Method for analyzing impact action and controlling vibration of a press

Abstract

The application discloses a press impact analysis and vibration control method. The application comprises the following steps: simplifying a press into a double-connecting-rod type crank slider mechanism and a three-degree-of-freedom system dynamics model; obtaining a vertical component force according to a vertical component of a crank rotation inertia force and a reciprocating inertia force of a slider in a vertical direction, and then establishing a vibration differential equation according to the vertical component force; calculating a force transmission rate according to the vibration differential equation; solving the vibration differential equation; and optimizing a vibration isolator system parameter according to the force transmission rate. The application solves the problem of difficult press vibration power analysis in the related art.

Description

Technical Field

[0001] This invention relates to the field of engineering vibration technology, and more particularly to a method for analyzing the impact of a press and controlling its vibration. Background Technology

[0002] Mechanical presses generate significant periodic and impact vibrations during stamping and forming operations. These vibrations not only affect the equipment's processing accuracy, structural safety, and service life, but also propagate through the foundation and ground to surrounding buildings, causing environmental vibration and noise pollution. Currently, engineering projects typically use empirical formulas, simplified equivalent loads, or single-condition testing methods to analyze press vibrations and then design vibration isolation based on these analyses.

[0003] Existing research largely focuses on the dynamic modeling, vibration characteristic analysis, and parameter optimization of multi-degree-of-freedom press systems. Excitation source modeling often employs simplified concentrated force or empirical spectrum descriptions, failing to accurately reflect the time-varying and spectral characteristics of the excitation during press operation. Dynamic models are often designed for single components or single degrees of freedom, lacking systematicity and failing to reveal the influence of key parameters on the overall vibration response. Generally, a two-degree-of-freedom mass-spring-damped model is constructed, employing genetic algorithms or particle swarm optimization to optimize the vibration isolation system parameters and improve its vibration isolation performance. Traditional optimization algorithms are prone to getting trapped in local optima in multi-parameter coupled problems, require pre-set weighting coefficients, and suffer from insufficient convergence efficiency; therefore, developing more efficient intelligent optimization strategies is particularly necessary. Vibration isolation design often relies on engineering experience or single-objective optimization, making it difficult to achieve a balance between vibration isolation effect, structural stability, and engineering feasibility. Analysis of vibration propagation along the ground and its impact on surrounding buildings is insufficient, and a unified modeling and evaluation method is lacking. Furthermore, in practical engineering, mechanical systems such as presses are typically multi-degree-of-freedom rigid-flexible coupled structures. Traditional two-degree-of-freedom models often neglect the elastic deformation of connecting rods and sliders, resulting in insufficient characterization of the excitation source and leading to significant errors in dynamic response prediction. While the aforementioned press modeling and optimization methods are practically significant, they also have certain limitations, affecting the accuracy of the calculation results and the subsequent accuracy of calculating vibration propagation along the ground.

[0004] In the existing technology, the modeling of the press does not fully reflect the vibration model of the actual working state. The accuracy of the dynamic response prediction error of the calculation results is large, resulting in insufficient accuracy of the input end of the press vibration propagation model along the ground. In addition, the optimization algorithm is prone to getting trapped in local optima, requires preset weight coefficients, and has insufficient convergence efficiency.

[0005] This invention aims to solve the following technical problems:

[0006] (1) Establish a dynamic model of the vibration system that can reflect the actual working state of the press;

[0007] (2) Accurately calculate the vibration response, analyze the influence of key parameters on the vibration response, and establish a more accurate vibration propagation model along the ground;

[0008] (3) Optimize the design of the vibration isolation system of the press based on a more intelligent optimization algorithm. Summary of the Invention

[0009] The main objective of this application is to provide a method for analyzing the impact of a press and controlling its vibration, so as to at least solve the problem of the difficulty in analyzing the vibration dynamics of a press in related technologies.

[0010] To achieve the above objectives, according to one aspect of this application, a method for analyzing the impact of a press and controlling vibration is provided. The method includes: simplifying the press into a double-link crank-slider mechanism and a three-degree-of-freedom system dynamic model, wherein the double-link crank-slider mechanism includes a crankshaft, a crank, a slider, and a connecting rod; the three-degree-of-freedom system dynamic model includes a housing, a transmission, and a base; a second spring and connecting rod damping connect the housing and the transmission; a first spring and machine frame structural damping connect the housing and the base; and a third spring and vibration isolator damping connect the transmission and the base; obtaining the vertical component of the crank rotational inertia force and the reciprocating inertia force of the slider in the vertical direction, and then establishing a vibration differential equation based on the vertical component; calculating the force transmissibility based on the vibration differential equation; solving the vibration differential equation; and optimizing the vibration isolator system parameters based on the force transmissibility.

[0011] Alternatively, the mass of the connecting rod can be equivalently transferred to the crank and the slider, respectively, as expressed by the formula: , ,in, The mass of the connecting rod is equivalent to that of the crank. The mass of the connecting rod is equivalent to that of the slider. For the mass of the connecting rod, This is the distance from the center of mass of the connecting rod to the end of the crankshaft. This is the distance from the center of mass of the connecting rod to the end of the slider.

[0012] Optionally, the vertical component of the crank rotational inertial force is calculated using the following formula: ,in, This represents the vertical component of the crankshaft rotational inertial force. For crank mass, Where is the crank radius. The crankshaft angular velocity, , The crankshaft speed. Let the mass of the connecting rod be equivalently replaced by the mass of the crank; calculate the reciprocating inertial force of the slider in the vertical direction using the following formula: ,in, Let be the reciprocating inertial force of the slider in the vertical direction. For the mass of the slider, For the acceleration of the slider, The mass of the connecting rod is equivalent to that of the slider; the vertical component of the force is calculated using the following formula: ,in, , , For amplitude, The phase angle, It is the sum of the crank mass and the equivalent crank mass obtained by substituting the connecting rod. The mass of the connecting rod is the sum of the mass of the slider and the mass of the slider itself, which are equivalently replaced by the mass of the connecting rod. The crank mass.

