Parameter optimization method of tuned mass pipeline damping device and damping device

Abstract

The invention relates to the technical field of pipeline vibration reduction, in particular to a parameter optimization method of a tuned mass pipeline vibration reduction device and the vibration reduction device. The method comprises the following steps: establishing a dynamic amplification coefficient calculation model responded by a controlled pipeline structure, and applying the calculation model to obtain a simple harmonic load frequency ratio of the controlled pipeline, a frequency ratio of a plurality of shock absorbers and a corresponding relation between a damping ratio of the plurality of shock absorbers and the dynamic amplification coefficient; the frequency ratio and the damping ratio of each shock absorber are in one-to-one correspondence to form a parameter column of each shock absorber, and a dynamic amplification coefficient, the simple harmonic load frequency of the controlled pipeline and a target function associated with a parameter combination are established through a parameter combination formed by parameter column sets of a plurality of shock absorbers; and optimizing the parameter combination through an optimization algorithm. According to the method, the optimal parameters of the detector can be obtained through optimization so as to ensure that the shock absorber achieves the optimal shock absorption effect.

Description

Technical Field

[0001] The present invention relates to the technical field of pipeline vibration reduction, and specifically to a parameter optimization method for a tuned mass pipeline vibration reduction device and a vibration reduction device. Background Art

[0002] Due to the influence of many factors such as changes in the fluid characteristics inside the pipeline, flexible design of the pipeline boundary constraints, and diversification of pipeline layouts in large chemical pipelines, there is a high probability of causing high-frequency vibration problems in local pipelines. Long-term pipeline vibration may cause pipeline fatigue problems. If a high-temperature pipeline is damaged or even cracked due to fatigue, resulting in the leakage of high-temperature media, this will not only seriously affect the safe and stable operation of petrochemical plants, but may also cause serious casualties. In addition, high-frequency vibration often brings serious noise pollution problems.

[0003] To suppress the above high-frequency vibration problems, most of the existing technologies adopt methods such as increasing pipeline supports and hangers, constraint supports, or setting vibration reduction devices.

[0004] When using supports and hangers, the pipeline is flexibly constrained. Therefore, the treatment effect on high-frequency vibration is limited. If rigid constraint supports are used, on the one hand, the pipeline will be unevenly stressed, and there will be obvious local stress concentration at the constraint; on the other hand, there is an obvious temperature effect in high-temperature pipelines. If rigid constraints are used, the temperature deformation cannot be released, and huge temperature stresses will be generated. The longer and larger the pipeline is, the greater the temperature stress will be. Therefore, large high-temperature pipelines cannot use rigid constraints for vibration suppression.

[0005] Therefore, in the existing technology, most large high-temperature pipelines adopt the vibration reduction form of tuned mass dampers. However, the parameter arrangement of the current tuned mass dampers mostly depends on manual experience for different working conditions. However, the method of setting parameters by manual experience often requires high manual experience, and the formed vibration reduction device is often difficult to achieve the required vibration reduction effect at one time, and the parameters of the vibration reduction device need to be adjusted multiple times. In addition, even if the parameters set by manual experience make the vibration reduction device achieve the required vibration reduction effect, the vibration reduction effect of the vibration reduction device is often not the best vibration reduction state. Therefore, the vibration reduction effect under extreme vibration conditions of the pipeline is not ideal. Therefore, it is urgent to solve. Summary of the Invention

[0006] In order to avoid and overcome the technical problems existing in the prior art, the present invention provides a parameter optimization method for a tuned mass pipeline vibration reduction device and a vibration reduction device, which can optimize and obtain the optimal parameters of the detector to ensure that the vibration reduction device achieves the best vibration reduction effect.

[0007] To achieve the above object, the present invention provides the following technical solutions:

[0008] A parameter optimization method for a tuned mass pipeline vibration reduction device, comprising the following steps:

[0009] S1. Establish a calculation model for the dynamic amplification factor of the controlled pipeline structure response. Apply the calculation model to obtain the corresponding relationship between the harmonic load frequency ratio of the controlled pipeline, the frequency ratios of several shock absorbers, the damping ratios of several shock absorbers, and the dynamic amplification factor.

