ground under the seat ring as a fixed constraint, Figure 2 FIG. 1 is a schematic diagram of the constraint situation of the vibration reduction method using damping alloy according to an embodiment of the present invention: Figure 2 The first 20 modes of the weapon station are analyzed, and the results are shown in Table 1 as the mode shape table;

[0062] Table 1

[0063]

[0064] It can be seen from Table 1 that the overall modal frequencies of the weapon station are relatively low, with the first-order frequency being 46.79 Hz and the 20th-order frequency being 437.72 Hz. The range is relatively small, indicating that the overall mass is relatively heavy, and the first few frequencies are quite different from the machine gun firing frequency (10 Hz, 600 rounds / min). Figure 3 is a schematic diagram of the first-order vibration mode of a weapon station using a damping alloy vibration reduction method according to an embodiment of the present invention; Figure 4 is a schematic diagram of the second-order vibration mode of a weapon station using a damping alloy vibration reduction method according to an embodiment of the present invention; Figure 5 is a schematic diagram of the third-order vibration mode of a weapon station using a damping alloy vibration reduction method according to an embodiment of the present invention; Figure 6 is a schematic diagram of the fourth-order vibration mode of a weapon station using a damping alloy vibration reduction method according to an embodiment of the present invention; Figure 7 is a schematic diagram of the fifth-order vibration mode of a weapon station using a damping alloy vibration reduction method according to an embodiment of the present invention; Figure 8 6 is a schematic diagram of the 6th vibration mode of a weapon station using a damping alloy vibration reduction method according to an embodiment of the present invention; Figures 3 to 8 It can be seen that the low-order modal vibration of the weapon station is mainly bending deformation. The first two orders are mainly concentrated on the bending vibration of the barrel, the last four orders are concentrated on the cradle, bracket, magazine and sighting device, the third order is left and right bending vibration, the fourth order is the up and down polarization of the sighting device, the fifth order is the up and down bending of the barrel, cradle, sighting device, and the sixth order is the horizontal bending of the barrel and sighting device. The vibration mode of the seat ring changes less, which is caused by the fixed constraint set between it and the ground.

[0065] From the modal results, it can be seen that the vibration of the barrel is large, which is caused by its large length-to-diameter ratio and is difficult to change, and the damping alloy is not suitable for coating the outer layer of the barrel; the vibration of the ammunition box has little effect on the weapon shooting; the vibration of the sighting device belongs to the local mode because of its small mass, and its stiffness can be increased accordingly, but it is not a reference for improving the overall vibration characteristics of the weapon station; the vibration of the bracket is less; therefore, from the modal vibration shape diagram, only the cradle part is suitable for the application of damping alloy vibration reduction, and it has a greater impact on the shooting accuracy of the weapon station.

[0066] The impact load of the weapon station when shooting is transmitted from the gun body to the cradle through the buffer, and the cradle is transmitted to the bracket through the ear shaft and the elevation half gear. The load is then transmitted to the seat ring through the bracket. The seat ring transmits the force to the bearing platform. At the same time, the excitation caused by the road surface excitation or the vehicle body vibration is also transmitted to the muzzle by the seat ring in the opposite direction. From the perspective of the vibration transmission path, the cradle half gear, buffer and seat ring are the more important links in the vibration transmission path, which directly affect the dynamic characteristics of the muzzle.

[0067] Based on the results of modal analysis and vibration transfer path analysis, it is determined that the application direction of the manganese-copper based damping alloy modification is mainly the buffer of the cradle.

[0068] Step 2: Then carry out damping alloy application design, and qualitatively determine the damping alloy application of each component through linear modal and harmonic response analysis. The preliminary plan includes: design of remote control weapon station buffer containing manganese-copper based damping alloy.