[0013] Optionally, the vibration differential equation can be obtained based on the vertical component force, expressed as follows: , , ,in, This is the sum of the masses of the housing, upper crossbeam, flywheel, crankshaft, and bearing housing. The sum of the masses of the connecting rod, the slider, and the upper mold. The sum of the masses of the lower mold and the base. For the vertical stiffness of the fuselage, For the stiffness of the connecting rod, For the vertical stiffness of the vibration isolator, For fuselage structural damping, For connecting rod damping, Damping for vibration isolators; This represents the displacement of the box-shaped section. The speed of the box section, The acceleration of the box section, This represents the displacement of the transmission component. The speed of the transmission part, The acceleration of the transmission component. This refers to the displacement of the base section. The speed of the base section, The acceleration of the base section, For stamping loads, the matrix form of the vibration differential equation is: The quality matrix is The damping matrix is The stiffness matrix is , , ,in, Let represent the displacement of each concentrated mass block. For motivation.

[0014] Optionally, the displacement of the slider relative to the origin is calculated using the following formula: ,in, For displacement, The length of the link. This is the link coefficient. , Where is the crank radius. The crankshaft angular velocity, , The crankshaft speed is given; the slider acceleration is calculated based on the slider's displacement relative to the origin, expressed by the formula: ,in, This is the acceleration of the slider.

[0015] Alternatively, a Fourier transform of the vibration differential equation can be performed to obtain the frequency domain equation. ,in, The frequency domain response of the system displacement. Here is the dynamic stiffness matrix of the system. For the frequency domain representation of the excitation force, , This represents the inertial excitation vector exerted on the transmission part by the motion of the slider and connecting rod. This represents the vector of stamping loads acting on the base and transmission components. The equivalent amplitude of the inertial excitation, The equivalent amplitude of the stamping load , , , , , , , , These represent the independent principal diagonal dynamic stiffness coefficients of the housing, transmission, and base components, respectively. This represents the dynamic stiffness coefficient of the coupling between the housing and the base. This represents the dynamic stiffness coefficient of the coupling between the housing and the transmission components. The imaginary unit, Let k1 be the excitation circular frequency, k2 be the vertical stiffness of the fuselage, k3 be the vertical stiffness of the vibration isolator, c1 be the structural damping of the fuselage, c2 be the damping of the connecting rod, and c3 be the damping of the vibration isolator. This is the sum of the masses of the housing, upper crossbeam, flywheel, crankshaft, and bearing housing. The sum of the masses of the connecting rod, the slider, and the upper mold. Let the mass be the sum of the masses of the lower mold and the base; the frequency domain response of the system displacement is obtained according to the frequency domain equation, the formula is: .

[0016] Optionally, the frequency domain displacement response of the base portion is calculated based on the frequency domain response of the system displacement, using the following formula: ,in, This represents the frequency domain displacement response of the base portion. The equivalent amplitude of the stamping load is given; the force transmitted to the foundation is calculated based on the frequency domain displacement response of the base section, using the following formula: The force transmissibility is calculated based on the force transmitted to the foundation. The calculation formula is as follows: ,in, For force transmission rate, This represents the amplitude of the stamping load.

[0017] Optionally, by making variable assumptions and reducing the order of the vibration differential equations, a system of first-order differential equations can be obtained. ,in, , , , , , They are respectively , , , , , With respect to the first derivative over time, k1 is the vertical stiffness of the fuselage, k2 is the stiffness of the connecting rod, k3 is the vertical stiffness of the vibration isolator, c1 is the structural damping of the fuselage, c2 is the damping of the connecting rod, c3 is the damping of the vibration isolator, and F(t) is the stamping load. The vertical component of the resultant inertial force. , This represents the vertical displacement of the box-shaped section. The speeds of the box section are respectively. This represents the vertical displacement of the transmission component. The speed of the transmission part, This represents the vertical displacement of the base section. The speed of the base section.

[0018] Optionally, the peak vibration response is calculated using the following formula: , For the natural frequency, The peak value of the vibration response is given; constraints are set, and the formula is expressed as follows: ,in, For the vertical stiffness of the vibration isolator, Damping for vibration isolators; , , The peak values ​​of the vibration response of the three concentrated mass blocks are respectively the housing, transmission, and base. , , The vibration amplitudes at time t represent the vibration values ​​of the three concentrated mass blocks: the housing, the transmission, and the base.

[0019] Optionally, the constrained problem can be transformed into an unconstrained problem using the penalty function method, and the objective function can be optimized as follows: , For force transmission rate, As a penalty factor, To optimize the objective function, the parameters of the vibration isolator system are optimized based on the objective function.

[0020] This application employs the following steps: The press is simplified into a double-link crank-slider mechanism and a three-degree-of-freedom system dynamic model. The double-link crank-slider mechanism includes a crankshaft, crank, slider, and connecting rod. The three-degree-of-freedom system dynamic model includes a housing, a transmission, and a base. A second spring and connecting rod damping connect the housing and transmission. A first spring and machine frame damping connect the housing and base. A third spring and vibration isolator damping connect the transmission and base. The vertical component of the crank rotational inertia force and the reciprocating inertia force of the slider in the vertical direction are obtained. A vibration differential equation is then established based on the vertical component. The force transmissibility is calculated based on the vibration differential equation. The vibration differential equation is solved. The vibration isolator system parameters are optimized based on the force transmissibility. This solves the problem of difficult dynamic analysis of press vibration in related technologies, thereby achieving accurate analysis of the impact force of the pressure and stable control of the vibration. Attached Figure Description

[0021] To more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0022] Figure 1 This is a flowchart of a method for analyzing the impact of a press and controlling vibration, provided in an embodiment of this application.

