Method and device for optimizing transformer substation vibration control device

Abstract

The invention discloses an optimization method and device for a transformer substation vibration control device. Initial vibration control devices, including an initial single-tuned inertial damper, an initial tuned viscous mass damper and an initial double-tuned inertial system, in a transformer substation are collected, and the devices are constructed based on a traditional tuned mass damper by introducing different inertial elements. And then, an H norm optimization method is adopted to finely adjust inertial element parameters in each initial device, so that optimization of the vibration control device is realized, and the problem that a traditional tuned mass damper cannot meet the requirements of the marine environment is solved.

Description

Technical Field

[0001] The present invention relates to the field of substation vibration control device optimization, and in particular to a substation vibration control device optimization method and device. Background Art

[0002] With the rapid development of offshore wind power, offshore substations have become key facilities connecting wind farms and land power grids. Due to long-term exposure to complex marine environments and exposure to excitations such as wind, waves, and ocean currents, substations are susceptible to strong vibrations, posing a certain threat to their long-term safe operation. How to effectively control the vibration of offshore substations has become a technical problem. Traditional tuned mass dampers (TMDs) absorb structural vibration energy by adding mass blocks and are widely used in vibration control due to their simple and effective structure. However, the control effect of TMDs is overly dependent on their added mass, and the larger mass will impose an additional burden on the main structure of the substation. Especially in offshore environments, existing traditional tuned mass dampers cannot meet the needs of offshore environments. Summary of the invention

[0003] The present invention provides an optimization method and device for a transformer substation vibration control device, so as to solve the problem that a traditional tuned mass damper cannot meet the requirements of an offshore environment.

[0004] In a first aspect, the present application provides a method for optimizing a vibration control device of a substation, comprising:

[0005] Obtaining each initial vibration control device in the substation;

[0006] Wherein, each of the initial vibration control devices comprises: an initial single tuned inertial damper, an initial tuned viscous mass damper and an initial double tuned inertial system; each component in each of the initial vibration control devices is constructed based on a tuned mass damper by introducing each inertial element;

[0007] According to the H-norm optimization method, each parameter of each inertial element in each of the initial vibration control devices is optimized respectively to obtain each vibration control device.

[0008] The present application can provide a variety of vibration control solutions for offshore substations by introducing different types of inertial elements and constructing corresponding initial vibration control devices. The first inertial element is used to construct an initial single-tuned inertial damper, the second inertial element is used to construct an initial tuned viscous mass damper, and the third inertial element is used to construct an initial dual-tuned inertial system. The construction of these initial devices is based on the improvement of the traditional tuned mass damper (TMD), and the performance of the TMD is enhanced by introducing inertial elements with different characteristics. Furthermore, the present application uses the H-norm optimization method to fine-tune the parameters of the inertial elements in these initial devices. This optimization process takes into account the dynamic response of the system, especially the worst-case response (through the H∞ norm) and the overall response (through the H2 norm) of the system. The present application can improve the vibration control effect and achieve system lightweighting to solve the problem that traditional tuned mass dampers cannot meet the needs of the offshore environment.

[0009] As a preferred embodiment of the first aspect, the initial single tuned inertial damper is constructed based on a tuned mass damper when a first inertial element is introduced; and the respective parameters of the respective inertial elements in the respective initial vibration control devices are optimized according to the H-norm optimization method, including:

[0010] An initial single tuned inertial damper is constructed according to the first inertial element and the tuned mass damper;

[0011] Optimizing various parameters of the first inertial element of the initial single tuned inertial damper according to the first dynamic amplification function, the infinite H norm and the second H norm to obtain a first inertia coefficient, a first damping coefficient and a first stiffness;

[0012] The initial single tuned inertial damper is optimized according to the first inertia coefficient, the first damping coefficient and the first stiffness to obtain a single tuned inertial damper.

[0013] In this preferred embodiment, the present application uses the H-norm optimization method, especially the infinite H-norm and the second H-norm of the first dynamic amplification function, to perform detailed parameter optimization on the first inertial element in the initial single tuned inertial damper. This process involves calculating the maximum value of the frequency response of the dynamic amplification function and the mean square value of the response in the entire frequency range, so as to accurately adjust the first inertia coefficient, the first damping coefficient and the first stiffness. This comprehensive optimization strategy not only ensures the minimization of the vibration response in the worst case, but also takes into account the overall performance of the system under broadband excitation. The resulting single tuned inertial damper provides a more effective vibration control effect while reducing weight. Therefore, compared with traditional tuned mass dampers, the present application achieves lightweighting of the device and improvement of vibration control performance, making it more suitable for environments with strict requirements on vibration control, such as offshore substations.

[0014] As a preferred embodiment of the first aspect, the initial tuned viscous mass damper is constructed based on a tuned mass damper in the case of a second inertial element; and the respective parameters of the respective inertial elements in the respective initial vibration control devices are optimized according to the H-norm optimization method, including:

[0015] An initial tuned viscous mass damper is constructed according to the second inertial element and the tuned mass damper;

[0016] Optimizing various parameters of the second inertial element of the initial tuned viscous mass damper according to the second dynamic amplification function, the infinite H norm and the second H norm to obtain a second inertia coefficient, a second damping coefficient and a second stiffness;

[0017] The initial tuned viscous mass damper is optimized according to the second inertia coefficient, the second damping coefficient and the second stiffness to obtain a tuned viscous mass damper.

[0018] In this preferred embodiment, the present application optimizes the parameters of the second inertia element of the initial tuned viscous mass damper by applying the H-norm optimization method, uses the infinite H-norm of the second dynamic amplification function to determine the vibration response of the system under the worst case, and uses the second H-norm to evaluate the overall vibration performance of the system under wide-band random excitation. This dual-norm optimization strategy ensures effective control under extreme and continuous vibration conditions, thereby accurately calculating the second inertia coefficient, the second damping coefficient, and the second stiffness. Based on these optimal parameters, the initial tuned viscous mass damper is further optimized, and the obtained tuned viscous mass damper reduces the weight of the device while keeping the structural response within a safe range, thereby improving the operating efficiency and reliability of the offshore substation in a complex marine environment. Therefore, the present application provides a tuned viscous mass damper that can effectively control vibration and reduce the structural burden, and is particularly suitable for offshore substation application scenarios with strict requirements for vibration control.

[0019] As a preferred embodiment of the first aspect, the initial dual tuned inertial system is constructed based on a tuned mass damper in the case of a third inertial element; and the respective parameters of the respective inertial elements in the respective initial vibration control devices are optimized according to the H-norm optimization method, including:

[0020] An initial double tuned inertial system is constructed based on the third inertial element and the tuned mass damper;

[0021] Optimizing various parameters of a third inertial element of the initial double tuned inertial system according to a third dynamic amplification function, an infinite H norm and a second H norm to obtain a third inertia coefficient, a third damping coefficient and a third stiffness;

[0022] The initial dual-tuned inertial system is optimized according to the third inertia coefficient, the third damping coefficient and the third stiffness to obtain a dual-tuned inertial system.

[0023] In this preferred embodiment, the present application uses the H-norm optimization method to make detailed parameter adjustments to the third inertial element of the initial dual-tuned inertial system. First, the third dynamic amplification function is combined with the infinite H-norm to identify and maximize the worst-case vibration response of the system, and then the second H-norm is used to measure and minimize the overall vibration energy efficiency of the system under wide-band excitation. This dual optimization strategy ensures that excellent control effects can be achieved under extreme and continuous vibration conditions. Based on these analyses, the third inertia coefficient, the third damping coefficient and the third stiffness are accurately calculated, and then the initial dual-tuned inertial system is optimized. The resulting dual-tuned inertial system not only performs well in vibration control of multiple frequencies, but also achieves a significant reduction in structural weight compared to traditional designs. Therefore, the present application provides a dual-tuned inertial system that is suitable for complex marine environments, can effectively cope with multi-band vibrations and is more lightweight, greatly improving the long-term operation safety and reliability of offshore substations.