[0069] The buffer mainly absorbs the recoil force generated when the machine gun is fired, ensures the smooth recoil of the weapon, buffers and consumes the force and energy transmitted to the mount, and plays a key role in improving the stability of the mount. The buffer of the existing remote control weapon station is mainly a spring buffer. The buffer is connected to the machine gun through a fixed frame. When the gun body recoils, the spring is compressed by the pin rod. Part of the recoil force is converted into elastic force, and part is converted into heat energy dissipation, thereby achieving the buffering purpose. However, ordinary spring buffers have low energy absorption rate, secondary impact, excessive stiffness and other phenomena during the shooting process, which leads to aggravated muzzle vibration and affects the shooting accuracy. In order to overcome the above problems, this paper designs a new manganese-copper based damping alloy disc spring buffer. Fig. 9 It is a schematic diagram of a manganese-copper based damping alloy disc spring buffer utilizing a damping alloy vibration reduction method according to an embodiment of the present invention; the use of a disc spring structure with a high load and small displacement, combined with the special vibration absorption capability of the damping alloy, can not only meet the strength requirements of the buffer, but also improve the damping performance of the buffer.

[0070] The original spring in the buffer is a rectangular coil spring made of 60Si2Mn. The original buffer spring is 56mm long after compression and has a preload of 1848N. In order to obtain accurate mechanical parameters of the original buffer spring, a servo hydraulic testing machine is used for static pressure testing. The spring is vertically mounted on the testing machine platform and uniformly compressed at a speed of 2mm / s. The force and displacement curves are recorded until it enters the yield state and the test is stopped. The force and displacement curves obtained from the test are Fig.10 Schematic diagram of the static pressure curve of the buffer spring using the damping alloy vibration reduction method according to an embodiment of the present invention. Fig.10 shown.

[0071] from Fig.10 It can be seen that the buffer spring enters the yield state after 3kN, and the displacement is 12.98mm. The equivalent stiffness of the buffer spring is calculated to be 231N / mm, indicating that the actual force applied to the buffer is no more than 3000N. Based on this, the manganese-copper based damping alloy disc spring buffer is designed.

[0072] The disc spring design standard refers to the disc spring standard GB / T 1972-2005, and the strength calculation is based on the disc spring design empirical formula introduced in the mechanical design manual.

[0073] The load calculation formula for a single disc spring is:

[0074]

[0075] Where: 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; h0 is the calculated value of the deformation when the disc spring is flattened, mm; E is the elastic modulus of the disc spring material, MPa; calculation coefficient in is the diameter ratio, d is the inner diameter of the disc spring; for the disc spring without support surface, K4=1.

[0076] The stress calculation formula of a single disc spring is:

[0077]

[0078] Where σ OM ——Stress of single disc spring, MPa; μ——Poisson’s ratio.

[0079] Since a single disc spring is generally difficult to meet the requirements of load and deformation, disc springs are generally used in combination. The main application forms include overlapping, matching and composite combination. Overlapping means that multiple disc springs are stacked together in the same direction, matching means that multiple disc springs are combined in opposite directions in sequence, and composite combination means overlapping first and then matching to share the load and deformation. Fig.11 FIG. 1 is a schematic diagram of calculating the load and deformation of the disc spring stack using the damping alloy vibration reduction method according to an embodiment of the present invention. Fig.11 As shown in the figure, when the friction force is ignored, the load F of n disc springs of the same specification stacked together Z =n×F, but the deformation amount is the same as that of a single piece.

[0080] Fig.12 FIG. 1 is a schematic diagram of calculating the load and deformation of the disc spring pair using the damping alloy vibration reduction method according to an embodiment of the present invention. Fig.12 As shown in the figure, when the friction force is ignored, the deformation f of i opposite disc springs is Z =i×f, the load is the same as that of a single piece.

[0081] Fig.13 FIG. 1 is a schematic diagram of calculating the load and deformation of a composite disc spring using a damping alloy vibration reduction method according to an embodiment of the present invention. Fig.13 As shown in the figure, when the friction force is ignored, the deformation of the disc spring is f Z =i×f, F Z =n×F The load is the same as that of a single piece.

