Method and device for optimizing a substation vibration control device

Abstract

The application discloses a kind of optimization method and device of substation vibration control device.The initial vibration control device in substation is collected in the application, including initial single-tuned inertance damper, initial tuned viscous mass damper and initial double-tuned inertance system, these devices are all constructed based on traditional tuned mass damper by introducing different inertial elements.Then, the inertia element parameters in each initial device are adjusted in detail using H norm optimization method to optimize the vibration control device, solving the problem that traditional tuned mass damper cannot meet the needs of offshore environment.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of substation vibration control device optimization, and particularly relates to a substation vibration control device optimization method and device. BACKGROUND

[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, subjected to wind, waves, and currents, substations are prone to be affected by strong vibrations, which poses 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 through additional mass blocks, and are widely used in vibration control due to their simple and effective structure. However, the control effect of TMDs is excessively dependent on their additional mass, and a larger mass will cause an additional burden on the main structure of the substation. In particular, in the marine environment, existing traditional tuned mass dampers cannot meet the needs of the marine environment. SUMMARY

[0003] The present application provides a substation vibration control device optimization method and device to solve the problem that traditional tuned mass dampers cannot meet the needs of the marine environment.

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

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

[0006] The 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 the each initial vibration control device is constructed based on a tuned mass damper with the introduction of each inertial element;

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

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

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

[0010] The initial single-tuned inertia damper is constructed according to the first inertia element and the tuned mass damper;

[0011] The parameters of the first inertia element of the initial single-tuned inertia damper are optimized according to the first dynamic amplification function, the infinite H-norm and the second H-norm, to obtain the first inertia coefficient, the first damping coefficient and the first stiffness;

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

[0013] In this preferred embodiment, the application finely optimizes the parameters of the first inertia element in the initial single-tuned inertia damper by using the H-norm optimization method, especially in combination with the infinite H-norm and the second H-norm of the first dynamic amplification function. This process involves calculating the maximum value of the frequency response of the dynamic amplification function and the response mean square value 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 wideband excitation. Finally, the single-tuned inertia damper obtained in this way not only reduces the weight, but also provides more effective vibration control effect. Therefore, compared with the traditional tuned mass damper, the application realizes the lightweight and performance improvement of the device, making it more suitable for offshore substations and other environments with strict requirements for vibration control.

[0014] As a preferred embodiment of the first aspect, the initial tuned viscous mass damper is constructed based on a tuned mass damper with a second inertial element; the H-norm optimization method is used to optimize the parameters of the second inertial element in each initial vibration control device, including:

[0015] The initial tuned viscous mass damper is constructed based on the second inertial element and the tuned mass damper;

[0016] The parameters of the second inertial element of the initial tuned viscous mass damper are optimized based on the second dynamic amplification function, the infinite H-norm, and the second H-norm, to obtain a second inertial coefficient, a second damping coefficient, and a second stiffness;

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

[0018] In this preferred embodiment, the H-norm optimization method is applied to optimize the parameters of the second inertial element of the initial tuned viscous mass damper. The infinite H-norm of the second dynamic amplification function is used to determine the worst-case vibration response of the system, and the second H-norm is used to evaluate the overall vibration performance of the system under wideband random excitation. This dual-norm optimization strategy ensures effective control under extreme and sustained vibration conditions, thereby accurately calculating the second inertial coefficient, the second damping coefficient, and the second stiffness. Based on these optimal parameters, the initial tuned viscous mass damper is further optimized to obtain a tuned viscous mass damper that not only keeps the structural response within a safe range but also reduces the weight of the device and improves the operational efficiency and reliability of offshore substations in complex marine environments. Therefore, the tuned viscous mass damper provided by the present application can effectively control vibration while reducing structural burden, and is particularly suitable for application scenarios of offshore substations with strict vibration control requirements.

[0019] As a preferred embodiment of the first aspect, the initial double-tuned inertial system is constructed based on a tuned mass damper with a third inertial element; the H-norm optimization method is used to optimize the parameters of the third inertial element in each initial vibration control device, including:

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

[0021] The parameters of the third inertial element of the initial double-tuned inertial system are optimized based on the third dynamic amplification function, the infinite H-norm, and the second H-norm, to obtain a third inertial coefficient, a third damping coefficient, and a third stiffness;

[0022] According to the third inertia coefficient, the third damping coefficient and the third stiffness, the initial double-tuned inertia system is optimized to obtain a double-tuned inertia system.

[0023] In this preferred embodiment, the application optimizes the third inertia element of the initial double-tuned inertia system by using the H-norm optimization method. First, the third dynamic amplification function is combined with the infinite H-norm to identify and maximize the vibration response of the system under the worst-case scenario. Then, the second H-norm is used to measure and minimize the overall vibration energy efficiency of the system under wideband excitation. This double optimization strategy ensures excellent control effect 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 the initial double-tuned inertia system is optimized. The final double-tuned inertia system not only performs well in vibration control at multiple frequencies, but also significantly reduces the structure weight compared to traditional designs. Therefore, the application provides a double-tuned inertia system suitable for complex marine environments, which can effectively deal with multi-band vibration 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 the parameters of the initial single-tuned inertia damper according to the first dynamic amplification function, the infinite H-norm and the second H-norm is as follows:

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

[0026] The infinite H-norm is used to determine the range 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. The calculation formula of the infinite H-norm optimization is as follows:

[0027]

[0028] In the formula, θ opt-∞ represents the optimal parameters determined by the 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, and θ represents the first inertia coefficient, the first damping coefficient and the first stiffness. min represents the minimum value of the first inertia coefficient, the first damping coefficient and the first stiffness, and 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 determined by calculating the mean square value of the frequency response of the first dynamic amplification function, and the calculation formula of the second H-norm optimization is:

[0030] find θ opt-2 (π)

[0031]

[0032] s.t.θ 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 application optimizes the parameters of the initial single-tuned inertial damper by comprehensively using the infinite H-norm and the second H-norm optimization methods, 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, so as to realize the overall performance optimization of the system under wideband excitation. This dual-norm optimization strategy not only improves the accuracy and reliability of vibration control, but also realizes fine adjustment of the initial device by accurately controlling the value range of the parameters, and finally obtains a single-tuned inertial damper that provides more excellent vibration control effect while maintaining lightweight. Therefore, the 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 with strict vibration control requirements.

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

[0036] According to each equivalent mass ratio, it is determined that each component in the vibration control device has an optimal effect of each parameter of each inertia element when each inertia element is introduced.

[0037] According to the first equivalent mass ratio, it is determined that each component in the initial single-tuned inertial damper has an optimal effect of each parameter of the first inertia element when the first inertia element is introduced, and the optimal effect is specifically:

[0038] According to the first equivalent mass ratio, the optimization effect of each parameter of the first inertial element is determined.

[0039] The first equivalent mass ratio formula is:

[0040]

[0041] In the formula, μ eq1 The first equivalent mass ratio is represented as β1 is the first inertance ratio, μ1 is the first mass ratio, The first position correction factor is:

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

[0043] According to the second equivalent mass ratio, the optimization effect of each parameter of the second inertial element is determined when each component in the tuned viscous mass damper is introduced into the second inertial element, and the optimization effect of each parameter of the second inertial element is determined.

[0044] According to the second equivalent mass ratio, the optimization effect of each parameter of the second inertial element is determined.

[0045] The second equivalent mass ratio formula is:

[0046]

[0047] In the formula, μ eq2 The second equivalent mass ratio is represented as β2 is the second inertance ratio, The second position correction factor is:

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

[0049] According to the third equivalent mass ratio, the optimization effect of each parameter of the third inertial element is determined when each component in the double-tuned inertial system is introduced into the third inertial element.

[0050] According to the third equivalent mass ratio, the optimization effect of each parameter of the third inertial element is determined.

[0051] The third equivalent mass ratio formula is:

[0052] μ eq3 = αμ3,

[0053] In the formula, μ eq3 The third equivalent mass ratio is represented as 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 application can quantitatively evaluate the optimization effect of the inertial element parameters by introducing the concept of equivalent mass ratio. If the value of each equivalent mass ratio is greater than or equal to a preset threshold, it indicates that the actual mass of the inertial element is relatively small compared to the inertial effect (equivalent mass) it produces, which means that the optimized parameters enable the inertial element to produce a larger inertial force while maintaining a relatively light mass, thereby effectively controlling the 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 quantitative evaluation of the equivalent mass ratio provided by the application provides a lightweight and efficient vibration control solution for offshore substations.

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

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

[0058] The initial vibration control device comprises an initial single-tuned inertial damper, an initial tuned viscous mass damper, and an initial double-tuned inertial system. Each component in the initial vibration control device is constructed based on a tuned mass damper with the introduction of each inertial element.

[0059] The optimization module is configured to optimize each parameter of each inertial element in each initial vibration control device according to an H-norm optimization method, to obtain each vibration control device.

[0060] The device uses two modules to work better and coordinate to optimize the substation vibration control device. The application can provide diversified vibration control solutions for offshore substations by introducing different types of inertia elements and constructing corresponding initial vibration control devices. The first inertia element is used to construct an initial single-tuned inertia damper, the second inertia element is used to construct an initial tuned viscous mass damper, and the third inertia element is used to construct an initial double-tuned inertia 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 inertia elements with different characteristics. Further, the application uses the H-norm optimization method to finely adjust the inertia element parameters in these initial devices. This optimization process takes into account the dynamic response of the system, especially the worst-case response (through H∞ norm) and the overall response (through H2 norm) of the system. The application can improve the vibration control effect and realize the lightweight of the system to solve the problem that the traditional tuned mass damper cannot meet the needs of offshore environment.

[0061] As a preferred embodiment of the second aspect, the initial single-tuned inertia damper is constructed based on the tuned mass damper by introducing the first inertia element; and the H-norm optimization method is used to optimize the parameters of the inertia elements in the initial vibration control devices, including:

[0062] According to the first inertia element and the tuned mass damper, an initial single-tuned inertia damper is constructed;

[0063] According to the first dynamic amplification function, the infinite H-norm and the second H-norm, the parameters of the first inertia element of the initial single-tuned inertia damper are optimized to obtain the first inertia coefficient, the first damping coefficient and the first stiffness;

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

[0065] In this preferred embodiment, the application optimizes the parameters of the first inertia element in the initial single-tuned inertia damper by using the H-norm optimization method, particularly in combination with the infinite H-norm and the second H-norm of the first dynamic amplification function. 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 wideband excitation, and ultimately obtains a single-tuned inertia damper that provides more effective vibration control effect while reducing weight. Therefore, compared with the traditional tuned mass damper, the application realizes the lightweight and performance improvement of the device, making it more suitable for offshore substations and other environments with strict requirements for vibration control.