[0023] Figure 2 This is a simplified diagram of the press assembly;

[0024] Figure 3 This is a simplified diagram of the stamping mechanism;

[0025] Figure 4 This is a schematic diagram of a press vibration isolation system;

[0026] Figure 5 This is a force diagram of a concentrated mass block;

[0027] Figure 6 It is a vibration dynamics model of a three-degree-of-freedom system;

[0028] Figure 7 These are vibration waveforms under no-load conditions;

[0029] Figure 8 These are vibration waveforms under various load conditions;

[0030] Figure 9 These are vibration waveforms of the enclosure under different k3 values ​​when partially loaded.

[0031] Figure 10 These are vibration waveforms of the transmission component under different k3 loads.

[0032] Figure 11 These are vibration waveforms at different k3 values ​​when the base is partially loaded;

[0033] Figure 12 These are time-domain diagrams of different c3 vibrations under partial load on the enclosure;

[0034] Figure 13 These are time-domain diagrams of different c3 vibrations under load on the transmission components;

[0035] Figure 14 These are time-domain diagrams of different c3 vibrations under partial load on the base.

[0036] Figure 15 It is the force transmission rate of different vibration isolators with different stiffness and damping;

[0037] Figure 16 These are time-domain vibration waveforms of the enclosure before and after optimization.

[0038] Figure 17 It optimizes the time-domain vibration waveforms of the front and rear transmission components;

[0039] Figure 18 These are time-domain vibration waveforms of the base section before and after optimization.

[0040] Figure 19 This is a comparison chart of the frequency domain response of the force transmissibility before and after optimization;

[0041] Figure 20 This is a schematic diagram of the spring-damping force of a vibration isolator;

[0042] Figure 21 It is a three-degree-of-freedom vibration system of a press - soil model;

[0043] Figure 22 This is a schematic diagram of foundation deformation along the x-axis.

[0044] Figure 23 This is a schematic diagram of foundation deformation along the y-axis.

[0045] Figure 24 This is a schematic diagram of foundation deformation along the z-axis.

[0046] Figure 25 It is a diagram of foundation deformation relating the vertical stiffness and damping of the vibration isolator;

[0047] Figure 26 It is a diagram of foundation deformation with twice the vertical stiffness of the vibration isolator and the damping of the vibration isolator;

[0048] Figure 27 This is a diagram showing the foundation deformation with 0.5 times the vertical stiffness of the vibration isolator and the damping of the vibration isolator.

[0049] Figure 28 This is a diagram showing the foundation deformation based on the vertical stiffness of the vibration isolator and 5 times the damping of the vibration isolator.

[0050] Figure 29 This is a diagram showing the foundation deformation with respect to the vertical stiffness of the vibration isolator and 0.2 times the damping of the vibration isolator.

[0051] Reference numerals in the attached diagram: 1. Connecting rod; 2. Slider; 3. Housing; 4. Stamping platform; 5. Vibration isolator. Detailed Implementation

[0052] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. This application will now be described in detail with reference to the accompanying drawings and embodiments.

[0053] To enable those skilled in the art to better understand the present application, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present application, and not all embodiments. Based on the embodiments in the present application, all other embodiments obtained by those of ordinary skill in the art without creative effort should fall within the scope of protection of the present application.

[0054] It should be noted that the terms "first," "second," etc., in the specification, claims, and accompanying drawings of this application are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate for the embodiments of this application described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion; for example, a process, method, system, product, or apparatus that comprises a series of steps or units is not necessarily limited to those steps or units explicitly listed, but may include other steps or units not explicitly listed or inherent to such processes, methods, products, or apparatus.

[0055] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention.

[0056] This embodiment provides a method for analyzing the impact of a press and controlling vibration, which runs on a mobile terminal, computer terminal, or similar computing device. It should be noted that the steps shown in the flowchart in the accompanying drawings can be executed in a computer system such as a set of computer-executable instructions. Also, although the logical order is shown in the flowchart, in some cases, the steps shown or described may be executed in a different order than that shown here.

[0057] Figure 1 This is a flowchart illustrating a method for analyzing the impact of a press and controlling vibration according to an embodiment of this application. Figure 1 As shown, the method includes the following steps:

[0058] Step S101: The press is simplified into a double-link crank-slider mechanism and a three-degree-of-freedom system dynamic model. The double-link crank-slider mechanism includes a crankshaft, a crank, a slider, and a connecting rod. The three-degree-of-freedom system dynamic model includes a housing, a transmission, and a base. A second spring and a connecting rod damping are connected between the housing and the transmission. A first spring and a machine body structure damping are connected between the housing and the base. A third spring and a vibration isolator damping are connected between the transmission and the base.

[0059] Specifically, the press is simplified into a double-link crank-slider mechanism. Crankshaft 1 drives crank OA to rotate around the crank center O, and slider C performs reciprocating linear motion under the drive of connecting rod AB. Figure 2 and 3 As shown. Vibration isolation is achieved by installing vibration isolators between the press and the foundation. The simplified vibration isolation system is as follows: Figure 4 As shown. To study the dynamic response of a high-speed press during operation, the force analysis of each concentrated mass block was performed using the Newton-Euler vector mechanics method. The lumped parameter method was used to simplify the entire machine into three concentrated mass blocks: the housing, the transmission section, and the base section, as shown. Figure 2 , 3 As shown in Figure 4.