[0024] As a preferred embodiment of the first aspect, the optimization of various parameters of the initial single tuned inertial damper according to the first dynamic amplification function, the infinite H norm and the second H norm is specifically as follows:

[0025] According to the infinite H-norm optimization method and the second H-norm optimization method, maximum values ​​and minimum values ​​of the first inertia coefficient, the first damping coefficient and the first stiffness are calculated;

[0026] The infinite H norm is to determine the respective ranges of the first inertia coefficient, the first damping coefficient and the first stiffness by calculating the maximum value of the frequency response of the first dynamic amplification function, and the infinite H norm optimization calculation formula is:

[0027]

[0028] In the formula, θ opt-∞ (π) represents the optimal parameter determined by infinite H-norm optimization, D max represents the maximum value of the frequency response of the first dynamic amplification function, D represents the first dynamic amplification function, π is a predetermined parameter represented by a vector in the first dynamic amplification function, θ represents the first inertia coefficient, the first damping coefficient and the first stiffness, θ min represents the minimum value of the first inertia coefficient, the first damping coefficient and the first stiffness, θ max represents the maximum value of the first inertia coefficient, the first damping coefficient and the first stiffness;

[0029] The second H norm is to determine the respective ranges of the first inertia coefficient, the first damping coefficient and the first stiffness by calculating the mean square value of the frequency response of the first dynamic amplification function. The calculation formula for optimizing the second H norm is:

[0030] find θ opt-2 (π)

[0031]

[0032] stθ min ≤θ≤θ max

[0033] In the formula, θ opt-2 (π) represents the optimal parameter determined by the second H-norm optimization, and I represents the second H-norm of the first dynamic amplification function.

[0034] In this preferred embodiment, the present application optimizes the parameters of the initial single tuned inertial damper by comprehensively using the infinite H norm and the second H norm optimization method, and can accurately calculate the optimal value range of the first inertia coefficient, the first damping coefficient and the first stiffness. The infinite H norm optimization determines the possible maximum and minimum values ​​of these parameters by evaluating the maximum value of the frequency response of the first dynamic amplification function, thereby ensuring that the vibration response of the system in the worst case is effectively controlled. The second H norm optimization further refines the value range of the parameters by calculating the mean square value of the frequency response of the dynamic amplification function to achieve the overall performance optimization of the system under wide-band excitation. This dual norm optimization strategy not only improves the accuracy and reliability of vibration control, but also achieves fine adjustment of the initial device by accurately controlling the value range of the parameters. The single tuned inertial damper finally obtained provides a more outstanding vibration control effect while maintaining lightweight. Therefore, the present application provides a vibration control device that can not only cope with extreme vibration conditions, but also ensure excellent overall performance, and is particularly suitable for application scenarios such as offshore substations that have strict requirements on vibration control.

[0035] As a preferred embodiment of the first aspect, after optimizing the components in the vibration control device according to the H-norm optimization method, the method further includes:

[0036] According to each equivalent mass ratio, each optimization effect of each parameter of each inertial element is determined when each component in the vibration control device is introduced with each inertial element.

[0037] The optimization effect of each parameter of each component in the initial single tuned inertial damper when the first inertial element is introduced according to the first equivalent mass ratio is determined as follows:

[0038] determining, according to the first equivalent mass ratio, optimization effects of various parameters of the first inertial element;

[0039] The first equivalent mass ratio formula is:

[0040]

[0041] In the formula, μ eq1 It is expressed as the first equivalent mass ratio, β1 is the first inertia ratio, μ1 is the first mass ratio, is the first position correction factor;

[0042] If the value of the first equivalent mass ratio is greater than or equal to a first preset threshold, the optimization effect of each parameter of the first inertial element is determined.

[0043] The optimization effect of each parameter of the second inertial element of each component in the tuned viscous mass damper when the second inertial element is introduced is determined according to the second equivalent mass ratio, specifically:

[0044] determining, according to the second equivalent mass ratio, optimization effects of various parameters of the second inertial element;

[0045] The second equivalent mass ratio formula is:

[0046]

[0047] In the formula, μ eq2 It is expressed as the second equivalent mass ratio, β2 is the second inertia ratio, is the second position correction factor;

[0048] If the value of the second equivalent mass ratio is greater than or equal to a second preset threshold, the optimization effect of each parameter of the second inertial element is determined.

[0049] The optimization effect of each parameter of the third inertial element on each component in the dual tuned inertial system when the third inertial element is introduced according to the third equivalent mass ratio is specifically as follows:

[0050] determining, according to the third equivalent mass ratio, optimization effects of various parameters of the third inertial element;

[0051] The formula of the third equivalent mass ratio is:

[0052] μ eq3 =αμ3,

[0053] In the formula, μ eq3 It is expressed as the third equivalent mass ratio, α is the third mass amplification effect factor, and μ3 is the third mass ratio;

[0054] If the value of the third equivalent mass ratio is greater than or equal to a third preset threshold, the optimization effect of each parameter of the third inertial element is determined.

[0055] In this preferred embodiment, the present application can quantitatively evaluate the effect of inertial element parameter optimization by introducing the concept of equivalent mass ratio. If the value of each equivalent mass ratio is greater than or equal to the preset threshold, this indicates that the actual mass of the inertial element is smaller than the inertial effect (equivalent mass) it produces, indicating that the optimized parameters enable the inertial element to generate a larger inertial force while maintaining a lighter mass, thereby effectively controlling vibration. This optimization effect not only reduces the structural burden, but also improves the vibration control efficiency, achieving lightweight and high-performance control of the device. Therefore, the present application provides a lightweight and efficient vibration control solution for offshore substations through quantitative evaluation of the equivalent mass ratio.

[0056] In a second aspect, the present application provides an optimization device for a substation vibration control device. The optimization device for a substation vibration control device comprises an acquisition module and an optimization module:

[0057] The acquisition module is used to acquire each initial vibration control device in the substation;

[0058] Wherein, each of the initial vibration control devices comprises: an initial single tuned inertial damper, an initial tuned viscous mass damper and an initial double tuned inertial system; each component in each of the initial vibration control devices is constructed based on a tuned mass damper by introducing each inertial element;

[0059] The optimization module is used to optimize the parameters of the inertial elements in the initial vibration control devices according to the H-norm optimization method to obtain the vibration control devices.

[0060] This device uses two modules to divide the work and coordinate the work to better optimize the vibration control device of the substation. This application can provide a variety of vibration control solutions for offshore substations by introducing different types of inertial elements and constructing corresponding initial vibration control devices. The first inertial element is used to construct an initial single-tuned inertial damper, the second inertial element is used to construct an initial tuned viscous mass damper, and the third inertial element is used to construct an initial dual-tuned inertial system. The construction of these initial devices is based on the improvement of the traditional tuned mass damper (TMD), and the performance of the TMD is enhanced by introducing inertial elements with different characteristics. Furthermore, this application uses the H-norm optimization method to fine-tune the parameters of the inertial elements in these initial devices. This optimization process takes into account the dynamic response of the system, especially the worst-case response (through the H∞ norm) and the overall response (through the H2 norm) of the system. This application can improve the vibration control effect and achieve system lightweighting to solve the problem that traditional tuned mass dampers cannot meet the needs of the offshore environment.

[0061] As a preferred embodiment of the second aspect, the initial single tuned inertial damper is constructed based on a tuned mass damper when a first inertial element is introduced; and the respective parameters of the respective inertial elements in the respective initial vibration control devices are optimized according to the H-norm optimization method, including:

[0062] An initial single tuned inertial damper is constructed according to the first inertial element and the tuned mass damper;

[0063] Optimizing various parameters of the first inertial element of the initial single tuned inertial damper according to the first dynamic amplification function, the infinite H norm and the second H norm to obtain a first inertia coefficient, a first damping coefficient and a first stiffness;

[0064] The initial single tuned inertial damper is optimized according to the first inertia coefficient, the first damping coefficient and the first stiffness to obtain a single tuned inertial damper.

[0065] In this preferred embodiment, the present application uses the H-norm optimization method, especially the infinite H-norm and the second H-norm of the first dynamic amplification function, to perform detailed parameter optimization on the first inertial element in the initial single tuned inertial damper. This process involves calculating the maximum value of the frequency response of the dynamic amplification function and the mean square value of the response in the entire frequency range, so as to accurately adjust the first inertia coefficient, the first damping coefficient and the first stiffness. This comprehensive optimization strategy not only ensures the minimization of the vibration response in the worst case, but also takes into account the overall performance of the system under broadband excitation. The resulting single tuned inertial damper provides a more effective vibration control effect while reducing weight. Therefore, compared with traditional tuned mass dampers, the present application achieves lightweighting of the device and improvement of vibration control performance, making it more suitable for environments with strict requirements on vibration control, such as offshore substations.