[0066] As a preferred embodiment of the second aspect, the initial tuned viscous mass damper is constructed based on the tuned mass damper in the case of the second inertia element; and the H-norm optimization method is used to optimize the parameters of the inertia element in each initial vibration control device, including:

[0067] According to the second inertia element and the tuned mass damper, an initial tuned viscous mass damper is constructed;

[0068] According to the second dynamic amplification function, the infinite H-norm and the second H-norm, the parameters of the second inertia element of the initial tuned viscous mass damper are optimized to obtain the second inertia coefficient, the second damping coefficient and the second stiffness;

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

[0070] In this preferred embodiment, the application optimizes the parameters of the second inertia element of the initial tuned viscous mass damper by applying the H-norm optimization method, determines the vibration response of the system in the worst case using the infinite H-norm of the second dynamic amplification function, and evaluates the overall vibration performance of the system under wideband random excitation using the second H-norm. 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, resulting in a tuned viscous mass damper that not only keeps the structural response within a safe range but also reduces the weight of the device and improves the operational efficiency and reliability of offshore substations in complex marine environments. Therefore, the application provides a tuned viscous mass damper that can effectively control vibration and reduce structural burden, which is particularly suitable for offshore substation application scenarios with strict vibration control requirements.

[0071] As a preferred embodiment of the second aspect, the initial double-tuned inertia system is constructed based on a tuned mass damper with a third inertia element; and the H-norm optimization method is used to optimize the parameters of each inertia element in each initial vibration control device, including:

[0072] An initial double-tuned inertia system is constructed based on a third inertia element and a tuned mass damper;

[0073] The parameters of the third inertia element of the initial double-tuned inertia system are optimized based on the third dynamic amplification function, the infinite H-norm, and the second H-norm, to obtain a third inertia coefficient, a third damping coefficient, and a third stiffness;

[0074] The initial double-tuned inertia system is optimized based on the third inertia coefficient, the third damping coefficient, and the third stiffness, to obtain a double-tuned inertia system.

[0075] In this preferred embodiment, the application optimizes the third inertia element of the initial double-tuned inertia system by using the H-norm optimization method. First, the third dynamic amplification function is combined with the infinite H-norm to identify and maximize the system's vibration response under the worst-case scenario. Then, the second H-norm is used to measure and minimize the system's overall vibration energy efficiency under wideband excitation. This dual optimization strategy ensures excellent control effect under extreme and continuous vibration conditions. Based on these analyses, the third inertia coefficient, third damping coefficient, and third stiffness are accurately calculated, and the initial double-tuned inertia system is optimized. The final double-tuned inertia system not only performs well in vibration control at multiple frequencies, but also significantly reduces the structure's weight compared to traditional designs. Therefore, the application provides a double-tuned inertia system suitable for complex marine environments, which can effectively deal with multi-band vibration 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 parameters of the initial single-tuned inertia damper are optimized according to the first dynamic amplification function, the infinite H-norm, and the second H-norm, specifically:

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

[0078] The infinite H-norm determines the range 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. The calculation formula of the infinite H-norm optimization is:

[0079]

[0080] where θ opt-∞ represents the optimal parameters determined by the 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, and 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 determines the range 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 of the second H-norm optimization is:

[0082] find θ opt-2 (π)

[0083]

[0084] s.t.θ 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 application optimizes the parameters of the initial single-tuned inertial damper by comprehensively using the infinite H-norm and the second H-norm optimization methods, 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, so as to realize the overall performance optimization of the system under wideband excitation. This dual-norm optimization strategy not only improves the accuracy and reliability of vibration control, but also realizes fine adjustment of the initial device by accurately controlling the value range of the parameters, and finally obtains a single-tuned inertial damper that provides more excellent vibration control effect while maintaining lightweight. Therefore, the 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 with strict vibration control requirements.

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

[0088] According to each equivalent mass ratio, it is determined that each parameter of each inertia element has an optimization effect when each component in the vibration control device introduces each inertia element.

[0089] According to the first equivalent mass ratio, it is determined that each parameter of the first inertia element has an optimization effect when each component in the initial single-tuned inertial damper introduces the first inertia element, and the determination comprises:

[0090] According to the first equivalent mass ratio, it is determined that each parameter of the first inertia element has an optimization effect;

[0091] The first equivalent mass ratio formula is:

[0092]

[0093] wherein μ eq1 is a first equivalent mass ratio, β1 is a first inertance ratio, μ1 is a first mass ratio, is a first position correction factor;

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

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

[0096] The optimization effect of each parameter of the second inertial element is determined according to the second equivalent mass ratio;

[0097] The formula of the second equivalent mass ratio is:

[0098]

[0099] wherein μ eq2 is a second equivalent mass ratio, β2 is a second inertance ratio, is a second position correction factor;

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

[0101] The third equivalent mass ratio is used to determine the optimization effect of each parameter of the third inertial element when each component in the double-tuned inertial system is introduced into the third inertial element, and the third equivalent mass ratio is specifically:

[0102] The optimization effect of each parameter of the third inertial element is determined according to the third equivalent mass ratio;