[0060] During the stamping process, the slider 2 is subjected to a severe instantaneous stamping load at the moment of contact with the workpiece. This load is transmitted upward through the connecting rod 1-crankshaft-body path, causing elastic deformation of the connecting rod 1 and the housing 3 structure. Therefore, both the connecting rod 1 and the housing 3 are regarded as elastic bodies with stiffness and damping characteristics.

[0061] Reference Figure 4 This is a schematic diagram of the vibration isolation system. Below the housing 3 is the stamping platform 4, and below the stamping platform 4 is the vibration isolator 5. The housing 3 contains the slider 2 and the connecting rod 1.

[0062] According to Newton's third law, the stamping load is considered as equal but opposite forces acting on the base and slider 2 respectively. The base is connected to the foundation through vibration isolator 5. Considering elastic deformation and damping characteristics, to simplify the analysis and highlight the main vibration characteristics, the three concentrated mass blocks are considered as rigid bodies; the spring provides only linear elastic force, and the damping is viscous damping. Furthermore, considering only the vertical vibration of the system, it is simplified to a three-degree-of-freedom vibration model, taking the vertically downward direction as positive, as follows... Figure 5 As shown.

[0063] Step S102: Obtain the vertical component of the crank rotational inertial force and the reciprocating inertial force of the slider in the vertical direction, and then establish the vibration differential equation based on the vertical component.

[0064] Step S103: Calculate the force transmissibility based on the vibration differential equation;

[0065] Step S104: Solve the vibration differential equation;

[0066] Step S105: Optimize the parameters of the vibration isolator system based on the force transmission rate.

[0067] In an alternative embodiment, the mass of the connecting rod is equivalently transferred to the crank and the slider, respectively, as expressed by the formula: , ,in, The mass of the connecting rod is equivalent to that of the crank. The mass of the connecting rod is equivalent to that of the slider. For the mass of the connecting rod, This is the distance from the center of mass of the connecting rod to the end of the crankshaft. This is the distance from the center of mass of the connecting rod to the end of the slider.

[0068] Specifically, in engineering, due to the complex shape of the connecting rod, static equivalent two-point substitution is generally used to transfer the mass of the connecting rod to the crank and the slider respectively.

[0069] In an optional embodiment, the vertical component of the crank rotational inertial force is calculated using the following formula: ,in, This represents the vertical component of the crankshaft rotational inertial force. For crank mass, Where is the crank radius. The crankshaft angular velocity, , The crankshaft speed. Let the mass of the connecting rod be equivalently replaced by the mass of the crank; calculate the reciprocating inertial force of the slider in the vertical direction using the following formula: ,in, Let be the reciprocating inertial force of the slider in the vertical direction. For the mass of the slider, For the acceleration of the slider, The mass of the connecting rod is equivalent to that of the slider; the vertical component of the force is calculated using the following formula: ,in, , , For amplitude, The phase angle, It is the sum of the crank mass and the equivalent crank mass obtained by substituting the connecting rod. The mass of the connecting rod is the sum of the mass of the slider and the mass of the slider itself, which are equivalently replaced by the mass of the connecting rod. The crank mass.

[0070] Specifically, the inertial force originates from reciprocating periodic motion, including the centrifugal inertial force caused by the crank rotation and the reciprocating inertial force caused by the linear motion of the slider. The vertical component of the crank rotation inertial force can be expressed as: The reciprocating inertial force of the slider in the vertical direction can be expressed as: Because the linkage coefficient is small, the amplitude of the second-order term of the slider's reciprocating motion is significantly smaller than that of the first-order term, resulting in a smaller contribution to the total inertial excitation force. Therefore, only the first-order force inertia is retained for subsequent analysis, and the vertical component of the resultant inertial force is expressed as... , It is the sum of the crank mass and the mass of the connecting rod equivalently replaced by the crank mass. = , The mass of the connecting rod is the sum of the mass of the slider and the mass of the slider itself, which are equivalently replaced by the mass of the connecting rod. .

[0071] In one alternative embodiment, the vibration differential equation is obtained based on the vertical component force, expressed as follows: , , ,in, This is the sum of the masses of the housing, upper crossbeam, flywheel, crankshaft, and bearing housing. The sum of the masses of the connecting rod, the slider, and the upper mold. The sum of the masses of the lower mold and the base. For the vertical stiffness of the fuselage, For the stiffness of the connecting rod, For the vertical stiffness of the vibration isolator, For fuselage structural damping, For connecting rod damping, Damping for vibration isolators; This represents the displacement of the box-shaped section. The speed of the box section, The acceleration of the box section, This represents the displacement of the transmission component. The speed of the transmission part, The acceleration of the transmission component. This refers to the displacement of the base section. The speed of the base section, The acceleration of the base section, For stamping loads, the matrix form of the vibration differential equation is: The quality matrix is The damping matrix is The stiffness matrix is , , ,in, Let represent the displacement of each concentrated mass block. For motivation.

[0072] Specifically, when a high-speed press is in operation, the vibration of the entire machine is mainly caused by the inertial force generated by the moving parts. The crank's rotational motion generates centrifugal inertial force, and the slider's linear motion generates reciprocating linear inertial force. Based on the above derivation, the vertical inertial force of the press during operation can be obtained. Figure 5 Force analysis of concentrated mass block and Figure 6 Vibration dynamics model of a three-degree-of-freedom system.

[0073] In one alternative embodiment, the displacement of the slider relative to the origin is calculated using the following formula: ,in, For displacement, The length of the link. This is the link coefficient. , Where is the crank radius. The crankshaft angular velocity, , The crankshaft speed is given; the slider acceleration is calculated based on the slider's displacement relative to the origin, expressed by the formula: ,in, This is the acceleration of the slider.