[0066] As a preferred embodiment of the second aspect, the initial tuned viscous mass damper is constructed based on a tuned mass damper in the case of a second inertial element; and the respective parameters of the respective inertial elements in the respective initial vibration control devices are optimized according to the H-norm optimization method, including:

[0067] An initial tuned viscous mass damper is constructed according to the second inertial element and the tuned mass damper;

[0068] Optimizing various parameters of the second inertial element of the initial tuned viscous mass damper according to the second dynamic amplification function, the infinite H norm and the second H norm to obtain a second inertia coefficient, a second damping coefficient and a second stiffness;

[0069] The initial tuned viscous mass damper is optimized according to the second inertia coefficient, the second damping coefficient and the second stiffness to obtain a tuned viscous mass damper.

[0070] In this preferred embodiment, the present application optimizes the parameters of the second inertia element of the initial tuned viscous mass damper by applying the H-norm optimization method, uses the infinite H-norm of the second dynamic amplification function to determine the vibration response of the system under the worst case, and uses the second H-norm to evaluate the overall vibration performance of the system under wide-band random excitation. This dual-norm optimization strategy ensures effective control under extreme and continuous vibration conditions, thereby accurately calculating the second inertia coefficient, the second damping coefficient, and the second stiffness. Based on these optimal parameters, the initial tuned viscous mass damper is further optimized, and the obtained tuned viscous mass damper reduces the weight of the device while keeping the structural response within a safe range, thereby improving the operating efficiency and reliability of the offshore substation in a complex marine environment. Therefore, the present application provides a tuned viscous mass damper that can effectively control vibration and reduce the structural burden, and is particularly suitable for offshore substation application scenarios with strict requirements for vibration control.

[0071] As a preferred embodiment of the second aspect, the initial dual tuned inertial system is constructed based on a tuned mass damper in the case of a third inertial element; and optimizing the parameters of each inertial element in each initial vibration control device according to the H-norm optimization method respectively includes:

[0072] An initial double tuned inertial system is constructed based on the third inertial element and the tuned mass damper;

[0073] Optimizing various parameters of a third inertial element of the initial double tuned inertial system according to a third dynamic amplification function, an infinite H norm and a second H norm to obtain a third inertia coefficient, a third damping coefficient and a third stiffness;

[0074] The initial dual-tuned inertial system is optimized according to the third inertia coefficient, the third damping coefficient and the third stiffness to obtain a dual-tuned inertial system.

[0075] In this preferred embodiment, the present application uses the H-norm optimization method to make detailed parameter adjustments to the third inertial element of the initial dual-tuned inertial system. First, the third dynamic amplification function is combined with the infinite H-norm to identify and maximize the worst-case vibration response of the system, and then the second H-norm is used to measure and minimize the overall vibration energy efficiency of the system under wide-band excitation. This dual optimization strategy ensures that excellent control effects can be achieved under extreme and continuous vibration conditions. Based on these analyses, the third inertia coefficient, the third damping coefficient and the third stiffness are accurately calculated, and then the initial dual-tuned inertial system is optimized. The resulting dual-tuned inertial system not only performs well in vibration control of multiple frequencies, but also achieves a significant reduction in structural weight compared to traditional designs. Therefore, the present application provides a dual-tuned inertial system that is suitable for complex marine environments, can effectively cope with multi-band vibrations and is more lightweight, greatly improving the long-term operation safety and reliability of offshore substations.

[0076] As a preferred embodiment of the second aspect, the optimization of various parameters of the initial single tuned inertial damper according to the first dynamic amplification function, the infinite H norm and the second H norm is specifically as follows:

[0077] According to the infinite H-norm optimization method and the second H-norm optimization method, maximum values ​​and minimum values ​​of the first inertia coefficient, the first damping coefficient and the first stiffness are calculated;

[0078] The infinite H norm is to determine the respective ranges of the first inertia coefficient, the first damping coefficient and the first stiffness by calculating the maximum value of the frequency response of the first dynamic amplification function, and the infinite H norm optimization calculation formula is:

[0079]

[0080] In the formula, θ opt-∞ (π) represents the optimal parameter determined by infinite H-norm optimization, D max represents the maximum value of the frequency response of the first dynamic amplification function, D represents the first dynamic amplification function, π is a predetermined parameter represented by a vector in the first dynamic amplification function, θ represents the first inertia coefficient, the first damping coefficient and the first stiffness, θ min represents the minimum value of the first inertia coefficient, the first damping coefficient and the first stiffness, θ max represents the maximum value of the first inertia coefficient, the first damping coefficient and the first stiffness;

[0081] The second H norm is to determine the respective ranges of the first inertia coefficient, the first damping coefficient and the first stiffness by calculating the mean square value of the frequency response of the first dynamic amplification function. The calculation formula for optimizing the second H norm is:

[0082] find θ opt-2 (π)

[0083]

[0084] stθ min ≤θ≤θ max

[0085] In the formula, θ opt-2 (π) represents the optimal parameter determined by the second H-norm optimization, and I represents the second H-norm of the first dynamic amplification function.

[0086] In this preferred embodiment, the present application optimizes the parameters of the initial single tuned inertial damper by comprehensively using the infinite H norm and the second H norm optimization method, and can accurately calculate the optimal value range of the first inertia coefficient, the first damping coefficient and the first stiffness. The infinite H norm optimization determines the possible maximum and minimum values ​​of these parameters by evaluating the maximum value of the frequency response of the first dynamic amplification function, thereby ensuring that the vibration response of the system in the worst case is effectively controlled. The second H norm optimization further refines the value range of the parameters by calculating the mean square value of the frequency response of the dynamic amplification function to achieve the overall performance optimization of the system under wide-band excitation. This dual norm optimization strategy not only improves the accuracy and reliability of vibration control, but also achieves fine adjustment of the initial device by accurately controlling the value range of the parameters. The single tuned inertial damper finally obtained provides a more outstanding vibration control effect while maintaining lightweight. Therefore, the present application provides a vibration control device that can not only cope with extreme vibration conditions, but also ensure excellent overall performance, and is particularly suitable for application scenarios such as offshore substations that have strict requirements on vibration control.

[0087] As a preferred embodiment of the second aspect, after optimizing the components in the vibration control device according to the H-norm optimization method, the method further includes:

[0088] According to each equivalent mass ratio, each optimization effect of each parameter of each inertial element is determined when each component in the vibration control device is introduced with each inertial element.

[0089] The optimization effect of each parameter of each component in the initial single tuned inertial damper when the first inertial element is introduced according to the first equivalent mass ratio is determined as follows:

[0090] determining, according to the first equivalent mass ratio, optimization effects of various parameters of the first inertial element;

[0091] The first equivalent mass ratio formula is:

[0092]

[0093] In the formula, μ eq1 It is expressed as the first equivalent mass ratio, β1 is the first inertia ratio, μ1 is the first mass ratio, is the first position correction factor;

[0094] If the value of the first equivalent mass ratio is greater than or equal to a first preset threshold, the optimization effect of each parameter of the first inertial element is determined.

[0095] The optimization effect of each parameter of the second inertial element of each component in the tuned viscous mass damper when the second inertial element is introduced is determined according to the second equivalent mass ratio, specifically:

[0096] determining, according to the second equivalent mass ratio, optimization effects of various parameters of the second inertial element;

[0097] The second equivalent mass ratio formula is:

[0098]

[0099] In the formula, μ eq2 It is expressed as the second equivalent mass ratio, β2 is the second inertia ratio, is the second position correction factor;

[0100] If the value of the second equivalent mass ratio is greater than or equal to a second preset threshold, the optimization effect of each parameter of the second inertial element is determined.

[0101] The optimization effect of each parameter of the third inertial element on each component in the dual tuned inertial system when the third inertial element is introduced according to the third equivalent mass ratio is specifically as follows:

[0102] determining, according to the third equivalent mass ratio, optimization effects of various parameters of the third inertial element;

[0103] The formula of the third equivalent mass ratio is:

[0104] μ eq3 =αμ3,

[0105] In the formula, μ eq3 It is expressed as the third equivalent mass ratio, α is the third mass amplification effect factor, and μ3 is the third mass ratio;

[0106] If the value of the third equivalent mass ratio is greater than or equal to a third preset threshold, the optimization effect of each parameter of the third inertial element is determined.