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

[0104] μ eq3 = α μ3,

[0105] wherein μ eq3 is a third equivalent mass ratio, α is a third mass amplification effect factor, and μ3 is a third mass ratio;

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

[0107] In this preferred embodiment, the application can quantitatively evaluate the effect of optimization of the parameters of the inertial element by introducing the concept of equivalent mass ratio. If the value of each equivalent mass ratio is greater than or equal to a preset threshold, it indicates that the actual mass of the inertial element is relatively small compared to the inertial effect (equivalent mass) it produces, which means that the optimized parameters enable the inertial element to produce a larger inertial force while maintaining a relatively light mass, thereby effectively controlling the 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 quantitative evaluation of the equivalent mass ratio provided by the application provides a lightweight and efficient vibration control solution for offshore substations. BRIEF DESCRIPTION OF DRAWINGS

[0108] Figure 1 : a flowchart of an embodiment of the optimization method of the substation vibration control device provided by the application;

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

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

[0111] The technical solutions in the embodiments of the application will be described clearly and completely below with reference to the drawings in the embodiments of the application. Obviously, the described embodiments are only part of the embodiments of the application, not all. Based on the embodiments in the application, all other embodiments obtained by those of ordinary skill in the art without creative labor fall within the scope of protection of the application.

[0112] Embodiment one

[0113] Please refer to Figure 1 , an optimization method of a substation vibration control device provided by an embodiment of the application.

[0114] The traditional tuned mass damper (TMD) absorbs structural vibration energy by adding a mass block, and is widely used in vibration control due to its simple and effective structure. However, the control effect of TMD depends too much on its additional mass, and a larger mass will cause additional burden to the main structure of the substation. Especially in the marine environment, reducing the weight of the structure is an important design requirement.

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

[0116] The application proposes three vibration device design schemes based on a single-tuned inertial damper (TMDI), a tuned viscous mass damper (TVMD), and a double-tuned system (RIDTMD), as shown in Figure 2 As shown in the figure, according to the requirements, the three vibration devices are respectively applicable to different offshore substation scenarios:

[0117] A. Single-tuned inertial damper (TMDI): The inertial element is combined with the traditional TMD, and the lightweight design is realized through parameter optimization. Applicable scenario: suitable for offshore small substation that needs to reduce the mass burden but also needs better vibration control effect.

[0118] B. Tuned viscous mass damper (TVMD): The inertial element completely replaces the mass block, and the parameter optimization of the inertial element is performed to achieve higher lightweight effect. Applicable scenario: suitable for offshore medium substation that has higher requirements for vibration control performance but has strict mass limitation.

[0119] C. Double-tuned inertial system (RIDTMD): A complex double-tuned network is adopted, and the inertial element is combined with the mass block, and the parameter optimization of the inertial element is performed to realize different frequency tuning, further improve the vibration control effect, and reduce the mass. Applicable scenario: suitable for complex environment that needs to cope with multiple vibration frequencies, needs to accurately control the vibration of multiple frequency bands, and requires high vibration control of large offshore substation, large offshore wind power equipment, etc.

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

[0121] S01: Obtain each initial vibration control device in the substation; wherein the 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 the each initial vibration control device is constructed based on a tuned mass damper under the condition of introducing each inertial element.

[0122] S02: According to the H-norm optimization method, optimize each parameter of each inertial element in each initial vibration control device to obtain each vibration control device.

[0123] As a preferred embodiment of embodiment one, the H-norm optimization method is used to optimize the parameters of each inertial element in each initial vibration control device, specifically:

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

[0125] ① Define design objectives and constraints;

[0126] The goal is to optimize the parameters of vibration control devices (TMDI, TVMD, RIMTMD) by introducing inertial elements, to achieve lightweight design while ensuring or improving vibration control effect.

[0127] ② Select vibration control device scheme;

[0128] According to the specific application scenario and design requirements, the most suitable type of vibration control device is selected.

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

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

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

[0132] The tuning inertance ratio of the vibration control device β

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

[0134] ④ Determine the dynamic amplification function;

[0135] Through dimensionless method, the equation of structure vibration response (system transfer function) is converted to dimensionless form:

[0136]

[0137] Among them, for TMDI, TVMD and RIDTMD, the polynomial in the transfer function will be different according to its structure form and parameters.

[0138] For single-tuned vibration control device:

[0139]

[0140] For tuned viscous mass damping vibration device:

[0141]

[0142] For the double-tuned vibration device, we have:

[0143]

[0144] where, is defined as a dimensionless mechanical impedance function for dimensionless processing of the transfer functions of the three devices:

[0145]

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

[0147]

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

[0149] 5. Optimize the parameters by H-norm;

[0150] H-norm optimization includes two parts: infinite norm optimization (H ∞ optimization) and second norm optimization (H2 optimization):

[0151] 1. The objective of H ∞ optimization is to minimize the infinite norm D max of the dynamic magnification function, find the maximum value of the corresponding frequency response, and is suitable for structures subjected to excitation of various frequencies.

[0152] findθ opt-∞ (π),

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

[0154] s. t. θ min ≤ θ ≤ θ max .

[0155] In the above equations, θopt-∞ (π) represents the optimal parameters determined by the infinite H-norm optimization, D max represents the maximum value of the frequency response of the first dynamic magnification function, D represents the first dynamic magnification function, π is a predetermined parameter represented by a vector in the first dynamic magnification function, and 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] By adjusting the parameters of the inertia element (such as the inertance ratio β, the mass ratio μ, etc.), the optimal vibration effect can be achieved.