[0082] When the disc spring adopts a disc spring combination, friction exists at the contact cone surface and the load-bearing edge of the disc spring. The disc spring load increases when loaded and decreases when unloaded. The disc spring load considering the influence of friction is calculated as follows:

[0083]

[0084] Where: F is the load of a single disc spring, f M ——Friction coefficient between the conical surfaces of the disc spring, f R — — Friction coefficient at the load-bearing edge, where the sign is - when loading and + when unloading. In this paper, based on the characteristics of manganese-copper-based damping alloy, the friction coefficient between the conical surfaces of the disc spring is f M Take 0.02, the friction coefficient at the load edge f R Take 0.03.

[0085] Since the manganese-copper-based damping alloy buffer requires a certain amount of deformation to increase the buffering and energy absorption effects, the disc spring cannot be too thick. Combined with the size limitation of the original buffer, the thickness of a single disc needs to be less than 6mm, and the load it is subjected to is large. A single disc spring cannot meet the requirements. Therefore, according to the disc spring standard GB / T 1972-2005, a support-free, combined disc spring is selected, and the genetic algorithm toolbox of Matlab is used to optimize the disc spring parameters.

[0086] Design variables: The main parameters involved in the disc spring design are disc spring thickness (t), disc spring outer diameter (D), disc spring inner diameter (d), single disc spring deformation (f), and disc spring flattening deformation (h0). According to the original structural size restrictions of the buffer, combined with the need to leave a certain gap (0.5mm determined by looking up the table) when the inner and outer diameters of the disc spring will change when deformed, it can be determined that the disc spring outer diameter D = 32mm and the disc spring inner diameter d = 13mm. The remaining unknown variables are disc spring thickness (t), single disc spring deformation (f), disc spring flattening deformation (h0), number of matching groups i, number of overlapping sheets n. Based on engineering experience, the initial range of each parameter is determined as: 0 <t<4,0<f<2,0<h0<10,1≤i≤5,1≤n≤10。

[0087] Objective function: The expression of the height H0 of a single disc spring is:

[0088]

[0089] in is the angle between the lower surface of the disc spring and the horizontal plane, and the total height of the disc spring in the free state is H z =i*H0. Considering that the installation length of the original buffer spring is 56mm and a pre-compression of 0.3mm is required for the disc spring, the objective function f(x) can be defined as the minimum difference between the total height of the disc spring and 56.3mm.

[0090] f(x)=min(H z -56.3) Formula 4;

[0091] Constraints: Single group load Fz greater than 3000N;

[0092]

[0093] In order to obtain a larger safety factor, the single-piece stress is less than 180Mpa;

[0094] σ OM ≤180 Formula 6;

[0095] After optimization, the parameters of the two types of combined disc springs and composite combined disc springs were obtained. Fig.14 FIG. 1 is a schematic diagram of the optimization result of the combined disc spring buffer using the damping alloy vibration reduction method according to an embodiment of the present invention. Fig.14 As shown in Table 2, the design parameters of the combined disc spring are shown.

[0096] Table 2

[0097]

[0098] From Table 2, it can be seen that the optimal result of the manganese-copper-based damping alloy buffer in the form of paired disc springs is 8 disc springs placed in pairs. Substituting the parameters into Formula 1, it can be obtained that the single-piece load of the 8-piece paired disc spring buffer is F=3365.05N, and the stress of the single disc spring is 114.25Mpa, which is less than the yield strength of the damping alloy of 240Mpa, meeting the strength requirements. Fig.15 The eight-piece combination of the damping alloy vibration reduction method of the embodiment of the present invention is

[0099] Table 3

[0100]

[0101] Fig.16 Schematic diagram of the optimization result of the composite disc spring using the damping alloy vibration reduction method in the embodiment of the present invention; From the table, it can be seen that the optimization result of the manganese-copper-based damping alloy buffer in the form of a composite disc spring is 3 disc springs stacked, 8 sets of disc springs are placed in pairs, Fig.17 It is a schematic diagram of the combination form of 24 composite disc springs using the damping alloy vibration reduction method in an embodiment of the present invention. Substituting the parameters into Formula 1, it can be obtained that the single-piece load of the 24-piece 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 is 0.27*2*4=2.16mm.