[0107] In this preferred embodiment, the present application can quantitatively evaluate the effect of inertial element parameter optimization by introducing the concept of equivalent mass ratio. If the value of each equivalent mass ratio is greater than or equal to the preset threshold, this indicates that the actual mass of the inertial element is smaller than the inertial effect (equivalent mass) it produces, indicating that the optimized parameters enable the inertial element to generate a larger inertial force while maintaining a lighter mass, thereby effectively controlling vibration. This optimization effect not only reduces the structural burden, but also improves the vibration control efficiency, achieving lightweight and high-performance control of the device. Therefore, the present application provides a lightweight and efficient vibration control solution for offshore substations through quantitative evaluation of the equivalent mass ratio. BRIEF DESCRIPTION OF THE DRAWINGS

[0108] Figure 1 : A flow chart of an embodiment of an optimization method for a substation vibration control device provided by the present application;

[0109] Figure 2 : A structural schematic diagram of an embodiment of a method for connecting a vibration control device of a substation provided by the present application;

[0110] Figure 3 : A structural schematic diagram of an embodiment of an optimization device for a substation vibration control device provided in the present application. DETAILED DESCRIPTION

[0111] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0112] Embodiment 1

[0113] Please refer to Figure 1 , which is an optimization method for a substation vibration control device provided by an embodiment of the present invention.

[0114] Traditional tuned mass dampers (TMDs) absorb structural vibration energy by adding mass blocks. They are widely used in vibration control due to their simple and effective structure. However, the control effect of TMDs is overly dependent on their added mass, and the large mass will cause additional burden on the main structure of the substation. Especially in offshore environments, reducing the weight of the structure is an important design requirement.

[0115] This application optimizes and upgrades the traditional TMD by introducing an inertial element. An inertial element is a mechanical element that can output a force proportional to the relative acceleration, which is equivalent to a large mass block in a TMD, but its actual mass is much smaller than the simulated mass block.

[0116] This application proposes three vibration device designs based on a single tuned inertial damper (TMDI), a tuned viscous mass damper (TVMD), and a dual tuned system (RIDTMD), such as Figure 2 As shown in the figure, according to the needs, three vibration devices are suitable for different offshore substation scenarios:

[0117] A. Single tuned inertial damper (TMDI): Combines inertial elements with traditional TMDs to achieve lightweight design through parameter optimization. Applicable scenarios: Applicable to offshore small offshore substations that need to reduce mass burden but require better vibration control effects.

[0118] B. Tuned Viscous Mass Damper (TVMD): Use inertial elements to completely replace mass blocks, and optimize the parameters of inertial elements to achieve a higher lightweight effect. Applicable scenarios: Applicable to offshore medium-sized substations with high requirements for vibration control performance but strict mass restrictions.

[0119] C. Dual-tuned inertial system (RIDTMD): It uses a complex dual-tuned network, also introduces inertial elements and mass blocks, and optimizes the parameters of the inertial elements. While achieving tuning at different frequencies, it further improves the vibration control effect and reduces the mass. Applicable scenarios: It is suitable for complex environments that need to cope with multiple vibration frequencies, and requires precise control of vibrations in multiple frequency bands. At the same time, it requires high vibration control requirements for large offshore substations and large offshore wind power generation equipment.

[0120] In this embodiment, the process of the optimization method of the substation vibration control device in the present application is described in detail through steps S01-S02.

[0121] S01: Acquire each initial vibration control device in the substation; wherein, each initial vibration control device includes: an initial single tuned inertial damper, an initial tuned viscous mass damper and an initial double tuned inertial system; each component in each initial vibration control device is constructed based on a tuned mass damper by introducing each inertial element.

[0122] S02: Optimizing the parameters of the inertial elements in the initial vibration control devices respectively according to the H-norm optimization method to obtain the vibration control devices.

[0123] As a preferred embodiment of the first embodiment, the H-norm optimization method is used to optimize the parameters of the inertial elements in the initial vibration control devices, specifically:

[0124] The optimal parameters of various vibration control devices based on inertial elements, including inertia coefficient, damping coefficient, stiffness, etc., are determined by the H-norm optimization method. The overall process of configuring the optimal parameters by the H-norm optimization method is as follows:

[0125] ①Define design goals and constraints;

[0126] The clear goal is to optimize the parameters of the vibration control devices (TMDI, TVMD, RIMTMD) by introducing inertial elements, so as to ensure or improve the vibration control effect while achieving lightweight design.

[0127] ②Select a vibration control device solution;

[0128] Choose the most suitable type of vibration control device based on specific application scenarios and design requirements.

[0129] ③ Determine the dynamic characteristics and control requirements of the vibration control device;

[0130] Natural frequency of the main structure of the substation ω n ;

[0131] The tuning frequency ratio v of the vibration control device;

[0132] The tuned inertia ratio β of the vibration control device;

[0133] Nominal damping ratio ζ of the vibration control device d ;

[0134] ④Determine the dynamic amplification function;

[0135] The equation transformation of the structural vibration response (system transfer function) is converted into a dimensionless form by the dimensionless method:

[0136]

[0137] Among them, for the three devices TMDI, TVMD and RIDTMD, the polynomial in the transfer function It will vary according to its structural form and parameters.

[0138] For the monotonic oscillation control device, there are:

[0139]

[0140] For a tuned viscous mass damped vibration device:

[0141]

[0142] For a dual-tuned oscillator, we have:

[0143]

[0144] in, is defined as a dimensionless mechanical impedance function and is used to make the transfer functions of the three devices dimensionless:

[0145]

[0146] The dynamic amplification functions of the three device schemes are expressed as:

[0147]

[0148] In the above equation, the dimensionless excitation frequency is defined as ω is the system frequency; ω n is the natural frequency of the main structure of the substation; is the position correction factor; n is the damping ratio of the first-level offshore substation structure; μ is the tuning mass ratio of the vibration control device; β is the tuning inertia ratio of the vibration control device; v is the tuning frequency ratio of the vibration control device; γ is the secondary tuning frequency ratio; ζ d is the nominal damping ratio of the vibration control device; λ is the dimensionless complex frequency; C3, C4, and C6 are the models of the double-tuned vibration device.

[0149] ⑤Optimize parameters through H norm;

[0150] H-norm optimization includes infinite norm optimization (H ∞ Optimization) and second norm optimization (H 2 Optimization) two parts:

[0151] 1.H ∞ The optimization goal is to minimize the infinite norm D of the dynamic amplification function. max , find the maximum value of the corresponding frequency response, which is applicable to structures subjected to excitations of various frequencies.

[0152] findθ opt-∞ (π),

[0153] minimizeD max =∥D(Ω;π,θ)∥ ∞ =max{D(Ω;π,θ)},

[0154] stθ min ≤θ≤θ max .

[0155] In the formula, θ opt-∞ (π) represents the optimal parameter determined by infinite H-norm optimization, D max represents the maximum value of the frequency response of the first dynamic amplification function, D represents the first dynamic amplification function, π is a predetermined parameter represented by a vector in the first dynamic amplification function, θ represents the first inertia coefficient, the first damping coefficient and the first stiffness, θ min represents the minimum value of the first inertia coefficient, the first damping coefficient and the first stiffness, θ max represents the maximum value of the first inertia coefficient, the first damping coefficient and the first stiffness;

[0156] The best vibration effect can be achieved by adjusting various parameters of the inertial element (such as inertia-volume ratio β, mass ratio μ, etc.).

[0157] 2.H 2 The optimization goal is to minimize the second norm I of the dynamic amplification function, which reflects the mean square value of the structure's response over the entire frequency range and is particularly suitable for broadband random excitation.

[0158] findθ opt-2 (π),

[0159]

[0160] stθ min ≤θ≤θ max .

[0161] In the formula, θ opt-2 (π) represents the optimal parameter determined by the second H-norm optimization, and I represents the second H-norm of the first dynamic amplification function;

[0162] This step uses numerical optimization to determine the optimal inertia coefficient β and damping coefficient ζ d , stiffness k and other underdetermined parameters. The parameters of the vibration control device are represented by predetermined parameters represented by π as a vector and underdetermined parameters represented by θ as a vector. opt-∞ (π) and θ opt-2 (π) represents the optimal underdetermined parameter determined by norm optimization; θ min ,θ max Represents the lower and upper bounds of the parameter vector.