[0074] Specifically, a rectangular coordinate system is established with the crankshaft rotation center as the origin O, and the displacement of the slider relative to the origin can be obtained by first-order approximate expansion using Taylor series. The calculation process is as follows: The acceleration of the slider is obtained by differentiating the displacement twice, and the formula is expressed as follows: .

[0075] In one alternative embodiment, a Fourier transform of the vibration differential equation yields the frequency domain equation. ,in, The frequency domain response of the system displacement. Here is the dynamic stiffness matrix of the system. For the frequency domain representation of the excitation force, , This represents the inertial excitation vector exerted on the transmission part by the motion of the slider and connecting rod. This represents the vector of stamping loads acting on the base and transmission components. The equivalent amplitude of the inertial excitation, The equivalent amplitude of the stamping load , , , , , , , , These represent the independent principal diagonal dynamic stiffness coefficients of the housing, transmission, and base components, respectively. This represents the dynamic stiffness coefficient of the coupling between the housing and the base. This represents the dynamic stiffness coefficient of the coupling between the housing and the transmission components. The imaginary unit, Let k1 be the excitation circular frequency, k2 be the vertical stiffness of the fuselage, k3 be the vertical stiffness of the vibration isolator, c1 be the structural damping of the fuselage, c2 be the damping of the connecting rod, and c3 be the damping of the vibration isolator. This is the sum of the masses of the housing, upper crossbeam, flywheel, crankshaft, and bearing housing. The sum of the masses of the connecting rod, the slider, and the upper mold. Let the mass be the sum of the masses of the lower mold and the base; the frequency domain response of the system displacement is obtained according to the frequency domain equation, the formula is: .

[0076] Specifically, The first term on the right side of the equation represents the inertial excitation vector of the slider and connecting rod motion acting on the transmission part, and the second term represents the stamping load vector acting on the base and transmission part. The frequency domain response of the system displacement is: Without considering the internal inertial force excitation of the system, and only taking the stamping load as an external excitation input, that is... .

[0077] In one optional embodiment, the frequency domain displacement response of the base portion is calculated based on the frequency domain response of the system displacement, using the following formula: ,in, This represents the frequency domain displacement response of the base portion. This represents the equivalent amplitude of the stamping load.

[0078] Specifically, to evaluate the vibration isolation effect, the displacement of the base is calculated to determine the force ultimately transmitted to the foundation. Using the relationship between the inverse matrix and the algebraic cofactor, the displacement of the base (i.e.,...) can be obtained. Figure 6 Frequency domain displacement response of mass block M3 , Let Z be the equivalent amplitude of the stamping load, det denotes the determinant, and det(Z) is the determinant of the dynamic stiffness matrix. Dynamic stiffness matrix The algebraic cofactor is solved by the inverse matrix. Since only the second term (transmission part) and the third term (base part) in the excitation vector have stamping load input, according to the matrix multiplication rule, only the corresponding algebraic cofactor C is retained in the expanded terms. 23 With C 33 , This represents the equivalent amplitude of the stamping load.

[0079] In one alternative embodiment, the force transmitted to the foundation is calculated based on the frequency domain displacement response of the base portion, using the following formula: The force transmissibility is calculated based on the force transmitted to the foundation. The calculation formula is as follows: ,in, For force transmission rate, This represents the amplitude of the stamping load.

[0080] Specifically, the effectiveness of vibration isolation is often expressed by the force transmissibility, which is the ratio of the force amplitude transmitted to the foundation after the vibration isolation system is subjected to an excitation force to the amplitude of the impact load (i.e., the amplitude F of the excitation force F(t)). Based on the above derivation, the force transmitted to the foundation can be obtained.

[0081] In one optional embodiment, the vibration differential equation is subjected to variable assumptions and order reduction to obtain a system of first-order differential equations. ,in, , , , , , They are respectively , , , , , With respect to the first derivative over time, k1 is the vertical stiffness of the fuselage, k2 is the stiffness of the connecting rod, k3 is the vertical stiffness of the vibration isolator, c1 is the structural damping of the fuselage, c2 is the damping of the connecting rod, c3 is the damping of the vibration isolator, and F(t) is the stamping load. The vertical component of the resultant inertial force. , This represents the vertical displacement of the box-shaped section. The speeds of the box section are respectively. This represents the vertical displacement of the transmission component. The speed of the transmission part, This represents the vertical displacement of the base section. The speed of the base section.

[0082] Specifically, the high-precision Runge-Kutta method is used to solve the vibration motion differential equations of the press system. First, the differential equations are transformed from higher order to lower order, and then MATLAB is used for programming and computation. The solver is ode45; the computation time range is 0-1s, with a step size of [missing information]. Initial state setup: Assume that the displacement, velocity, and acceleration of each concentrated mass block are all zero at the initial moment, and the system is in a state of static equilibrium, i.e. (The 0 in parentheses indicates the initial time t=0).

[0083] Unloaded The time-domain vibration waveforms of each concentrated mass block under load can be calculated by modifying the above solution method, such as... Figure 7 , 8 As shown, the amplitude is small before the impact load is applied; when subjected to impact force, the amplitude of each mass block increases sharply. The influence of different vibration isolation system parameters on the vibration response can be calculated by changing the values ​​of k3 and c3.