[0102] Step 2 preliminary plan also includes: Modal analysis of manganese-copper-based damping alloy disc spring buffer:

[0103] The finite element modeling of the manganese-copper-based damping alloy disc spring structure was carried out, and the original rectangular spring structure was replaced. The modal analysis of the weapon station with different manganese-copper-based damping alloy disc spring structures is shown in Table 4. The natural frequency comparison results of the weapon station with different buffers are shown in Table 4. Fig.18 It is a schematic diagram of a manganese-copper-based damping alloy eight-piece combined disc spring using a damping alloy vibration reduction method according to an embodiment of the present invention; Fig.19 It is a 24-piece composite disc spring of manganese-copper-based damping alloy using a damping alloy vibration reduction method according to an embodiment of the present invention;

[0104] Table 4

[0105]

[0106] It can be seen from the table that the natural frequencies of the first six orders of the weapon station installed with the manganese-copper-based damping alloy disc spring buffer remain basically unchanged, so the proposed structural scheme will basically not change the natural vibration characteristics of the original weapon station.

[0107] In order to determine the response amplitude of the weapon station equipped with disc spring buffers of different damping alloys in the frequency domain, a harmonic response analysis was performed.

[0108] Fig. 20 1 is a schematic diagram comparing acceleration results of muzzle X-direction harmonic response analysis using a damping alloy vibration reduction method according to an embodiment of the present invention; Fig.21 1 is a schematic diagram comparing acceleration results of Y-direction harmonic response analysis of a muzzle using a damping alloy vibration reduction method according to an embodiment of the present invention; Fig. 22 FIG. 20 is a schematic diagram showing the comparison of acceleration results of the muzzle Z-direction harmonic response analysis using the damping alloy vibration reduction method according to an embodiment of the present invention; FIG. Fig. 22 It can be seen that the weapon station using the manganese-copper-based damping alloy disc spring buffer has a good vibration suppression effect in three directions, and the acceleration amplitude reduction effect of the manganese-copper-based damping alloy 8-piece combined disc spring buffer is better than that of the manganese-copper-based damping alloy 24-piece composite disc spring buffer. The vibration acceleration level of different buffer vibration reduction schemes in the frequency range of 0-150Hz, Table 5 Vibration acceleration level (dB) of different manganese-copper-based damping alloy buffer structure vibration reduction schemes;

[0109] Table 5

[0110]

[0111] As can be seen from the table, the manganese copper-based damping alloy disc spring buffer is 14.08dB lower than the original weapon station in the X direction, 12.47dB lower in the Z direction, and 2.21dB lower in the Y direction. It can be determined that the manganese copper-based damping alloy disc spring buffer can reduce the vibration acceleration response of the muzzle shooting within 0-150Hz. However, the specific vibration reduction effect of the two buffers still needs to be determined by nonlinear transient analysis.

[0112] Step 3 includes: finally, using nonlinear transient analysis to optimize the preliminary damping alloy application scheme for different application parts, quantitatively analyzing the vibration reduction effect, and determining the final vibration reduction design scheme for each part. Specifically, it includes: nonlinear transient analysis of the manganese-copper-based damping alloy disc spring buffer to determine the boundary conditions and loading conditions;

[0113] In order to reduce the workload of nonlinear analysis, the buffer is taken as the analysis object alone. The buffer mainly bears the recoil force when the machine gun is fired. The recoil compresses the rectangular cylindrical spring to do work, part of which is converted into elastic potential energy and part of which is converted into internal energy dissipation. Its working environment is relatively simple and is only related to the gun body and the cradle. Therefore, combined with the structural distribution of the buffer on the cradle, it can be simplified to be fixed on a rectangular steel plate, and the guide rod is subjected to the recoil force transmitted by the gun body. The finite element model of different buffer structures is established and meshing is performed. Fig.23Schematic diagram of a rectangular cylindrical helical spring buffer using a damping alloy vibration reduction method according to an embodiment of the present invention; the rectangular cylindrical helical spring buffer is divided into a grid of 233724 nodes and 130792 units. Fig.24 It is a schematic diagram of a manganese-copper-based damping alloy eight-piece combined disc spring buffer using a damping alloy vibration reduction method according to an embodiment of the present invention;

[0114] The 8-piece combined disc spring buffer of manganese-copper-based damping alloy is divided into a total of 175,140 nodes and 66,831 units. Fig.25 It is a schematic diagram of a manganese-copper-based damping alloy 24-piece composite disc spring buffer using a damping alloy vibration reduction method according to an embodiment of the present invention; the manganese-copper-based damping alloy 24-piece composite disc spring buffer is divided into a grid of 221,910 nodes and 73,329 units.