[0163] In this preferred embodiment, the present application optimizes the parameters of the initial single tuned inertial damper by comprehensively using the infinite H norm and the second H norm optimization method, and can accurately calculate the optimal value range of the first inertia coefficient, the first damping coefficient and the first stiffness. The infinite H norm optimization determines the possible maximum and minimum values ​​of these parameters by evaluating the maximum value of the frequency response of the first dynamic amplification function, thereby ensuring that the vibration response of the system in the worst case is effectively controlled. The second H norm optimization further refines the value range of the parameters by calculating the mean square value of the frequency response of the dynamic amplification function to achieve the overall performance optimization of the system under wide-band excitation. This dual norm optimization strategy not only improves the accuracy and reliability of vibration control, but also achieves fine adjustment of the initial device by accurately controlling the value range of the parameters. The single tuned inertial damper finally obtained provides a more outstanding vibration control effect while maintaining lightweight. Therefore, the present application provides a vibration control device that can not only cope with extreme vibration conditions, but also ensure excellent overall performance, and is particularly suitable for application scenarios such as offshore substations that have strict requirements on vibration control.

[0164] As a preferred embodiment of the first embodiment, the initial single tuned inertial damper is constructed based on a tuned mass damper when a first inertial element is introduced; and the H-norm optimization method is used to optimize the parameters of the inertial elements in the initial vibration control devices, respectively, including:

[0165] An initial single tuned inertial damper is constructed according to the first inertial element and the tuned mass damper;

[0166] Optimizing various parameters of the first inertial element of the initial single tuned inertial damper according to the first dynamic amplification function, the infinite H norm and the second H norm to obtain a first inertia coefficient, a first damping coefficient and a first stiffness;

[0167] The initial single tuned inertial damper is optimized according to the first inertia coefficient, the first damping coefficient and the first stiffness to obtain a single tuned inertial damper.

[0168] In this preferred embodiment, the present application uses the H-norm optimization method, especially the infinite H-norm and the second H-norm of the first dynamic amplification function, to perform detailed parameter optimization on the first inertial element in the initial single tuned inertial damper. This process involves calculating the maximum value of the frequency response of the dynamic amplification function and the mean square value of the response in the entire frequency range, so as to accurately adjust the first inertia coefficient, the first damping coefficient and the first stiffness. This comprehensive optimization strategy not only ensures the minimization of the vibration response in the worst case, but also takes into account the overall performance of the system under broadband excitation. The resulting single tuned inertial damper provides a more effective vibration control effect while reducing weight. Therefore, compared with traditional tuned mass dampers, the present application achieves lightweighting of the device and improvement of vibration control performance, making it more suitable for environments with strict requirements on vibration control, such as offshore substations.

[0169] As a preferred embodiment of the first embodiment, the initial tuned viscous mass damper is constructed based on a tuned mass damper in the case of a second inertial element; the optimization of the parameters of the inertial elements in the initial vibration control devices according to the H-norm optimization method includes:

[0170] An initial tuned viscous mass damper is constructed according to the second inertial element and the tuned mass damper;

[0171] Optimizing various parameters of the second inertial element of the initial tuned viscous mass damper according to the second dynamic amplification function, the infinite H norm and the second H norm to obtain a second inertia coefficient, a second damping coefficient and a second stiffness;

[0172] The initial tuned viscous mass damper is optimized according to the second inertia coefficient, the second damping coefficient and the second stiffness to obtain a tuned viscous mass damper.

[0173] In this preferred embodiment, the present application optimizes the parameters of the second inertia element of the initial tuned viscous mass damper by applying the H-norm optimization method, uses the infinite H-norm of the second dynamic amplification function to determine the vibration response of the system under the worst case, and uses the second H-norm to evaluate the overall vibration performance of the system under wide-band random excitation. This dual-norm optimization strategy ensures effective control under extreme and continuous vibration conditions, thereby accurately calculating the second inertia coefficient, the second damping coefficient, and the second stiffness. Based on these optimal parameters, the initial tuned viscous mass damper is further optimized, and the obtained tuned viscous mass damper reduces the weight of the device while keeping the structural response within a safe range, thereby improving the operating efficiency and reliability of the offshore substation in a complex marine environment. Therefore, the present application provides a tuned viscous mass damper that can effectively control vibration and reduce the structural burden, and is particularly suitable for offshore substation application scenarios with strict requirements for vibration control.

[0174] As a preferred embodiment of the first embodiment, the initial dual tuned inertial system is constructed based on a tuned mass damper in the case of a third inertial element; the H-norm optimization method is used to optimize the parameters of the inertial elements in the initial vibration control devices, including:

[0175] An initial double tuned inertial system is constructed based on the third inertial element and the tuned mass damper;

[0176] Optimizing various parameters of a third inertial element of the initial double tuned inertial system according to a third dynamic amplification function, an infinite H norm and a second H norm to obtain a third inertia coefficient, a third damping coefficient and a third stiffness;

[0177] The initial dual-tuned inertial system is optimized according to the third inertia coefficient, the third damping coefficient and the third stiffness to obtain a dual-tuned inertial system.

[0178] In this preferred embodiment, the present application uses the H-norm optimization method to make detailed parameter adjustments to the third inertial element of the initial dual-tuned inertial system. First, the third dynamic amplification function is combined with the infinite H-norm to identify and maximize the worst-case vibration response of the system, and then the second H-norm is used to measure and minimize the overall vibration energy efficiency of the system under wide-band excitation. This dual optimization strategy ensures that excellent control effects can be achieved under extreme and continuous vibration conditions. Based on these analyses, the third inertia coefficient, the third damping coefficient and the third stiffness are accurately calculated, and then the initial dual-tuned inertial system is optimized. The resulting dual-tuned inertial system not only performs well in vibration control of multiple frequencies, but also achieves a significant reduction in structural weight compared to traditional designs. Therefore, the present application provides a dual-tuned inertial system that is suitable for complex marine environments, can effectively cope with multi-band vibrations and is more lightweight, greatly improving the long-term operation safety and reliability of offshore substations.

[0179] As a preferred embodiment of the first embodiment, after optimizing the components in the vibration control device according to the H-norm optimization method, the method further includes:

[0180] According to each equivalent mass ratio, each optimization effect of each parameter of each inertial element is determined when each component in the vibration control device is introduced with each inertial element.

[0181] Furthermore, the optimization effect of each parameter of the first inertial element when the first inertial element is introduced into each component in the initial single tuned inertial damper according to the first equivalent mass ratio is specifically as follows:

[0182] determining, according to the first equivalent mass ratio, optimization effects of various parameters of the first inertial element;

[0183] The equivalent mass μ of the monotonic oscillation control device eq It is expressed as: The applicable scope of equivalent mass is: Outside this range, the use of inertial elements cannot effectively improve vibration control performance.

[0184] Furthermore, the optimization effect of each parameter of the second inertial element when the second inertial element is introduced into each component in the tuned viscous mass damper according to the second equivalent mass ratio is specifically as follows:

[0185] determining, according to the second equivalent mass ratio, optimization effects of various parameters of the second inertial element;

[0186] The equivalent mass μ of the tuned viscous mass damping vibration control device eq It is expressed as: The applicable scope of equivalent mass depends on the object requirements. Different requirements have different thresholds ∈ for the vibration control effect. eq >∈.

[0187] Furthermore, the optimization effect of each parameter of the third inertial element when the third inertial element is introduced into each component in the dual tuned inertial system according to the third equivalent mass ratio is specifically as follows:

[0188] determining, according to the third equivalent mass ratio, optimization effects of various parameters of the third inertial element;

[0189] The equivalent mass μ of the dual-tuned vibration control device eq Expressed as: μ eq =αμ, where α is the mass amplification factor. The coefficient α will be controlled by the optimal H of the double-tuned vibration control device. 2 Optimal H norm and conventional TMD 2 The norm is equal to determine, expressed as I opt ,

[0190]

[0191] The applicable scope of equivalent mass is: and β 1 and β 2 are the inertia-capacitance ratio in the two frequency ranges, and are the correction factors in the two frequency ranges, μ 1 and μ 1 are the mass ratios in the two frequency ranges, respectively.