[0010] S2. Form a parameter column for each shock absorber by corresponding the frequency ratio and damping ratio of each shock absorber one by one. Use the parameter combinations formed by the parameter column sets of several shock absorbers to establish an objective function related to the dynamic amplification factor, the harmonic load frequency of the controlled pipeline, and the parameter combinations.

[0011] S3. Optimize the parameter combinations through an optimization algorithm to minimize the maximum value of the dynamic amplification factor of the controlled pipeline structure response during the continuous change of the harmonic load frequency ratio of the controlled pipeline within a set interval, and make this maximum value less than the expected value.

[0012] As a further solution of the present invention: The calculation model for the dynamic amplification factor of the controlled pipeline structure response is specifically:

[0013]

[0014] where DMF is the dynamic amplification factor of the controlled pipeline structure response;

[0015] j is the imaginary unit;

[0016] ξ p is the damping ratio of the controlled pipeline structure;

[0017] λ p is the harmonic load frequency ratio of the controlled pipeline;

[0018] μ i is the mass ratio of the i-th shock absorber;

[0019] λ i is the frequency ratio of the i-th shock absorber;

[0020] ξ i is the damping ratio of the i-th shock absorber;

[0021] n represents the number of shock absorbers.

[0022] As a further solution of the present invention:

[0023] The parameter combinations are specifically: (λ1, ξ1, λ2, ξ2, …, λ n , ξ n );

[0024] The objective function related to the harmonic load frequency ratio of the controlled pipeline and the parameter combinations is specifically:

[0025]

[0026] As a further solution of the present invention: the optimization algorithm is a genetic algorithm, and the process of optimizing the parameter combination by the optimization algorithm in step S3 specifically includes:

[0027] S31. Initialize the population of parameter combinations to be optimized;

[0028] S32. Randomly initialize the parameter population of the genetic algorithm;

[0029] S33. Generate the offspring population;

[0030] S34. Merge the populations, and calculate the objective function value of the parameter combination corresponding to the merged population. Thereafter, determine whether the objective function is less than the expected value. If so, the optimization ends. If not, proceed to step S35;

[0031] S35. Sort the individuals of the merged population according to the superiority or inferiority of the objective function results from good to bad or from bad to good;

[0032] S36. Select a predetermined number of population individuals with the objective function results in the front row to generate a new generation of population;

[0033] S37. Determine whether the maximum number of iterations is reached. If not, return to step S33 for re-iteration. If so, update the parameter population of the genetic algorithm and return to step S33.

[0034] As a further solution of the present invention: the process of randomly initializing the parameter population of the genetic algorithm in step S32 is specifically to randomly initialize the genetic population size, the number of genetic iterations, the crossover ratio, the mutation ratio, the mutation rate, and the mutation step coefficient.

[0035] As a further solution of the present invention: the process of generating the offspring population in step S33 specifically includes:

[0036] Obtain the number of individuals to be crossed under the genetic population size according to the crossover ratio, and cross the individuals to be crossed in pairs to form new offspring individuals;

[0037] Obtain the number of individuals that mutate under the genetic population size according to the mutation ratio;

[0038] Obtain the mutation step vector according to the mutation step coefficient;

[0039] Obtain the number of parameters to be corrected for mutation according to the mutation rate, and randomly select the positions of the parameters to be corrected;

[0040] Generate the mutated offspring individuals according to the number of mutated individuals, the mutation step vector, and the parameters to be optimized for mutation;

[0041] Replace the new offspring individuals at the corresponding positions with the mutated offspring individuals to form an offspring population.

[0042] A vibration damping device applying the parameter optimization method of the tuned mass pipeline vibration damping device, including shock absorbers fixed to the controlled pipeline structure by hoop fasteners. There are at least two shock absorbers axially evenly distributed around the axis of the controlled pipeline structure, and the frequency ratio and damping ratio of each shock absorber correspond to one of the parameter columns in the parameter combination obtained by optimizing the parameter optimization method of the tuned mass pipeline vibration damping device.

[0043] As a further scheme of the present invention: each of the shock absorbers includes a mounting link with a cross-shaped structure. One end of the mounting link is connected to the hoop fastener, and mass blocks are fixed to the other three ends. Magnets are fixed to the outer plate surfaces perpendicular to the corresponding ends of the mounting link. Copper plates fixed to the hoop fasteners are arranged at each magnet.