[0115] The rectangular plate simulates the buffer fixing surface on the cradle, and the guide rod head is loaded with horizontal backward internal ballistic force. Four fixing bolts fix the buffer base on the rectangular plate. The preload force is 11712N. The buffer guide rod is defined as friction contact with the spring and disc spring, and friction contact is defined between disc springs. It is divided into 4 calculation steps with a total of 1.05s. The first calculation step of 1s is a static loading step, which mainly loads the pre-compression amount and bolt preload force of each buffer structure. The spring pre-compression amount is 8mm, and the pre-compression amount of the manganese-copper based damping alloy disc spring buffer is 0.3mm, and the bolt preload force is 11712N; the subsequent three time steps are transient analysis time steps, which are used to load the impact load and solve the dynamic response of the structure. Fig.26 FIG. 1 is a schematic diagram of the impact load of the buffer transient analysis using the damping alloy vibration reduction method according to an embodiment of the present invention, such as Fig.26 As shown: Since the static pressure test results of the spring show that the actual impact load on the spring is no more than 3000N, combined with the peak value of the internal ballistic force of 0.002s, the impact load is defined as a force of 3000N and a duration of 0.002s;

[0116] The nonlinear transient analysis results are obtained: First, the strength of the manganese-copper-based damping alloy disc spring buffer under a 3000N impact load is tested to see if it meets the requirements. The locations where the structural strain of the manganese-copper-based damping alloy disc spring is large are mainly concentrated at the outer diameter edge and the upper end of the inner diameter of the disc spring, which is consistent with the actual situation. The maximum strain of the manganese-copper-based damping alloy 8-piece combined disc spring can reach 1.197x10 -3 The maximum strain of the 24-piece composite disc spring can reach 1.853x10 -3, the strains are all within the elastic range, indicating that the design scheme meets the structural strength requirements. The rear end surface of the buffer is selected as the acceleration collection surface. Since the buffer focuses on the acceleration attenuation value in the loading direction of the shooting load, only the acceleration values ​​of different buffers in the X direction are compared;

[0117] Fig. 27 It is a schematic diagram of the acceleration response in the X direction under the impact load of different buffers using the damping alloy vibration reduction method of the embodiment of the present invention; the original weapon station rectangular cylindrical spring buffer vibrates more after being impacted, and the acceleration amplitude attenuation is smaller, indicating that its damping energy dissipation effect is poor. The acceleration amplitude attenuation of the new manganese-copper-based damping alloy disc spring buffer is greater than that of the original spring buffer, but the acceleration attenuation ability of the 24-piece composite disc spring of the manganese-copper-based damping alloy is better than that of the 8-piece combined disc spring form, which is contrary to the harmonic response analysis result. This is because the harmonic response cannot reflect the nonlinearity of the damping alloy. The strain amplitude of the 24-piece composite disc spring of the manganese-copper-based damping alloy is larger, while the damping performance of the manganese-copper-based damping alloy is positively correlated with the strain amplitude, and the friction between the sheets in the superimposed form absorbs more vibration energy. The vibration acceleration level of disc spring buffers with different damping alloys is shown in the table as the vibration acceleration level (dB) of the nonlinear transient analysis under the impact load of different buffers.

[0118] Table 6

[0119]

[0120] It can be seen from the table that the vibration acceleration level in the X direction of the original rectangular cylindrical spring buffer is 172.74dB, the 8-piece manganese-copper-based damping alloy combined disc spring buffer is 166.13dB, which can be relatively reduced by 6.61dB, and the 24-piece manganese-copper-based damping alloy composite combined disc spring buffer is 163.27dB, which can be relatively reduced by 9.47dB. The reduction range is relatively large.