[0192] In this preferred embodiment, the present application can quantitatively evaluate the effect of inertial element parameter optimization by introducing the concept of equivalent mass ratio. If the value of each equivalent mass ratio is greater than or equal to the preset threshold, this indicates that the actual mass of the inertial element is smaller than the inertial effect (equivalent mass) it produces, indicating that the optimized parameters enable the inertial element to generate a larger inertial force while maintaining a lighter mass, thereby effectively controlling vibration. This optimization effect not only reduces the structural burden, but also improves the vibration control efficiency, achieving lightweight and high-performance control of the device. Therefore, the present application provides a lightweight and efficient vibration control solution for offshore substations through quantitative evaluation of the equivalent mass ratio.

[0193] The present application can provide a variety of vibration control solutions for offshore substations by introducing different types of inertial elements and constructing corresponding initial vibration control devices. The first inertial element is used to construct an initial single-tuned inertial damper, the second inertial element is used to construct an initial tuned viscous mass damper, and the third inertial element is used to construct an initial dual-tuned inertial system. The construction of these initial devices is based on the improvement of the traditional tuned mass damper (TMD), and the performance of the TMD is enhanced by introducing inertial elements with different characteristics. Furthermore, the present application uses the H-norm optimization method to fine-tune the parameters of the inertial elements in these initial devices. This optimization process takes into account the dynamic response of the system, especially the worst-case response (through the H∞ norm) and the overall response (through the H2 norm) of the system. The present application can improve the vibration control effect and achieve system lightweighting to solve the problem that traditional tuned mass dampers cannot meet the needs of the offshore environment.

[0194] Embodiment 2

[0195] Please refer to Figure 3 , which is an optimization device for a substation vibration control device provided in an embodiment of the present application.

[0196] Traditional tuned mass dampers (TMDs) absorb structural vibration energy by adding mass blocks. They are widely used in vibration control due to their simple and effective structure. However, the control effect of TMDs is overly dependent on their added mass, and the large mass will cause additional burden on the main structure of the substation. Especially in offshore environments, reducing the weight of the structure is an important design requirement.

[0197] This application optimizes and upgrades the traditional TMD by introducing an inertial element. An inertial element is a mechanical element that can output a force proportional to the relative acceleration, which is equivalent to a large mass block in a TMD, but its actual mass is much smaller than the simulated mass block.

[0198] This application proposes three vibration device designs based on a single tuned inertial damper (TMDI), a tuned viscous mass damper (TVMD), and a dual tuned system (RIDTMD), such as Figure 2 As shown in the figure, according to the needs, three vibration devices are suitable for different offshore substation scenarios:

[0199] A. Single tuned inertial damper (TMDI): Combines inertial elements with traditional TMDs to achieve lightweight design through parameter optimization. Applicable scenarios: Applicable to offshore small offshore substations that need to reduce mass burden but require better vibration control effects.

[0200] B. Tuned Viscous Mass Damper (TVMD): Use inertial elements to completely replace mass blocks, and optimize the parameters of inertial elements to achieve a higher lightweight effect. Applicable scenarios: Applicable to offshore medium-sized substations with high requirements for vibration control performance but strict mass restrictions.

[0201] C. Dual-tuned inertial system (RIDTMD): It uses a complex dual-tuned network, also introduces inertial elements and mass blocks, and optimizes the parameters of the inertial elements. While achieving tuning at different frequencies, it further improves the vibration control effect and reduces the mass. Applicable scenarios: It is suitable for complex environments that need to cope with multiple vibration frequencies, and requires precise control of vibrations in multiple frequency bands. At the same time, it requires high vibration control requirements for large offshore substations and large offshore wind power generation equipment.

[0202] In this embodiment, the optimization device of the substation vibration control device includes an acquisition module 10 and an optimization module 20 .

[0203] The acquisition module 10 is used to acquire each initial vibration control device in the substation; wherein, each initial vibration control device includes: an initial single tuned inertial damper, an initial tuned viscous mass damper and an initial double tuned inertial system; each component in each initial vibration control device is constructed based on a tuned mass damper by introducing each inertial element.

[0204] The optimization module 20 is used to optimize the parameters of the inertial elements in the initial vibration control devices according to the H-norm optimization method to obtain the vibration control devices.

[0205] As a preferred embodiment of the second embodiment, the parameters of each inertial element in each initial vibration control device are optimized respectively according to the H-norm optimization method, specifically:

[0206] The optimal parameters of various vibration control devices based on inertial elements, including inertia coefficient, damping coefficient, stiffness, etc., are determined by the H-norm optimization method. The overall process of configuring the optimal parameters by the H-norm optimization method is as follows:

[0207] ①Define design goals and constraints;

[0208] The clear goal is to optimize the parameters of the vibration control devices (TMDI, TVMD, RIMTMD) by introducing inertial elements, so as to ensure or improve the vibration control effect while achieving lightweight design.

[0209] ②Select a vibration control device solution;

[0210] Choose the most suitable type of vibration control device based on specific application scenarios and design requirements.

[0211] ③ Determine the dynamic characteristics and control requirements of the vibration control device;

[0212] Natural frequency of the main structure of the substation ω n ;

[0213] The tuning frequency ratio v of the vibration control device;

[0214] The tuned inertia ratio β of the vibration control device;

[0215] Nominal damping ratio ζ of the vibration control device d ;

[0216] ④Determine the dynamic amplification function;

[0217] The equation transformation of the structural vibration response (system transfer function) is converted into a dimensionless form by the dimensionless method:

[0218]

[0219] Among them, for the three devices TMDI, TVMD and RIDTMD, the polynomial in the transfer function It will vary according to its structural form and parameters.

[0220] For the monotonic oscillation control device, there are:

[0221]

[0222] For a tuned viscous mass damped vibration device:

[0223]

[0224] For a dual-tuned oscillator, we have:

[0225]

[0226] in, is defined as a dimensionless mechanical impedance function and is used to make the transfer functions of the three devices dimensionless:

[0227]

[0228] The dynamic amplification functions of the three device schemes are expressed as:

[0229]

[0230] In the above equation, the dimensionless excitation frequency is defined as ω is the system frequency; ω n is the natural frequency of the main structure of the substation; is the position correction factor; n is the damping ratio of the first-level offshore substation structure; μ is the tuning mass ratio of the vibration control device; β is the tuning inertia ratio of the vibration control device; v is the tuning frequency ratio of the vibration control device; γ is the secondary tuning frequency ratio; ζ d is the nominal damping ratio of the vibration control device; λ is the dimensionless complex frequency; C3, C4, and C6 are the models of the double-tuned vibration device.

[0231] ⑤Optimize parameters through H norm;

[0232] H-norm optimization includes infinite-norm optimization (H ∞ Optimization) and second norm optimization (H 2 Optimization) two parts:

[0233] 1.H ∞ The optimization goal is to minimize the infinite norm D of the dynamic amplification function. max , find the maximum value of the corresponding frequency response, which is applicable to structures subjected to excitations of various frequencies.

[0234] findθ opt-∞ (π),

[0235] minimizeD max =∥D(Ω;π,θ)∥ ∞ =max{D(Ω;π,θ)},

[0236] stθ min ≤θ≤θ max .

[0237] The best vibration effect can be achieved by adjusting various parameters of the inertial element (such as inertia-volume ratio β, mass ratio μ, etc.).

[0238] 2.H 2 The optimization goal is to minimize the second norm I of the dynamic amplification function, which reflects the mean square value of the structure's response over the entire frequency range and is particularly suitable for broadband random excitation.

[0239] findθ opt-2 (π),

[0240]

[0241] stθ min ≤θ≤θ max .

[0242] In the formula, θ opt-2 (π) represents the optimal parameter determined by the second H-norm optimization, and I represents the second H-norm of the first dynamic amplification function.

[0243] This step uses numerical optimization to determine the optimal inertia coefficient β and damping coefficient ζ d , stiffness k and other underdetermined parameters. The parameters of the vibration control device are represented by predetermined parameters represented by π as a vector and underdetermined parameters represented by θ as a vector. opt-∞ (π) and θ opt-2 (π) represents the optimal underdetermined parameter determined by norm optimization; θ min ,θ max Represents the lower and upper bounds of the parameter vector.