[0044] As a further scheme of the present invention: the hoop fastener is composed of two-section semi-circular rings fixed by connecting bolts, and an anti-slip heat-insulating strip is arranged between the hoop fastener and the controlled pipeline structure.

[0045] Compared with the prior art, the beneficial effects of the present invention are:

[0046] 1. By constructing a calculation model, obtaining the corresponding relationship between the dynamic amplification factor, the harmonic load frequency ratio of the controlled pipeline, and the parameter combination formed by the frequency ratios and damping ratios of several shock absorbers through the calculation model. In addition, by establishing an objective function among the three, and optimizing the parameter combination through the genetic algorithm, the maximum value of the dynamic amplification factor of the response of the controlled pipeline structure is minimized, and this maximum value is less than the expected value. Thus, the optimal parameter arrangement of each shock absorber under different numbers of shock absorber layouts is obtained, which not only enables the shock absorber to have the best vibration damping effect under normal vibration conditions, but also enables the shock absorber to have the expected vibration damping effect on the pipeline under extreme vibration conditions.

[0047] 2. By using the genetic algorithm to optimize the parameter combination, the optimal solution can be found in a complex search space, and it has good performance in dealing with non-linear and non-convex problems such as those in this application. In addition, the genetic algorithm can adapt to various changing environments and problems, and self-adjust and optimize through the competition of individuals in the population and genetic operations, ensuring the accuracy of the final data.

[0048] 3. By distributing at least two shock absorbers in a multi-point distribution manner on the outer periphery of the controlled pipeline structure, the mass of a single shock absorber is significantly reduced, reducing the local shear force on the pipeline; in addition, the evenly distributed shock absorbers effectively avoid local stress concentration, reduce the risk of pipeline fatigue failure, and significantly improve safety.

[0049] 4. Through the design of the mounting link with a cross-shaped structure, the vibration of the controlled pipeline structure in multiple directions can be controlled simultaneously, and the vibration energy can be dissipated through the eddy current effect, achieving efficient suppression of multi-frequency vibration. Compared with the traditional single-direction design, the multi-direction structure of the present invention is more adaptable to complex vibration conditions and significantly improves the vibration reduction effect. BRIEF DESCRIPTION OF THE DRAWINGS

[0050] Figure 1 It is a schematic diagram of the working process of the present invention.

[0051] Figure 2 It is a schematic diagram of the working process of the genetic algorithm in the present invention.

[0052] Figure 3 It is a schematic diagram of the structure of the vibration reduction device in the present invention.

[0053] Figure 4 It is a schematic diagram of the structure of the shock absorber in the present invention.

[0054] In the figure: 10, hoop; 20, anti-slip heat insulation strip; 30, controlled pipeline structure; 40, connecting bolt; 50, mass block; 60, copper plate; 70, magnet; 80, mounting link. DETAILED DESCRIPTION OF THE INVENTION

[0055] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present invention.

[0056] For ease of understanding, the specific structure and working mode of the present invention are further described as follows in conjunction with the accompanying drawings:

[0057] A method for optimizing the parameters of a tuned mass pipeline vibration reduction device includes the following steps:

[0058] S1. Establish a calculation model for the dynamic magnification factor of the response of the controlled pipeline structure, and use the calculation model to obtain the corresponding relationship between the harmonic load frequency ratio of the controlled pipeline, the frequency ratios of several shock absorbers, the damping ratios of several shock absorbers, and the dynamic magnification factor;

[0059] S2. Correspond the frequency ratio and damping ratio of each shock absorber one by one to form a parameter column for each shock absorber, and establish an objective function related to the dynamic magnification factor, the harmonic load frequency of the controlled pipeline, and the parameter combination formed by the parameter column sets of several shock absorbers;

[0060] S3. Optimize the parameter combination through an optimization algorithm to minimize the maximum value of the dynamic amplification factor of the controlled pipeline structure response during the continuous change of the frequency ratio of the harmonic load of the controlled pipeline within a set interval, and this maximum value is less than the expected value.

[0061] In actual implementation, the above set interval can use the frequency ratio of the harmonic load of the controlled pipeline in the extreme vibration state as one of the interval boundaries. At the same time, the expected value can be set based on the dynamic square coefficient of the pipeline in the extreme vibration state, so that the optimized shock absorber parameters can also have the expected shock absorption effect on the pipeline in the extreme vibration state.