[0157] 2. The objective of H2 optimization is to minimize the second norm I of the dynamic magnification function, which reflects the mean square value of the response of the structure in the entire frequency range, and is particularly suitable for occasions with wide-band random excitation.

[0158] findθ opt-2 (π),

[0159]

[0160] s.t.θ min ≤θ≤θ max .

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

[0162] This step determines the optimal inertia coefficient β, damping coefficient ζ d , stiffness k, and other underdetermined parameters through numerical optimization. Among them, the parameters of the vibration control device are represented by predetermined parameters represented by π and underdetermined parameters represented by θ, respectively. θ opt-∞ (π) and θ opt-2 (π) represent the optimal underdetermined parameters determined by the norm optimization; θ min , θ max represent the lower and upper boundaries of the parameter vector.

[0163] In this preferred embodiment, the application optimizes the parameters of the initial single-tuned inertial damper by comprehensively using the infinite H-norm and the second H-norm optimization methods, 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, so as to realize the overall performance optimization of the system under wideband excitation. This dual-norm optimization strategy not only improves the accuracy and reliability of vibration control, but also realizes fine adjustment of the initial device by accurately controlling the value range of the parameters, and finally obtains a single-tuned inertial damper that maintains lightweight while providing more excellent vibration control effect. Therefore, the 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 with strict vibration control requirements.

[0164] As a preferred embodiment of Embodiment One, the initial single-tuned inertial damper is constructed based on a tuned mass damper with the introduction of a first inertia element; and the parameters of each inertia element in each initial vibration control device are optimized according to the H-norm optimization method, including:

[0165] The initial single-tuned inertial damper is constructed based on the first inertia element and the tuned mass damper;

[0166] The parameters of the first inertia element of the initial single-tuned inertial damper are optimized according to the first dynamic amplification function, the infinite H-norm and the second H-norm, to obtain the first inertia coefficient, the first damping coefficient and the 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 application optimizes the parameters of the first inertia element in the initial single-tuned inertia damper by using the H-norm optimization method, especially in combination with the infinite H-norm and the second H-norm of the first dynamic amplification function. 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 considers the overall performance of the system under wideband excitation, and finally obtains a single-tuned inertia damper that provides more effective vibration control effect while reducing weight. Therefore, compared with the traditional tuned mass damper, the application realizes the lightweight and performance improvement of the device, making it more suitable for offshore substations and other environments with strict requirements for vibration control.

[0169] As a preferred embodiment of embodiment one, the initial tuned viscous mass damper is constructed based on the tuned mass damper in the case of the second inertia element; and the H-norm optimization method is used to optimize the parameters of the inertia element in each initial vibration control device, including:

[0170] According to the second inertia element and the tuned mass damper, an initial tuned viscous mass damper is constructed;

[0171] According to the second dynamic amplification function, the infinite H-norm and the second H-norm, the parameters of the second inertia element of the initial tuned viscous mass damper are optimized to obtain the second inertia coefficient, the second damping coefficient and the second stiffness;

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

[0173] In this preferred embodiment, the application optimizes the parameters of the second inertia element of the initial tuned viscous mass damper by applying the H-norm optimization method, determines the vibration response of the system under the worst-case scenario using the infinite H-norm of the second dynamic amplification function, and evaluates the overall vibration performance of the system under wideband random excitation using the second H-norm. This dual-norm optimization strategy ensures effective control under extreme and sustained 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, resulting in a tuned viscous mass damper that not only keeps the structural response within a safe range but also reduces the weight of the device and improves the operational efficiency and reliability of offshore substations in complex marine environments. Therefore, the application provides a tuned viscous mass damper that can effectively control vibration and reduce structural burden, which is particularly suitable for offshore substation application scenarios with strict vibration control requirements.

[0174] As a preferred embodiment of Embodiment One, the initial double-tuned inertia system is constructed based on a tuned mass damper with a third inertia element; and the H-norm optimization method is used to optimize the parameters of each inertia element in each initial vibration control device, including:

[0175] An initial double-tuned inertia system is constructed based on a third inertia element and a tuned mass damper;

[0176] The parameters of the third inertia element of the initial double-tuned inertia system are optimized based on the third dynamic amplification function, the infinite H-norm, and the second H-norm, resulting in a third inertia coefficient, a third damping coefficient, and a third stiffness;

[0177] The initial double-tuned inertia system is optimized based on the third inertia coefficient, the third damping coefficient, and the third stiffness, resulting in a double-tuned inertia system.

[0178] In this preferred embodiment, the application uses the H-norm optimization method to finely adjust the parameters of the third inertial element of the initial double-tuned inertial system. First, the third dynamic amplification function is combined with the infinite H-norm to identify and maximize the system's vibration response under the worst-case scenario. Then, the second H-norm is used to measure and minimize the overall vibration energy efficiency of the system under wideband excitation. This dual optimization strategy ensures excellent control effect under extreme and continuous vibration conditions. Based on these analyses, the third inertia coefficient, third damping coefficient, and third stiffness are accurately calculated, and the initial double-tuned inertial system is optimized. The final double-tuned inertial system not only performs well in vibration control at multiple frequencies, but also significantly reduces the structure weight compared to traditional designs. Therefore, the application provides a double-tuned inertial system suitable for complex marine environments, which can effectively deal with multi-band vibration and is more lightweight, greatly improving the long-term operation safety and reliability of offshore substations.