[0244] In this preferred embodiment, the present application optimizes the parameters of the initial single tuned inertial damper by comprehensively using the infinite H norm and the second H norm optimization method, and can accurately calculate the optimal value range of the first inertia coefficient, the first damping coefficient and the first stiffness. The infinite H norm optimization determines the possible maximum and minimum values ​​of these parameters by evaluating the maximum value of the frequency response of the first dynamic amplification function, thereby ensuring that the vibration response of the system in the worst case is effectively controlled. The second H norm optimization further refines the value range of the parameters by calculating the mean square value of the frequency response of the dynamic amplification function to achieve the overall performance optimization of the system under wide-band excitation. This dual norm optimization strategy not only improves the accuracy and reliability of vibration control, but also achieves fine adjustment of the initial device by accurately controlling the value range of the parameters. The single tuned inertial damper finally obtained provides a more outstanding vibration control effect while maintaining lightweight. Therefore, the present application provides a vibration control device that can not only cope with extreme vibration conditions, but also ensure excellent overall performance, and is particularly suitable for application scenarios such as offshore substations that have strict requirements on vibration control.

[0245] As a preferred embodiment of the second embodiment, the initial single tuned inertial damper is constructed based on a tuned mass damper when the first inertial element is introduced; and the H-norm optimization method is used to optimize the parameters of the inertial elements in the initial vibration control devices, respectively, including:

[0246] An initial single tuned inertial damper is constructed according to the first inertial element and the tuned mass damper;

[0247] Optimizing various parameters of the first inertial element of the initial single tuned inertial damper according to the first dynamic amplification function, the infinite H norm and the second H norm to obtain a first inertia coefficient, a first damping coefficient and a first stiffness;

[0248] The initial single tuned inertial damper is optimized according to the first inertia coefficient, the first damping coefficient and the first stiffness to obtain a single tuned inertial damper.

[0249] In this preferred embodiment, the present application uses the H-norm optimization method, especially the infinite H-norm and the second H-norm of the first dynamic amplification function, to perform detailed parameter optimization on the first inertial element in the initial single tuned inertial damper. This process involves calculating the maximum value of the frequency response of the dynamic amplification function and the mean square value of the response in the entire frequency range, so as to accurately adjust the first inertia coefficient, the first damping coefficient and the first stiffness. This comprehensive optimization strategy not only ensures the minimization of the vibration response in the worst case, but also takes into account the overall performance of the system under broadband excitation. The resulting single tuned inertial damper provides a more effective vibration control effect while reducing weight. Therefore, compared with traditional tuned mass dampers, the present application achieves lightweighting of the device and improvement of vibration control performance, making it more suitable for environments with strict requirements on vibration control, such as offshore substations.

[0250] As a preferred embodiment of the second embodiment, the initial tuned viscous mass damper is constructed based on a tuned mass damper in the case of a second inertial element; the H-norm optimization method is used to optimize the parameters of the inertial elements in the initial vibration control devices, including:

[0251] An initial tuned viscous mass damper is constructed according to the second inertial element and the tuned mass damper;

[0252] Optimizing various parameters of the second inertial element of the initial tuned viscous mass damper according to the second dynamic amplification function, the infinite H norm and the second H norm to obtain a second inertia coefficient, a second damping coefficient and a second stiffness;

[0253] The initial tuned viscous mass damper is optimized according to the second inertia coefficient, the second damping coefficient and the second stiffness to obtain a tuned viscous mass damper.

[0254] In this preferred embodiment, the present application optimizes the parameters of the second inertia element of the initial tuned viscous mass damper by applying the H-norm optimization method, uses the infinite H-norm of the second dynamic amplification function to determine the vibration response of the system under the worst case, and uses the second H-norm to evaluate the overall vibration performance of the system under wide-band random excitation. This dual-norm optimization strategy ensures effective control under extreme and continuous vibration conditions, thereby accurately calculating the second inertia coefficient, the second damping coefficient, and the second stiffness. Based on these optimal parameters, the initial tuned viscous mass damper is further optimized, and the obtained tuned viscous mass damper reduces the weight of the device while keeping the structural response within a safe range, thereby improving the operating efficiency and reliability of the offshore substation in a complex marine environment. Therefore, the present application provides a tuned viscous mass damper that can effectively control vibration and reduce the structural burden, and is particularly suitable for offshore substation application scenarios with strict requirements for vibration control.

[0255] As a preferred embodiment of the second embodiment, the initial dual tuned inertial system is constructed based on a tuned mass damper in the case of a third inertial element; the H-norm optimization method is used to optimize the parameters of the inertial elements in the initial vibration control devices, including:

[0256] An initial double tuned inertial system is constructed based on the third inertial element and the tuned mass damper;

[0257] Optimizing various parameters of a third inertial element of the initial double tuned inertial system according to a third dynamic amplification function, an infinite H norm and a second H norm to obtain a third inertia coefficient, a third damping coefficient and a third stiffness;

[0258] The initial dual-tuned inertial system is optimized according to the third inertia coefficient, the third damping coefficient and the third stiffness to obtain a dual-tuned inertial system.

[0259] In this preferred embodiment, the present application uses the H-norm optimization method to make detailed parameter adjustments to the third inertial element of the initial dual-tuned inertial system. First, the third dynamic amplification function is combined with the infinite H-norm to identify and maximize the worst-case vibration response of the system, and then the second H-norm is used to measure and minimize the overall vibration energy efficiency of the system under wide-band excitation. This dual optimization strategy ensures that excellent control effects can be achieved under extreme and continuous vibration conditions. Based on these analyses, the third inertia coefficient, the third damping coefficient and the third stiffness are accurately calculated, and then the initial dual-tuned inertial system is optimized. The resulting dual-tuned inertial system not only performs well in vibration control of multiple frequencies, but also achieves a significant reduction in structural weight compared to traditional designs. Therefore, the present application provides a dual-tuned inertial system that is suitable for complex marine environments, can effectively cope with multi-band vibrations and is more lightweight, greatly improving the long-term operation safety and reliability of offshore substations.

[0260] As a preferred embodiment of the second embodiment, after optimizing the components in the vibration control device according to the H-norm optimization method, the method further includes:

[0261] According to each equivalent mass ratio, each optimization effect of each parameter of each inertial element is determined when each component in the vibration control device is introduced with each inertial element.

[0262] Furthermore, the optimization effect of each parameter of the first inertial element when the first inertial element is introduced into each component in the initial single tuned inertial damper according to the first equivalent mass ratio is specifically as follows:

[0263] determining, according to the first equivalent mass ratio, optimization effects of various parameters of the first inertial element;

[0264] The equivalent mass μ of the monotonic oscillation control device eq It is expressed as: The applicable scope of equivalent mass is: Outside this range, the use of inertial elements cannot effectively improve vibration control performance.

[0265] Furthermore, the optimization effect of each parameter of the second inertial element when the second inertial element is introduced into each component in the tuned viscous mass damper according to the second equivalent mass ratio is specifically as follows:

[0266] determining, according to the second equivalent mass ratio, optimization effects of various parameters of the second inertial element;

[0267] The equivalent mass μ of the tuned viscous mass damping vibration control device eq It is expressed as: The applicable scope of equivalent mass depends on the object requirements. Different requirements have different thresholds ∈ for the vibration control effect. eq >∈.

[0268] Furthermore, the optimization effect of each parameter of the third inertial element when the third inertial element is introduced into each component in the dual tuned inertial system according to the third equivalent mass ratio is specifically as follows:

[0269] determining, according to the third equivalent mass ratio, optimization effects of various parameters of the third inertial element;

[0270] The equivalent mass μ of the dual-tuned vibration control device eq Expressed as: μ eq =αμ, where α is the mass amplification factor. The coefficient α will be controlled by the optimal H of the double-tuned vibration control device. 2 Optimal H norm and conventional TMD 2 The norm is equal to determine, expressed as I opt ,

[0271]

[0272] The applicable scope of equivalent mass is: and β 1 and β 2 are the inertia-capacitance ratio in the two frequency ranges, and are the correction factors in the two frequency ranges, μ 1 and μ 1 are the mass ratios in the two frequency ranges, respectively.

[0273] In this preferred embodiment, the present application can quantitatively evaluate the effect of inertial element parameter optimization by introducing the concept of equivalent mass ratio. If the value of each equivalent mass ratio is greater than or equal to the preset threshold, this indicates that the actual mass of the inertial element is smaller than the inertial effect (equivalent mass) it produces, indicating that the optimized parameters enable the inertial element to generate a larger inertial force while maintaining a lighter mass, thereby effectively controlling vibration. This optimization effect not only reduces the structural burden, but also improves the vibration control efficiency, achieving lightweight and high-performance control of the device. Therefore, the present application provides a lightweight and efficient vibration control solution for offshore substations through quantitative evaluation of the equivalent mass ratio.