[0062] The present invention constructs a calculation model, obtains the corresponding relationship between the dynamic amplification factor, the frequency ratio of the harmonic load of the controlled pipeline, and the parameter combination formed by the frequency ratio and damping ratio of several shock absorbers through the calculation model. In addition, an objective function among the three is established, and the parameter combination is optimized through an optimization algorithm to minimize the maximum value of the dynamic amplification factor of the controlled pipeline structure response, and this maximum value is less than the expected value. Thus, the optimal parameter arrangement of each shock absorber under different numbers of shock absorber layouts is obtained, which not only enables the shock absorber to have the best shock absorption effect in the normal vibration state, but also enables the shock absorber to have the expected shock absorption effect on the pipeline in the extreme vibration state.

[0063] On the above basis, the calculation model of the dynamic amplification factor of the controlled pipeline structure response is specifically:

[0064]

[0065] Among them, DMF is the dynamic amplification factor of the controlled pipeline structure response;

[0066] j is the imaginary unit;

[0067] ξ p is the damping ratio of the controlled pipeline structure;

[0068] λ p is the frequency ratio of the harmonic load of the controlled pipeline;

[0069] μ i is the mass ratio of the i-th shock absorber;

[0070] λ i is the frequency ratio of the i-th shock absorber;

[0071] ξ i is the damping ratio of the i-th shock absorber;

[0072] n represents the number of shock absorbers.

[0073] In addition, the parameter combination is specifically: (λ1, ξ1, λ2, ξ2, …, λ n, ξ n );

[0074] The objective function of the correlation parameter combination of the controlled pipeline's harmonic load frequency ratio is specifically as follows:

[0075]

[0076] According to the mechanical model of the controlled pipeline - DTMD system, its motion equation can be expressed as:

[0077]

[0078] Among them, X is the displacement column vector, and its form is as follows:

[0079]

[0080] Among them, Xp is the displacement of the structure, and Xi is the displacement of the i-th shock absorber.

[0081] M, C, and K are respectively the mass matrix, damping matrix, and stiffness matrix of the system, and their forms are as follows:

[0082]

[0083] Assume that the external load acting on the controlled pipeline structure is P, and its form is as follows:

[0084]

[0085] In the formula, t represents time.

[0086] Assume that the excitation acting on the controlled pipeline structure is a harmonic load, and the complex form of the load P is as follows, where j is the imaginary unit (in practical engineering applications, the excitation load should be obtained from on-site measurements).

[0087]

[0088] In the formula, p0 is the amplitude of the harmonic excitation load, and ω is the circular frequency of the harmonic excitation. Then the solution of Equation 1 can be expressed as:

[0089]

[0090] Substituting Equations 2 - 5 and 7 - 8 into Equation 1, the displacement complex frequency response of the controlled pipeline structure can be obtained as shown in the following formula:

[0091]

[0092] In the formula, k p is the generalized stiffness of the controlled pipeline structure, c p is the generalized damping of the controlled pipeline structure, k iis the stiffness of the i-th shock absorber, m i is the mass of the i-th shock absorber, c i is the damping of the i-th shock absorber.

[0093] The dynamic amplification factor can be expressed as:

[0094]

[0095] Substituting Equation 9 into Equation 10, we can get:

[0096]

[0097] To better describe the properties of the controlled pipeline structure, the following parameters are defined. The natural circular frequency ω of the controlled pipeline structure p 2 = k p / m p , the damping ratio ξ of the controlled pipeline structure p = c p / 2m p ω p , the load frequency ratio λ p = ω / ω p , the mass ratio μ1 of the i-th shock absorber = m i / m p , the total mass ratio is , the natural circular frequency of the i-th shock absorber is The frequency ratio λ of the i-th shock absorber i = ω i / ω p , the damping ratio ξ of the i-th shock absorber i = c i / 2m i ω i . Therefore, Equation 11 can be rewritten to obtain the calculation model of the dynamic amplification factor of the response of the controlled pipeline structure required by this application:

[0098]

[0099] On this basis, as Figure 2 shown, the optimization algorithm is a genetic algorithm. The process of optimizing the parameter combination by the optimization algorithm in step S3 specifically includes:

[0100] S31. Initialize the population of parameters to be optimized;

[0101] S32. Randomly initialize the parameter population of the genetic algorithm;

[0102] S33. Generate the offspring population;

[0103] S34. Merge the populations and calculate the objective function value corresponding to the combined population. After that, determine whether the objective function is less than the expected value. If so, the optimization ends. If not, proceed to step S35;

[0104] S35. Sort the individuals of the combined population according to the objective function results from the best to the worst or from the worst to the best;

[0105] S36. Select a predetermined number of population individuals with the best objective function results to generate a new generation of population;

[0106] S37. Determine whether the maximum number of iterations has been reached. If not, return to step S33 for re-iteration. If so, update the genetic algorithm parameter population and return to step S33.