[0179] As a preferred embodiment of Embodiment One, after optimizing each component in the vibration control device according to the H-norm optimization method, the method further comprises:

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

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

[0182] According to the first equivalent mass ratio, the optimization effect of each parameter of the first inertial element is determined;

[0183] Equivalent mass of single-tuned vibration control device μ eq is represented as: The applicable range of equivalent mass is: Outside this range, the use of inertial elements cannot effectively improve the vibration control performance.

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

[0185] According to the second equivalent mass ratio, the optimization effect of each parameter of the second inertial element is determined;

[0186] Equivalent mass of tuned viscous mass damper vibration control device μ eq is represented as: The applicable range of the equivalent mass is determined according to the requirements of the object, and the control vibration control effect has different threshold values ∈ for different requirements. Only when μ eq > ∈ is satisfied, the vibration control effect can be achieved.

[0187] Further, according to the third equivalent mass ratio, the optimization effect of each parameter of the third inertial element when the third inertial element is introduced into the double-tuned inertial system is determined, and the third equivalent mass ratio is specifically:

[0188] According to the third equivalent mass ratio, the optimization effect of each parameter of the third inertial element is determined.

[0189] The equivalent mass μ of the double-tuned vibration control device eq is represented as: μ eq = αμ, where α is a mass amplification effect factor. The coefficient α will be determined by equating the optimal H2 norm of the double-tuned vibration control device to the optimal H2 norm of the conventional TMD, represented as I opt ,

[0190]

[0191] The applicable range of the equivalent mass is: and β1 and β2 are the inerter ratios in the two frequency ranges, respectively, and are the correction factors in the two frequency ranges, respectively, and μ1 and μ1 are the mass ratios in the two frequency ranges, respectively.

[0192] In this preferred embodiment, the application can quantitatively evaluate the optimization effect of the parameters of the inertial element 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 value, it indicates that the actual mass of the inertial element is relatively small compared to the inertial effect (equivalent mass) it produces, which means that the optimized parameters enable the inertial element to produce a larger inertial force while maintaining a relatively light mass, thereby effectively controlling the 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 quantitative evaluation of the equivalent mass ratio provides a lightweight and efficient vibration control solution for offshore substations.

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

[0194] Embodiment two

[0195] Please refer to Figure 3 , an optimization device of a substation vibration control device provided by the application embodiment.

[0196] The traditional tuned mass damper (TMD) absorbs structural vibration energy by adding a mass block, and is widely used in vibration control due to its simple and effective structure. However, the control effect of TMD depends too much on its additional mass, and a larger mass will cause additional burden to the main structure of the substation. Especially in the offshore environment, reducing the weight of the structure is an important design requirement.

[0197] The application optimizes and upgrades the traditional TMD by introducing inertia elements. Inertia element is a mechanical element that can output force proportional to relative acceleration, and its effect is equivalent to that of a large mass block in TMD, but the actual mass is much smaller than the simulated mass block.

[0198] The application proposes three vibration device design schemes based on single-tuned inertia damper (TMDI), tuned viscous mass damper (TVMD), and double-tuned system (RIDTMD), as shown in Figure 2 According to the requirements, the three kinds of vibration devices are respectively applicable to different offshore substation scenes:

[0199] A. Single-tuned inertia damper (TMDI): combining inertia elements with traditional TMD, and realizing lightweight design through parameter optimization. Applicable scene: suitable for small offshore substations near the sea that need to reduce mass burden but also need good vibration control effect.

[0200] B. Tuned viscous mass damper (TVMD): The inertia element is completely replaced by the mass block, and the inertia element is optimized in parameters to achieve higher lightweight effect. Applicable scenario: suitable for offshore medium-sized substations with high requirements for vibration control performance but strict mass limitation.

[0201] C. Double-tuned inertia system (RIDTMD): A complex double-tuned network is adopted, and the inertia element is combined with the mass block, and the inertia element is optimized in parameters, so as to realize different frequency tuning, further improve the vibration control effect, and reduce the mass. Applicable scenario: suitable for complex environments that need to cope with multiple vibration frequencies, and need to accurately control the vibration of multiple frequency bands, and require high vibration control of large offshore substations, large offshore wind power equipment, etc.

[0202] In the 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 configured to acquire each initial vibration control device in the substation; wherein the each initial vibration control device includes an initial single-tuned inertia damper, an initial tuned viscous mass damper, and an initial double-tuned inertia system; each component in the each initial vibration control device is constructed based on a tuned mass damper with the introduction of each inertia element.

[0204] The optimization module 20 is configured to optimize each parameter of each inertia element in the each initial vibration control device according to an H-norm optimization method, to obtain each vibration control device.

[0205] As a preferred embodiment of the second embodiment, the H-norm optimization method is used to optimize each parameter of each inertia element in the each initial vibration control device, specifically as follows:

[0206] The optimal parameters of various inertia element-based vibration control devices, 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] ① Define the design target and constraints;

[0208] The target is to optimize the parameters of the vibration control device (TMDI, TVMD, RIMTMD) by introducing the inertia element, so as to ensure or improve the vibration control effect while achieving lightweight design.