[0274] This device uses two modules to divide the work and coordinate the work to better optimize the vibration control device of the substation. This application can provide a variety of vibration control solutions for offshore substations by introducing different types of inertial elements and constructing corresponding initial vibration control devices. The first inertial element is used to construct an initial single-tuned inertial damper, the second inertial element is used to construct an initial tuned viscous mass damper, and the third inertial element is used to construct an initial dual-tuned inertial system. The construction of these initial devices is based on the improvement of the traditional tuned mass damper (TMD), and the performance of the TMD is enhanced by introducing inertial elements with different characteristics. Furthermore, this application uses the H-norm optimization method to fine-tune the parameters of the inertial elements in these initial devices. This optimization process takes into account the dynamic response of the system, especially the worst-case response (through the H∞ norm) and the overall response (through the H2 norm) of the system. This application can improve the vibration control effect and achieve system lightweighting to solve the problem that traditional tuned mass dampers cannot meet the needs of the offshore environment.

[0275] The specific embodiments described above further illustrate the purpose, technical solutions and beneficial effects of the present invention. It should be understood that the above description is only a specific embodiment of the present invention and is not intended to limit the scope of protection of the present invention. It is particularly pointed out that for those skilled in the art, any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the scope of protection of the present invention.

Claims

1. A method for optimizing a vibration control device of a substation, characterized in that: include: Obtaining each initial vibration control device in the substation; Wherein, each of the initial vibration control devices comprises: an initial single tuned inertial damper, an initial tuned viscous mass damper and an initial double tuned inertial system; each component in each of the initial vibration control devices is constructed based on a tuned mass damper by introducing each inertial element; According to the H-norm optimization method, each parameter of each inertial element in each of the initial vibration control devices is optimized respectively to obtain each vibration control device.

2. The optimization method of the substation vibration control device according to claim 1, characterized in that: The initial single tuned inertial damper is constructed based on a tuned mass damper when a first inertial element is introduced; and the H-norm optimization method is used to optimize the parameters of the inertial elements in the initial vibration control devices, respectively, including: An initial single tuned inertial damper is constructed according to the first inertial element and the tuned mass damper; Optimizing various parameters of the first inertial element of the initial single tuned inertial damper according to the first dynamic amplification function, the infinite H norm and the second H norm to obtain a first inertia coefficient, a first damping coefficient and a first stiffness; The initial single tuned inertial damper is optimized according to the first inertia coefficient, the first damping coefficient and the first stiffness to obtain a single tuned inertial damper.

3. The optimization method of the substation vibration control device according to claim 1, characterized in that: The initial tuned viscous mass damper is constructed based on a tuned mass damper in the case of a second inertial element; the H-norm optimization method is used to optimize the parameters of each inertial element in each initial vibration control device, including: An initial tuned viscous mass damper is constructed according to the second inertial element and the tuned mass damper; Optimizing various parameters of the second inertial element of the initial tuned viscous mass damper according to the second dynamic amplification function, the infinite H norm and the second H norm to obtain a second inertia coefficient, a second damping coefficient and a second stiffness; The initial tuned viscous mass damper is optimized according to the second inertia coefficient, the second damping coefficient and the second stiffness to obtain a tuned viscous mass damper.

4. The optimization method of the substation vibration control device according to claim 1, characterized in that: The initial dual tuned inertial system is constructed based on a tuned mass damper in the case of a third inertial element; the H-norm optimization method is used to optimize the parameters of each inertial element in each initial vibration control device, including: An initial double tuned inertial system is constructed based on the third inertial element and the tuned mass damper; Optimizing various parameters of a third inertial element of the initial double tuned inertial system according to a third dynamic amplification function, an infinite H norm and a second H norm to obtain a third inertia coefficient, a third damping coefficient and a third stiffness; The initial dual-tuned inertial system is optimized according to the third inertia coefficient, the third damping coefficient and the third stiffness to obtain a dual-tuned inertial system.

5. The optimization method of the substation vibration control device according to claim 2, characterized in that: The optimization of various parameters of the initial single tuned inertial damper according to the first dynamic amplification function, the infinite H norm and the second H norm is specifically as follows: According to the infinite H-norm optimization method and the second H-norm optimization method, maximum values ​​and minimum values ​​of the first inertia coefficient, the first damping coefficient and the first stiffness are calculated; The infinite H norm is to determine the respective ranges of the first inertia coefficient, the first damping coefficient and the first stiffness by calculating the maximum value of the frequency response of the first dynamic amplification function, and the infinite H norm optimization calculation formula is: find opt-∞ (p) minimize D max =||D(Ω;π,θ)|| ∞ =max{D(Ω;π,θ)}. stθ min ≤θ≤θ max In the formula, θ opt-∞ (π) represents the optimal parameter determined by infinite H-norm optimization, D max represents the maximum value of the frequency response of the first dynamic amplification function, D represents the first dynamic amplification function, π is a predetermined parameter represented by a vector in the first dynamic amplification function, θ represents the first inertia coefficient, the first damping coefficient and the first stiffness, θ min represents the minimum value of the first inertia coefficient, the first damping coefficient and the first stiffness, θ max represents the maximum value of the first inertia coefficient, the first damping coefficient and the first stiffness; The second H norm is to determine the respective ranges of the first inertia coefficient, the first damping coefficient and the first stiffness by calculating the mean square value of the frequency response of the first dynamic amplification function. The calculation formula for optimizing the second H norm is: In the formula, θ opt-2 (π) represents the optimal parameter determined by the second H-norm optimization, and I represents the second H-norm of the first dynamic amplification function.

6. The optimization method of the substation vibration control device according to claim 1, characterized in that: After optimizing the components in the vibration control device according to the H-norm optimization method, the method further includes: According to each equivalent mass ratio, each optimization effect of each parameter of each inertial element is determined when each component in the vibration control device is introduced with each inertial element.

7. The optimization method of the substation vibration control device according to claim 6, characterized in that: The optimization effect of each parameter of each component in the initial single tuned inertial damper when the first inertial element is introduced according to the first equivalent mass ratio is determined as follows: determining, according to the first equivalent mass ratio, optimization effects of various parameters of the first inertial element; The first equivalent mass ratio formula is: In the formula, μ eq1 It is expressed as the first equivalent mass ratio, β1 is the first inertia ratio, μ1 is the first mass ratio, is the first position correction factor; If the value of the first equivalent mass ratio is greater than or equal to a first preset threshold, the optimization effect of each parameter of the first inertial element is determined.

8. The optimization method of the substation vibration control device according to claim 6, characterized in that: The optimization effect of each parameter of the second inertial element of each component in the tuned viscous mass damper when the second inertial element is introduced is determined according to the second equivalent mass ratio, specifically: determining, according to the second equivalent mass ratio, optimization effects of various parameters of the second inertial element; The second equivalent mass ratio formula is: In the formula, μ eq2 It is expressed as the second equivalent mass ratio, β2 is the second inertia ratio, is the second position correction factor; If the value of the second equivalent mass ratio is greater than or equal to a second preset threshold, the optimization effect of each parameter of the second inertial element is determined.

9. The optimization method of a substation vibration control device according to claim 6, characterized in that: The optimization effect of each parameter of the third inertial element on each component in the dual tuned inertial system when the third inertial element is introduced according to the third equivalent mass ratio is specifically as follows: determining, according to the third equivalent mass ratio, optimization effects of various parameters of the third inertial element; The formula of the third equivalent mass ratio is: m eq3 =am3, In the formula, μ eq3 It is expressed as the third equivalent mass ratio, α is the third mass amplification effect factor, and μ3 is the third mass ratio; If the value of the third equivalent mass ratio is greater than or equal to a third preset threshold, the optimization effect of each parameter of the third inertial element is determined.

10. An optimization device for a substation vibration control device, characterized in that: Including acquisition module and optimization module: The acquisition module is used to acquire each initial vibration control device in the substation; Wherein, each of the initial vibration control devices comprises: an initial single tuned inertial damper, an initial tuned viscous mass damper and an initial double tuned inertial system; each component in each of the initial vibration control devices is constructed based on a tuned mass damper by introducing each inertial element; The optimization module is used to optimize the parameters of the inertial elements in the initial vibration control devices according to the H-norm optimization method to obtain the vibration control devices.

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