[0107] Among them, the process of randomly initializing the genetic algorithm parameter population in step S32 is specifically to randomly initialize the genetic population size, genetic iteration times, crossover ratio, mutation ratio, mutation rate, and mutation step coefficient.

[0108] Assume that the preset value ranges of each individual in the population are respectively:

[0109]

[0110] Therefore, the i-th individual in the population can be expressed as

[0111]

[0112] In the formula, the individual The element values in are all and Random numbers between. The randomly initialized population can be expressed as:

[0113]

[0114] In the formula, N is the size of the genetic algorithm random population

[0115] Then, the population of the to-be-optimized parameter combinations in step S31 can be expressed as:

[0116] Assume that the preset value ranges of λ and ξ in a single shock absorber parameter column are:

[0117]

[0118]

[0119] The i-th individual in the population of the to-be-optimized parameter combinations can be expressed as:

[0120]

[0121] In the formula, the individual The element values in are all and Random numbers between. The population of parameter combinations to be optimized can be expressed as:

[0122]

[0123] On the above basis, the process of generating the offspring population in step S33 is specifically as follows:

[0124] Obtain the number of individuals to be crossed under the size of this genetic population according to the crossover ratio, and cross the individuals to be crossed in pairs to form new offspring individuals;

[0125] Obtain the number of individuals that mutate under the size of this genetic population according to the mutation ratio;

[0126] According to the mutation step coefficient, and obtain the mutation step vector;

[0127] According to the mutation rate, and obtain the number of parameters to be corrected for mutation, and randomly select the positions of the parameters to be corrected;

[0128] Generate the mutated offspring individuals according to the number of mutated individuals, the mutation step vector, and the parameters to be optimized for mutation;

[0129] Replace the new offspring individuals at the corresponding positions with the mutated offspring individuals to form the offspring population.

[0130] Crossover simulates the process of individual gene recombination, generates new offspring by exchanging part of the genetic information of the parental population, and thus breeds more excellent individuals. The crossover operation increases the spatial diversity of the population and helps to avoid premature convergence.

[0131] More specifically:

[0132] Assume that the crossover ratio is β c , then the population p ga The number of individuals to be crossed N c is:

[0133] N c = N·β c

[0134] Since n c individuals need to be crossed in pairs, N c / 2 crossovers are required in one generation of the population. Assume there are two parental individuals and whose expression is

[0135]

[0136] In the formula: np is the number of genes in an individual, that is, the number of parameters in the parameter combination. Two parent individuals and perform a crossover operation to obtain new individuals and whose expression is:

[0137]

[0138] where α c is a random coefficient matrix with elements uniformly distributed in the interval [0, 1], and its dimension is the same as that of and . It is used to mix the genetic information of the two parent individuals proportionally.

[0139] The mutation operation aims to introduce individual diversity and prevent the algorithm from falling into local optima. Assuming the mutation ratio is β m , then the number of mutated individuals N m in the population is:

[0140] N m = N·β m

[0141] From the two expressions of the preset value ranges of λ and ξ of a single shock absorber parameter column, the mutation step vector σ can be obtained, and the expression is:

[0142]

[0143] where α m is the mutation step coefficient, which determines the mutation amplitude of the parameters in the parameter combination to be optimized. Assuming the number of parameters in the mutated parameter combination in individual is:

[0144]

[0145] where represents rounding up, and μ represents the mutation rate.

[0146] Among the n p parameters to be corrected, randomly select N μ positions j pos , denoted as the set

[0147] |j pos | = n p

[0148] In addition, the introduced mutation perturbation vector obeys the normal distribution. For the n p parameters to be corrected in the mutated individual, randomly select N μ positions jpos The parameter to be corrected then mutates to: the parameter to be corrected at the mutation position plus where represents taking the value corresponding to the j pos th item in σ.