[0121] In order to more vividly reflect the vibration reduction effect, the vibration acceleration level can be converted into the effective value of acceleration. The effective value of acceleration in the X direction of the original rectangular cylindrical spring buffer is 433.72m / s2, the 8-piece manganese-copper-based damping alloy combined disc spring buffer is 202.60m / s2, which can be relatively reduced by 53.29%, and the 24-piece manganese-copper-based damping alloy composite combined disc spring buffer is 145.64m / s2, which can be relatively reduced by 66.42%.

[0122] Therefore, the use of a new manganese-copper based damping alloy disc spring buffer can effectively buffer the impact load, and the vibration reduction effect of a 24-piece composite disc spring buffer is better than that of an 8-piece composite disc spring buffer.

[0123] Considering the nonlinear constitutive relationship of the damping alloy, the linear modal and harmonious response can be used to preliminarily analyze whether the vibration reduction structure has a vibration reduction effect, saving analysis time and improving calculation efficiency. However, the quantitative analysis of the vibration reduction effect needs to be completed by nonlinear transient analysis including the nonlinear constitutive relationship of the manganese-copper-based damping alloy.

[0124] System Example

[0125] According to an embodiment of the present invention, a system for reducing vibration using a damping alloy is provided. Fig.28 Schematic diagram of a system utilizing damping alloy for vibration reduction according to an embodiment of the present invention. Fig.28 As shown, specifically including:

[0126] Modal analysis module 10: determining the natural frequency and vibration mode of the damped object through modal analysis, and determining the application position of the damping alloy in the damped object according to the natural frequency and vibration mode of the damped object and in combination with the vibration transmission path of the damped object;

[0127] The modal analysis module 10 is specifically used to determine the natural frequency and vibration mode of the damped object by performing modal analysis on the finite element model, and determine the application position of the damping alloy in the damped object based on the natural frequency and vibration mode of the damped object and the vibration transmission path of the damped object.

[0128] Preliminary scheme module 11: for different application parts of the damping alloy, qualitatively determine the preliminary application scheme of the damping alloy through linear modal and harmonic response analysis;

[0129] The preliminary scheme module 11 is specifically used for: by performing finite element modeling on the damping alloy application, replacing the original structure of the damped object with the damping alloy application to perform modal and harmonious response analysis, and qualitatively determining the preliminary scheme of the damping alloy application.

[0130] Final Solution Module 12: Optimize the design of the preliminary damping alloy application solutions for different application parts through analysis, quantitatively analyze the vibration reduction effect, and determine the final vibration reduction design solutions for each part of the damped object.

[0131] The final solution module 12 is specifically used to optimize the design of the preliminary damping alloy application solutions for different application parts through nonlinear transient analysis, quantitatively analyze the vibration reduction effect, and determine the final vibration reduction design solutions for each part of the damped object.

[0132] The embodiment of the present invention is a system embodiment corresponding to the above-mentioned method embodiment. The specific operations of each module can be understood by referring to the description of the method embodiment, which will not be repeated here.

[0133] Device Example 1

[0134] The embodiment of the present invention provides a vibration reduction method using a damping alloy, such as Fig.29 As shown, it includes: a memory 200, a processor 220, and a computer program stored in the memory 200 and executable on the processor 220. When the computer program is executed by the processor, the steps in the above method embodiment are implemented.

[0135] Device Example 2

[0136] An embodiment of the present invention provides a computer-readable storage medium, on which a program for implementing information transmission is stored. When the program is executed by the processor 220, the steps in the above method embodiment are implemented.