[0084] With the damping value of the vibration isolator fixed, simulation calculations were performed by changing the stiffness value. As the stiffness of the vibration isolator increases, the peak amplitude increases, and the vibration frequency also increases accordingly. Figure 9 , 10 As shown in Figure 11, with the vibration isolator stiffness fixed and the damping value changed, simulation calculations were performed. As the damping of the vibration isolator increases, the peak amplitude decreases, and the vibration isolation effect improves. Figure 12 , 13 As shown in Figure 14, the force transmissibility of the system gradually decreases with increasing damping of the vibration isolator, indicating that high damping can effectively improve the vibration isolation effect. With increasing stiffness of the vibration isolator, the force transmissibility first decreases and then increases, as shown in Figure 14. Figure 15 As shown.

[0085] In an optional embodiment, the peak vibration response is calculated using the following formula: , For the natural frequency, The peak value of the vibration response is given; constraints are set, and the formula is expressed as follows: ,in, For the vertical stiffness of the vibration isolator, Damping for vibration isolators; , , The peak values ​​of the vibration response of the three concentrated mass blocks are respectively the housing, transmission, and base. , , The vibration amplitudes at time t represent the vibration values ​​of the three concentrated mass blocks: the housing, the transmission, and the base.

[0086] Specifically, the stiffness and damping of the vibration isolator are key parameters affecting vibration transmission. Appropriate values ​​can effectively solve vibration problems, reducing load transfer to the ground during stamping and preventing vibration from affecting the surrounding environment. According to national standards GB50040—2020 and GB50868—2013, the vibration response of each concentrated mass block must ensure that the displacement does not exceed its allowable threshold. The parameter values ​​of the vibration isolation system significantly affect the force transmission rate, while avoiding situations where excessively low stiffness leads to excessive displacement or excessively high stiffness results in poor vibration isolation. Therefore, with the force transmission rate as the optimization objective, the constraints are: .

[0087] In an optional embodiment, the constrained problem is transformed into an unconstrained problem using a penalty function method, and the objective function is optimized as follows: , For force transmission rate, As a penalty factor, To optimize the objective function, the parameters of the vibration isolator system are optimized based on the objective function.

[0088] Specifically, since the transmissibility and vibration amplitude differ by three orders of magnitude, the optimization process is unified. .

[0089] Furthermore, the effects of applying the Dream Optimization Algorithm (DOA), Genetic Algorithm (GA), and Particle Swarm Optimization (PSO) to vibration isolator parameter optimization were compared. To ensure fairness in the comparison, the algorithm parameters were uniformly set as follows: population size of 50, maximum number of iterations of 100, and 30 runs for each algorithm. The GA parameters were set as follows: crossover probability of 0.8 and mutation rate of 0.01. The PSO parameters were set as follows: inertia weight of 0.8, social cognition of 0.5, and self-cognition of 0.5.

[0090] The comparison results of vibration isolator parameters before optimization and after optimization using DOA, GA, and PSO are as follows: Figure 16 , 17 18 and Figure 19 As shown, after optimization by various algorithms, both the peak amplitude and force transmission rate decreased. However, after DOA optimization, the force transmission rate decreased to 15.257%, a reduction of 2.685% compared to the initial value. The peak amplitudes of the housing, transmission components, and base decreased to 1.430 × 10⁻⁶. -4 m, 1.583×10 -4 m, 8.54×10 -5 m, respectively decreased by 14.627%, 5.605% and 47.736%.

[0091] The above results show that DOA can reduce the amplitude of key components while ensuring the lowest transmissibility during the optimization process. High damping can effectively suppress resonance peaks, and low stiffness can avoid rigid coupling problems caused by excessive structural stiffness. The synergistic effect of the two can improve the vibration isolation performance of the system.

[0092] Using the vibration response at the foundation as the boundary input, such as Figure 20 As shown. A three-dimensional model of the foundation and a mathematical model of vibration propagation along the ground are established based on soil dynamics theory, as follows: Figure 21 As shown. The spring-damping force of the press vibration isolation system is used as the response input, and the deformation of the foundation along the x, y, and z directions is used as the output, as follows: Figure 22 , 23 As shown in Figure 24.

[0093] Based on ANSYS finite element transient analysis, the foundation deformation with different vibration isolator stiffness and damping was compared. Figure 25 , 26 As shown in Figures 27, 28, and 29, within a certain range, keeping the damping value of the vibration isolator constant, as the stiffness value of the vibration isolator increases, the total deformation of the soil layer gradually increases, and the vibration isolation mode of the vibration isolator deteriorates. Within a certain range, keeping the stiffness value of the vibration isolator constant, as the damping value of the vibration isolator increases, the total deformation of the soil layer gradually decreases, indicating that the vibration isolation effect of the vibration isolator improves.

[0094] This invention simplifies the entire press machine into three concentrated mass blocks: the housing, the slider, and the base, using a lumped parameter method. The excitation during operation is uniformly represented as a combination of "inertial excitation + stamping load," establishing a three-degree-of-freedom vibration dynamics model. Using the force transmissibility index as "force amplitude transmitted to the foundation / stamping load amplitude transmitted to the foundation / stamping load amplitude," the Dream Optimization Algorithm (DOA) is employed to optimize vibration isolation parameters. The model's advantages in reducing force transmissibility and the amplitude of key components are verified by comparison with GA and PSO. The excitation source and structural elasticity are more fully considered, resulting in more accurate response prediction: This scheme simultaneously considers "inertial excitation + stamping rectangular load," enabling the model to more closely resemble the actual working state and reducing dynamic response errors caused by insufficient excitation representation and excessive structural simplification, thereby improving the accuracy of subsequent ground-propagated input. The intelligent optimization effect is better and the stability is better. Compared with GA and PSO, DOA can achieve a lower force transmission rate and a smaller amplitude of key components under the same comparison settings. The foundation response after vibration isolation optimization is directly used as the input of the ground propagation model, and the impact of different vibration isolation parameters on foundation deformation is evaluated based on finite element transient analysis, realizing a unified analysis process from source control to environmental impact.