[0149] By using the genetic algorithm to optimize the parameter combination, the optimal solution can be found in a complex search space, and it has good performance when dealing with non-linear and non-convex problems such as those in this application. In addition, the genetic algorithm can adapt to various changing environments and problems, and self-adjust and optimize through the competition of individuals in the population and genetic operations, ensuring the accuracy of the final data.

[0150] The vibration damping device is as Figure 3 and Figure 4 shown. This vibration damping device applies a parameter optimization method for a tuned mass pipeline vibration damping device, including shock absorbers fixed to the controlled pipeline structure 30 by clamps 10. The shock absorbers are set to be at least two axially evenly distributed around the axis of the controlled pipeline structure 30, and the frequency ratio and damping ratio of each shock absorber correspond to one of the parameter columns in the parameter combination optimized by the parameter optimization method for the tuned mass pipeline vibration damping device.

[0151] The shock absorbers are set to be at least two axially evenly distributed around the axis of the controlled pipeline structure 30. Through the multi-point distribution method, the mass of a single shock absorber is significantly reduced, reducing the shear force acting on the local part of the pipeline. In addition, the evenly distributed shock absorbers effectively avoid local stress concentration, reduce the risk of pipeline fatigue failure, and significantly improve safety.

[0152] As Figure 4 shown, each shock absorber includes an installation link 80 with a cross-shaped structure. One end of the installation link 80 is connected to the clamp 10, and mass blocks 50 are fixed to the other three ends. Magnets 70 are fixed to the outer plate surfaces perpendicular to the corresponding ends of the installation link 80 of the mass blocks 50, and copper plates 60 fixed to the clamp 10 are arranged at each magnet 70. Through the design of the cross-shaped installation link 80, the vibration of the controlled pipeline structure 30 in multiple directions can be controlled simultaneously, and the vibration energy can be dissipated through the eddy current effect, realizing the efficient suppression of multi-frequency vibration. Compared with the traditional single-direction design, the multi-direction structure of the present invention is more adaptable to complex vibration conditions and significantly improves the vibration damping effect.

[0153] In addition, as Figure 3 shown, the clamp 10 is composed of two-section semi-circular rings fixed by connecting bolts 40, and an anti-slip heat-insulating strip 20 is arranged between the clamp 10 and the controlled pipeline structure 30, improving the assembly convenience of the clamp 10.

[0154] Of course, for those skilled in the art, the present invention is not limited to the details of the above-described exemplary embodiments, but also includes the same or similar structures that can be implemented in other specific forms without departing from the spirit or basic characteristics of the present invention. Therefore, from any point of view, the embodiments should be regarded as exemplary and non-limiting. The scope of the present invention is defined by the appended claims rather than the above description. Therefore, all changes falling within the meaning and scope of the equivalent elements of the claims are intended to be embraced within the present invention. Any reference signs in the claims should not be construed as limiting the claims involved.

[0155] In addition, it should be understood that although this specification is described in terms of embodiments, not every embodiment contains only one independent technical solution. This narrative manner of the specification is only for clarity. Those skilled in the art should regard the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

[0156] The technologies, shapes, and structures not detailed in the present invention are all well-known technologies.

Claims

1. A parameter optimization method for a tuned mass pipeline vibration damping device, characterized in that, It includes the following steps: S1. Establish a calculation model for the dynamic amplification factor of the controlled pipeline structure response. Apply the calculation model to obtain the corresponding relationships between the harmonic load frequency ratio of the controlled pipeline, the frequency ratios of several shock absorbers, the damping ratios of several shock absorbers, and the dynamic amplification factor; S2. One-to-one correspondence of the frequency ratio and damping ratio of each shock absorber forms a parameter column for each shock absorber. With the parameter combinations formed by the parameter column sets of several shock absorbers, establish an objective function that correlates the dynamic amplification factor, the harmonic load frequency of the controlled pipeline, and the parameter combinations; S3. Optimize the parameter combinations through an optimization algorithm to minimize the maximum value of the dynamic amplification factor of the controlled pipeline structure response during the continuous change of the harmonic load frequency ratio of the controlled pipeline within a set interval, and this maximum value is less than the expected value.