[0209] ② Select the vibration control device scheme;

[0210] According to the specific application scenario and design requirements, the most suitable type of vibration control device is selected.

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

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

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

[0214] Tuned compliance ratio of the vibration control device β;

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

[0216] ④ Determine the dynamic amplification function;

[0217] By the method of non-dimensionalization, the equation of structural vibration response (system transfer function) is converted into a non-dimensional form:

[0218]

[0219] Among them, for the three devices of TMDI, TVMD and RIDTMD, the polynomial in the transfer function will be different according to its structure form and parameters.

[0220] For single-tuned vibration control devices:

[0221]

[0222] For tuned viscous mass damping vibration devices:

[0223]

[0224] For double-tuned vibration devices:

[0225]

[0226] Among them, is defined as the non-dimensional mechanical impedance function, which is used for non-dimensional processing of the transfer functions of the three devices:

[0227]

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

[0229]

[0230] In the above formula, the non-dimensional excitation frequency is defined as ω is the system frequency; ω n is the natural frequency of the substation main structure; is the position correction factor; ζ n is the primary offshore substation structural damping ratio; μ is the tuned mass ratio of the vibration control device; β is the tuned inertance ratio of the vibration control device; v is the tuned frequency ratio of the vibration control device; γ is the secondary tuned frequency ratio; ζ d is the nominal damping ratio of the vibration control device; λ is the dimensionless complex frequency; C3, C4, C6 are the types of the double-tuned vibration device.

[0231] ⑤Optimizing the parameters by H-norm;

[0232] The H-norm optimization includes two parts: infinite-norm optimization (H ∞ optimization) and second-norm optimization (H2 optimization):

[0233] 1. H ∞ optimization aims to minimize the infinite-norm D max of the dynamic amplification function, find the maximum value of the corresponding frequency response, and is suitable for structures subjected to excitations of various frequencies.

[0234] findθ opt-∞ (π),

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

[0236] s. t. θ min ≤ θ ≤ θ max .

[0237] By adjusting the parameters of the inertial element (such as inertance ratio β, mass ratio μ, etc.), the best vibration effect can be achieved.

[0238] 2. H2 optimization aims to minimize the second-norm I of the dynamic amplification function, which reflects the mean square value of the structure's response in the entire frequency range, and is particularly suitable for situations with wide-band random excitations.

[0239] findθ opt-2 (π),

[0240]

[0241] s.t. θ min ≤ θ ≤ θ max .

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

[0243] This step determines the optimal inertia coefficient β, damping coefficient ζ d , stiffness k, etc. underdetermined parameters by numerical optimization. Among them, the parameters of the vibration control device are represented as predetermined parameters represented by π as a vector and underdetermined parameters represented by θ as a vector. θ opt-∞ (π) and θ opt-2 (π) represent the optimal underdetermined parameters determined by norm optimization; θ min , θ max represent the lower and upper boundaries 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 methods, which 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 overall performance optimization of the system under wideband excitation. This dual-norm optimization strategy not only improves the accuracy and reliability of vibration control, but also realizes fine adjustment of the initial device by accurately controlling the value range of the parameters, and ultimately obtains a single-tuned inertial damper that maintains lightweight while providing more excellent vibration control effect. Therefore, the present application provides a vibration control device that can not only cope with extreme vibration situations, but also ensure excellent overall performance, which is particularly suitable for application scenarios such as offshore substations that have strict requirements for vibration control.

[0245] As a preferred embodiment of Embodiment Two, the initial single-tuned inertial damper is constructed based on a tuned mass damper with the introduction of a first inertia element; and the parameters of each inertia element in each initial vibration control device are optimized according to the H-norm optimization method, including:

[0246] The initial single-tuned inertial damper is constructed based on the first inertia element and the tuned mass damper;

[0247] The parameters of the first inertia element of the initial single-tuned inertial damper are optimized according to the first dynamic amplification function, the infinite H-norm and the second H-norm, to obtain the first inertia coefficient, the first damping coefficient and the 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 application optimizes the parameters of the first inertia element in the initial single-tuned inertia damper by using the H-norm optimization method, especially in combination with the infinite H-norm and the second H-norm of the first dynamic amplification function. 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 considers the overall performance of the system under wideband excitation, and finally obtains a single-tuned inertia damper that provides more effective vibration control effect while reducing weight. Therefore, compared with the traditional tuned mass damper, the application realizes the lightweight and performance improvement of the device, making it more suitable for offshore substations and other environments with strict requirements for vibration control.

[0250] As a preferred embodiment of Embodiment Two, the initial tuned viscous mass damper is constructed based on a tuned mass damper with a second inertia element; and the H-norm optimization method is used to optimize the parameters of the inertia element in each initial vibration control device, including:

[0251] According to the second inertia element and the tuned mass damper, an initial tuned viscous mass damper is constructed;

[0252] According to the second dynamic amplification function, the infinite H-norm and the second H-norm, the parameters of the second inertia element of the initial tuned viscous mass damper are optimized to obtain a second inertia coefficient, a second damping coefficient and a second stiffness;

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

[0254] In this preferred embodiment, the application optimizes the parameters of the second inertia element of the initial tuned viscous mass damper by applying the H-norm optimization method, determines the vibration response of the system under the worst-case scenario using the infinite H-norm of the second dynamic amplification function, and evaluates the overall vibration performance of the system under wideband random excitation using the second H-norm. This dual-norm optimization strategy ensures effective control under extreme and sustained 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, resulting in a tuned viscous mass damper that not only keeps the structural response within a safe range but also reduces the weight of the device and improves the operational efficiency and reliability of offshore substations in complex marine environments. Therefore, the application provides a tuned viscous mass damper that can effectively control vibration and reduce structural burden, which is particularly suitable for offshore substation application scenarios with strict vibration control requirements.