[0095] Those skilled in the art will understand that embodiments of this application can be provided as methods, systems, or computer program products. Therefore, this application can take the form of a completely hardware embodiment, a completely software embodiment, or an embodiment combining software and hardware aspects. Furthermore, this application can take the form of a computer program product embodied on one or more computer-usable storage media (including but not limited to disk storage, CD-ROM, optical storage, etc.) containing computer-usable program code.

[0096] This application is described with reference to flowchart illustrations and / or block diagrams of methods, apparatus (systems), and computer program products according to embodiments of this application. It will be understood that each block of the flowchart illustrations and / or block diagrams, and combinations of blocks in the flowchart illustrations and / or block diagrams, can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general-purpose computer, special-purpose computer, embedded processor, or other programmable data processing apparatus to produce a machine, such that the instructions, which execute via the processor of the computer or other programmable data processing apparatus, generate instructions for implementing the flowchart... Figure 1 One or more processes and / or boxes Figure 1 A device that provides the functions specified in one or more boxes.

[0097] These computer program instructions may also be stored in a computer-readable storage medium that can direct a computer or other programmable data processing device to function in a particular manner, such that the instructions stored in the computer-readable storage medium produce an article of manufacture including instruction means, which are implemented in a process Figure 1 One or more processes and / or boxes Figure 1 The function specified in one or more boxes.

[0098] These computer program instructions may also be loaded onto a computer or other programmable data processing equipment to cause a series of operational steps to be performed on the computer or other programmable equipment to produce a computer-implemented process, thereby providing instructions that execute on the computer or other programmable equipment for implementing the process. Figure 1 One or more processes and / or boxes Figure 1 The steps of the function specified in one or more boxes.

[0099] In a typical configuration, a computing device includes one or more processors (CPU), input / output interfaces, network interfaces, and memory.

[0100] Memory may include non-persistent memory in computer-readable media, such as random access memory (RAM) and / or non-volatile memory, such as read-only memory (ROM) or flash RAM. Memory is an example of computer-readable media.

[0101] Computer-readable media includes both permanent and non-permanent, removable and non-removable media that can store information using any method or technology. Information can be computer-readable instructions, data structures, modules of programs, or other data. Examples of computer storage media include, but are not limited to, phase-change memory (PRAM), static random access memory (SRAM), dynamic random access memory (DRAM), other types of random access memory (RAM), read-only memory (ROM), electrically erasable programmable read-only memory (EEPROM), flash memory or other memory technologies, CD-ROM, digital versatile optical disc (DVD) or other optical storage, magnetic tape, magnetic disk storage or other magnetic storage devices, or any other non-transferable medium that can be used to store information accessible by a computing device. As defined herein, computer-readable media does not include transient computer-readable media, such as modulated data signals and carrier waves.

[0102] It should also be noted that the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such process, method, article, or apparatus. Unless otherwise specified, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes that element.

[0103] The above description is merely a preferred embodiment of this application and is not intended to limit this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A method for analyzing the impact of a press and controlling vibration, characterized in that, include: The press is simplified into a double-link crank-slider mechanism and a three-degree-of-freedom system dynamic model. The double-link crank-slider mechanism includes a crankshaft, a crank, a slider, and a connecting rod. The three-degree-of-freedom system dynamic model includes a housing part, a transmission part, and a base part. A second spring and a connecting rod damping are connected between the housing part and the transmission part. A first spring and a machine body structure damping are connected between the housing part and the base part. A third spring and a vibration isolator damping are connected between the transmission part and the base part. The vertical component of the crank rotational inertia force and the reciprocating inertia force of the slider in the vertical direction are used to obtain the vertical component force. Then, the vibration differential equation is established based on the vertical component force, the mass of the housing part, the mass of the transmission part, the mass of the base part, the stiffness of the first spring, the stiffness of the second spring, the stiffness of the third spring, the damping of the fuselage structure, the damping of the connecting rod, and the damping of the vibration isolator. The vertical component of the crank rotational inertial force and the reciprocating inertial force of the slider in the vertical direction are used to obtain the vertical component of the force. Then, a vibration differential equation is established based on this vertical component, including: calculating the vertical component of the crank rotational inertial force using the following formula: ,in, The vertical component of the crank rotational inertial force is... For crank mass, Where is the crank radius. The crankshaft angular velocity, , The crankshaft speed. Let the mass of the connecting rod be equivalently replaced by the mass of the crank; calculate the reciprocating inertial force of the slider in the vertical direction using the following formula: ,in, Let be the reciprocating inertial force of the slider in the vertical direction. For the mass of the slider, For the acceleration of the slider, The mass of the connecting rod is equivalent to that of the slider; the vertical component of the force is calculated using the following formula: ,in, , , For amplitude, The phase angle, It is the sum of the crank mass and the equivalent crank mass obtained by substituting the connecting rod. The mass of the connecting rod is the sum of the mass of the slider and the mass of the slider itself, which are equivalently replaced by the mass of the connecting rod. For crank mass; The vertical component of the crank rotational inertial force and the reciprocating inertial force of the slider in the vertical direction are used to obtain the vertical component force. Then, the vibration differential equation is established based on the vertical component force, including: obtaining the vibration differential equation based on the vertical component force, expressed as follows: , , ,in, This is the sum of the masses of the housing, upper crossbeam, flywheel, crankshaft, and bearing housing. The sum of the masses of the connecting rod, the slider, and the upper mold. The sum of the masses of the lower mold and the base. For the vertical stiffness of the fuselage, For the stiffness of the connecting rod, For the vertical stiffness of the vibration isolator, For fuselage structural damping, For connecting rod damping, Damping for vibration isolators; This represents the displacement of the box-shaped section. The speed of the box section, The acceleration of the box section, This represents the displacement of the transmission component. The speed of the transmission part, The acceleration of the transmission component. This refers to the displacement of the base section. The speed of the base section, The acceleration of the base section, For stamping loads, the matrix form of the vibration differential equation is: The quality matrix is The damping matrix is The stiffness matrix is , , ,in, Let represent the displacement of each concentrated mass block. For motivation; Calculate the force transmissibility based on the aforementioned vibration differential equation; Solve the vibration differential equation; The parameters of the vibration isolator system are optimized based on the force transmissibility.