2. The parameter optimization method of a tuned mass pipeline vibration damping device according to claim 1, characterized in that The calculation model for the dynamic amplification factor of the controlled pipeline structure response is specifically: where DMF is the dynamic amplification factor of the controlled pipeline structure response; j is the imaginary unit; ξ p is the damping ratio of the pipeline structure under control; λ p is the frequency ratio of the harmonic load of the pipeline under control; μ i is the mass ratio of the i-th shock absorber; λ i is the frequency ratio of the i-th shock absorber; ξ i is the damping ratio of the i-th shock absorber; n represents the number of shock absorbers.

3. The parameter optimization method of a tuned mass pipeline vibration damping device according to claim 2, characterized in that The specific parameter combination is: (λ1, ξ1, λ2, ξ2, …, λ n , ξ n ); The objective function that correlates the harmonic load frequency ratio of the controlled pipeline with the parameter combinations is specifically: min maxDMF λ1, ξ1, λ2, ξ2, …, λ n , ξ n λ p 。 4. A parameter optimization method for a tuned mass pipeline vibration damping device according to any one of claims 1-3, characterized in that The optimization algorithm is a genetic algorithm. The process of optimizing the parameter combinations by the optimization algorithm in step S3 specifically includes: S31. Initialize the population of the parameter combinations to be optimized; S32. Randomly initialize the parameter population of the genetic algorithm; S33. Generate the offspring population; S34. Merge the populations, and calculate the objective function values of the parameter combinations corresponding to the merged population. Thereafter, determine whether the objective function is less than the expected value. If so, the optimization ends. If not, proceed to step S35; S35. Sort the individuals of the merged population according to the superiority or inferiority of the objective function results, either from superior to inferior or from inferior to superior; S36. Select a predetermined number of population individuals with the leading objective function results to generate a new generation of population; S37. Determine whether the maximum number of iterations is reached. If not, return to step S33 for re-iteration. If so, update the parameter population of the genetic algorithm and return to step S33.

5. A parameter optimization method for a tuned mass pipeline vibration damping device according to claim 4, characterized in that The process of randomly initializing the parameter population of the genetic algorithm in step S32 is specifically to randomly initialize the genetic population size, the number of genetic iterations, the crossover ratio, the mutation ratio, the mutation rate, and the mutation step coefficient.

6. The parameter optimization method of a tuned mass pipeline vibration damping device according to claim 4, characterized in that, The process of generating the offspring population in step S33 is specifically: Obtain the number of individuals to be crossed under the genetic population size according to the crossover ratio, and cross the individuals to be crossed in pairs to form new offspring individuals; Obtain the number of individuals that mutate under the genetic population size according to the mutation ratio; Obtain the mutation step vector according to the mutation step coefficient; Obtain the number of parameters to be corrected for mutation according to the mutation rate, and randomly select the positions of the parameters to be corrected; Generate the mutated offspring individuals according to the number of mutated individuals, the mutation step vector, and the parameters to be optimized for mutation; Replace the new offspring individuals at the corresponding positions with the mutated offspring individuals to form the offspring population.

7. Vibration damping device, which applies the parameter optimization method of a tuned mass pipeline vibration damping device according to any one of claims 1-6, characterized in that, It includes shock absorbers fixed on the pipeline structure to be controlled (30) by means of a hoop (10), and at least two shock absorbers are arranged axially and evenly around the axis of the pipeline structure to be controlled (30), and the frequency ratio and damping ratio of each shock absorber respectively correspond to one of the parameter columns in the parameter combination obtained by optimizing the parameter optimization method of the tuned mass pipeline shock absorption device.

8. The vibration damping device according to claim 7, wherein Each of the shock absorbers includes an installation connecting rod (80) with a cross-shaped structure. One end of the installation connecting rod (80) is connected to the hoop (10), and mass blocks (50) are fixed to the other three ends. Magnets (70) are fixed to the outer plate surfaces perpendicular to the corresponding ends of the installation connecting rod (80), and copper plates (60) fixed to the hoop (10) are arranged at each of the magnets (70).

9. The shock absorption device according to claim 8, characterized in that The hoop (10) is composed of two semi-circular rings fixed by connecting bolts (40), and an anti-slip and heat-insulating strip (20) is arranged between the hoop (10) and the pipeline structure to be controlled (30).

Images