[0137] The computer-readable storage medium described in this embodiment includes but is not limited to: ROM, RAM, disk or optical disk, etc. Obviously, those skilled in the art should understand that the above modules or steps of the present invention can be implemented by a general computing device, they can be concentrated on a single computing device, or distributed on a network composed of multiple computing devices, optionally, they can be implemented by a program code executable by a computing device, so that they can be stored in a storage device and executed by the computing device, and in some cases, the steps shown or described can be executed in a different order from that here, or they can be made into individual integrated circuit modules, or multiple modules or steps therein can be made into a single integrated circuit module for implementation. In this way, 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 solutions of the present invention, not to limit them; although the present invention is described in detail with reference to the above embodiments, those skilled in the art should understand that they can still modify the technical solutions recorded in the above embodiments, or replace some or all of the technical features therein by equivalent; and these modifications or replacements of the technical solutions of the embodiments of the present invention do not make the essence of the corresponding technical solutions deviate from the scope of this solution.

Claims

1. A method for reducing vibration using a damping alloy, characterized in that: include, S1. Determine the natural frequency and vibration mode of the damped object by modal analysis, and determine the application position of the damping alloy in the damped object according to the natural frequency and vibration mode of the damped object and the vibration transmission path of the damped object; S2. For different application parts of the damping alloy, qualitatively determine the preliminary application plan of the damping alloy by analyzing the linear modal and harmonic response of the damping alloy; S3. Optimize the design of the preliminary damping alloy application schemes in different application parts by analyzing the damping effect quantitatively, and determine the final vibration reduction design scheme for each part of the damped object; The S3 specifically includes: optimizing the design of the preliminary damping alloy application scheme for different application parts through nonlinear transient analysis, quantitatively analyzing the vibration reduction effect, and determining the final vibration reduction design scheme for each part of the damped object.

2. The method according to claim 1, characterized in that The S1 specifically includes: determining the natural frequency and vibration mode of the damped object by performing modal analysis on the finite element model, and determining the application position of the damping alloy in the damped object according to the natural frequency and vibration mode of the damped object and in combination with the vibration transmission path of the damped object.

3. The method according to claim 2, characterized in that The S2 specifically includes: by performing finite element modeling on the damping alloy application, replacing the original structure of the damped object with the damping alloy application to perform modal and harmonious response analysis, and qualitatively determining the preliminary plan for the damping alloy application.

4. A system for reducing vibration using a damping alloy, characterized in that: include: Modal analysis module: used to determine the natural frequency and vibration mode of the damped object through modal analysis, and determine the application position of the damping alloy in the damped object according to the natural frequency and vibration mode of the damped object and the vibration transmission path of the damped object; Preliminary scheme module: used for qualitatively determining the preliminary scheme for application of the damping alloy through linear modal and harmonic response analysis for different application parts of the damping alloy; Final solution module: used to optimize the design of the preliminary damping alloy application solutions for different application parts through analysis, quantitatively analyze the vibration reduction effect, and determine the final vibration reduction design solutions for each part of the damped object; The final solution module is specifically used to optimize the design of the preliminary damping alloy application solutions for different application parts through nonlinear transient analysis, quantitatively analyze the vibration reduction effect, and determine the final vibration reduction design solutions for each part of the damped object.

5. The system according to claim 4, characterized in that The modal analysis module is specifically used to determine the natural frequency and vibration mode of the damped object by performing modal analysis on the finite element model, and determine the application position of the damping alloy in the damped object according to the natural frequency and vibration mode of the damped object and in combination with the vibration transmission path of the damped object.

6. The system according to claim 5, characterized in that The preliminary scheme module is specifically used to: qualitatively determine the preliminary scheme for the application of the damping alloy by performing finite element modeling on the damping alloy application, replacing the structure of the original damped object with the damping alloy for modal and harmonious response analysis.

7. A device for reducing vibration using a damping alloy, characterized in that: include: A memory, a processor, and a computer program stored in the memory and executable on the processor, wherein when the computer program is executed by the processor, the steps of the method for vibration reduction using a damping alloy as claimed in any one of claims 1 to 3 are implemented.

8. A computer-readable storage medium, characterized in that: The computer-readable storage medium stores an implementation program for information transmission, and when the program is executed by a processor, the steps of the method for vibration reduction using a damping alloy as claimed in any one of claims 1 to 3 are implemented.

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