2. The method according to claim 1, characterized in that, Before establishing the vibration differential equation based on the vertical component of the crank rotational inertial force and the reciprocating inertial force of the slider in the vertical direction, the following steps are taken: The mass of the connecting rod is equivalently transferred to the crank and the slider, respectively, as expressed by the formula: , ,in, The mass of the connecting rod is equivalent to that of the crank. The mass of the connecting rod is equivalent to that of the slider. For the mass of the connecting rod, This is the distance from the center of mass of the connecting rod to the end of the crankshaft. This is the distance from the center of mass of the connecting rod to the end of the slider.

3. The method according to claim 1, characterized in that, Calculate the reciprocating inertial force of the slider in the vertical direction, including: The formula for calculating the displacement of the slider relative to the origin is as follows: ,in, For displacement, The length of the link. This is the link coefficient. , Where is the crank radius. The crankshaft angular velocity, , This refers to the crankshaft speed; The acceleration of the slider is calculated based on its displacement relative to the origin, expressed by the following formula: ,in, The acceleration of the slider.

4. The method according to claim 1, characterized in that, The force transmissibility is calculated based on the aforementioned vibration differential equation, including: Performing a Fourier transform on the vibration differential equation yields the frequency domain equation. ,in, The frequency domain response of the system displacement. Here is the dynamic stiffness matrix of the system. For the frequency domain representation of the excitation force, , This represents the inertial excitation vector exerted on the transmission part by the motion of the slider and connecting rod. This represents the vector of stamping loads acting on the base and transmission components. The equivalent amplitude of the inertial excitation, The equivalent amplitude of the stamping load , , , , , , , , These represent the independent principal diagonal dynamic stiffness coefficients of the housing, transmission, and base components, respectively. This represents the dynamic stiffness coefficient of the coupling between the housing and the base. This represents the dynamic stiffness coefficient of the coupling between the housing and the transmission components. The imaginary unit, Let k1 be the excitation circular frequency, k2 be the vertical stiffness of the fuselage, k3 be the vertical stiffness of the vibration isolator, c1 be the structural damping of the fuselage, c2 be the damping of the connecting rod, and c3 be the damping of the vibration isolator. This is the sum of the masses of the housing, upper crossbeam, flywheel, crankshaft, and bearing housing. The sum of the masses of the connecting rod, the slider, and the upper mold. The sum of the masses of the lower mold and the base; The frequency domain response of the system displacement is obtained based on the frequency domain equation, and the formula is as follows: .

5. The method according to claim 4, characterized in that, The force transmissibility is calculated based on the aforementioned vibration differential equation, including: The frequency domain displacement response of the base portion is calculated based on the frequency domain response of the system displacement, using the following formula: ,in, This represents the frequency domain displacement response of the base portion. This represents the equivalent amplitude of the stamping load. The force transmitted to the foundation is calculated based on the frequency domain displacement response of the base portion, using the following formula: , The force transmitted to the foundation; The force transmissibility is calculated based on the force transmitted to the foundation, using the following formula: ,in, For force transmission rate, This represents the amplitude of the stamping load.

6. The method according to claim 1, characterized in that, Solving the vibration differential equation includes: By making variable assumptions and reducing the order of the vibration differential equations, we obtain a system of first-order differential equations. ,in, , , , , , They are respectively , , , , , With respect to the first derivative over time, k1 is the vertical stiffness of the fuselage, k2 is the stiffness of the connecting rod, k3 is the vertical stiffness of the vibration isolator, c1 is the structural damping of the fuselage, c2 is the damping of the connecting rod, c3 is the damping of the vibration isolator, and F(t) is the stamping load. The vertical component of the resultant inertial force. , This represents the vertical displacement of the box-shaped section. The speeds of the box section are respectively. This represents the vertical displacement of the transmission component. The speed of the transmission part, This represents the vertical displacement of the base section. M1 is the speed of the base section, M2 is the sum of the masses of the housing, upper crossbeam, flywheel, crankshaft and bearing housing, M3 is the sum of the masses of the connecting rod, slider and upper mold, and M4 is the sum of the masses of the lower mold and base.

7. The method according to claim 1, characterized in that, Optimization of vibration isolator system parameters based on the stated force transmissibility includes: The peak value of the vibration response is calculated using the following formula: , For the natural frequency, This represents the peak value of the vibration response. Define the constraints, and the formula is expressed as follows: ,in, For the vertical stiffness of the vibration isolator, Damping for vibration isolators; , , The peak values ​​of the vibration response of the three concentrated mass blocks are respectively the housing, transmission, and base. , , The vibration amplitudes at time t represent the vibration values ​​of the three concentrated mass blocks: the housing, the transmission, and the base.

8. The method according to claim 7, characterized in that, Optimization of vibration isolator system parameters based on the stated force transmissibility includes: The constrained problem is transformed into an unconstrained problem using the penalty function method, and the objective function is optimized as follows: , For force transmission rate, As a penalty factor, Let the optimization objective function be... The parameters of the vibration isolator system are optimized based on the aforementioned objective function.

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