[0255] As a preferred embodiment of Embodiment Two, the initial double-tuned inertia system is constructed based on a tuned mass damper with a third inertia element; and the H-norm optimization method is used to optimize the parameters of each inertia element in each initial vibration control device, including:

[0256] An initial double-tuned inertia system is constructed based on a third inertia element and a tuned mass damper;

[0257] The parameters of the third inertia element of the initial double-tuned inertia system are optimized based on the third dynamic amplification function, the infinite H-norm, and the second H-norm, resulting in a third inertia coefficient, a third damping coefficient, and a third stiffness;

[0258] The initial double-tuned inertia system is optimized based on the third inertia coefficient, the third damping coefficient, and the third stiffness, resulting in a double-tuned inertia 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. 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 at 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 of 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 various parameters of the first inertial element when the first inertial element is introduced into various components of the initial single tuned inertial damper according to the first equivalent mass ratio is determined 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 Expressed as: The scope of application of equivalent mass is: Outside this range, the use of inertial elements cannot effectively improve vibration control performance.

[0265] Furthermore, the optimization effect of various parameters of the second inertia element when the second inertia element is introduced into various components of the tuned viscous mass damper is determined based on the second equivalent mass ratio, specifically:

[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 Expressed as: The applicable range of the equivalent mass is determined according to the requirements of the object, and the control vibration control effect has different threshold values ε for different requirements. Only when μ eq >∈ is satisfied, the optimization effect of the parameters of the third inertia element can be achieved.

[0268] Further, according to the third equivalent mass ratio, the optimization effect of the parameters of the third inertia element in the double-tuned inertia system is determined, and the specific optimization effect is:

[0269] According to the third equivalent mass ratio, the optimization effect of the parameters of the third inertia element is determined.

[0270] The equivalent mass μ of the double-tuned vibration control device eq is represented as: μ eq = αμ, where α is a mass amplification effect factor. The coefficient α will be determined by equating the optimal H2 norm of the double-tuned vibration control device to the optimal H2 norm of the conventional TMD, represented as I opt ,

[0271]

[0272] The applicable range of the equivalent mass is: and β1 and β2 are the inerter ratios in the two frequency ranges, respectively, and are the correction factors in the two frequency ranges, respectively, and μ1 and μ1 are the mass ratios in the two frequency ranges, respectively.

[0273] In this preferred embodiment, the application can quantitatively evaluate the optimization effect of the parameters of the inertia element 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 value, it indicates that the actual mass of the inertia element is relatively small compared to the inertia effect (equivalent mass) it produces, which means that the optimized parameters enable the inertia element to produce a larger inertia force while maintaining a relatively light mass, thereby effectively controlling the 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 quantitative evaluation of the equivalent mass ratio provides a lightweight and efficient vibration control solution for offshore substations.

[0274] The device uses two modules to work better and coordinate to optimize the substation vibration control device. The application can provide diversified vibration control solutions for offshore substations by introducing different types of inertia elements and constructing corresponding initial vibration control devices. The first inertia element is used to construct an initial single-tuned inertia damper, the second inertia element is used to construct an initial tuned viscous mass damper, and the third inertia element is used to construct an initial double-tuned inertia 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 inertia elements with different characteristics. Further, the application uses the H-norm optimization method to finely adjust the inertia element parameters in these initial devices. This optimization process takes into account the dynamic response of the system, especially the worst-case response (through H∞ norm) and the overall response (through H2 norm) of the system. The application can improve the vibration control effect and realize the lightweight of the system to solve the problem that the traditional tuned mass damper cannot meet the needs of the offshore environment.

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

Claims

1. A method of optimizing a substation vibration control device, characterized by, The method comprises the following steps: obtaining each initial vibration control device in a transformer substation; wherein each initial vibration control device comprises an initial single-tuned inertance damper, an initial tuned viscous mass damper, and an initial double-tuned inertance system; each component in each initial vibration control device is constructed based on a tuned mass damper with each inertance element introduced; optimizing each parameter of each inertance element in each initial vibration control device according to an H-norm optimization method, to obtain each vibration control device; determining the optimization effect of each parameter of each inertance element in each initial vibration control device according to each equivalent mass ratio; the first equivalent mass ratio formula is: wherein μ eq1 is the first equivalent mass ratio, β1 is the first inertance ratio, μ1 is the first mass ratio, is the first position correction factor; the second equivalent mass ratio formula is: wherein μ eq2 is expressed as a second equivalent mass ratio, β2 is a second inertance ratio, is a second position correction factor; the third equivalent mass ratio formula is: μ eq3 = aμ3, wherein μ eq3 is the third equivalent mass ratio, a is the third mass amplification factor, and μ3is the third mass ratio.

2. The optimization method of substation vibration control apparatus according to claim 1, characterized by, the initial single-tuned inertance damper is constructed based on a tuned mass damper with a first inertance element introduced; the optimization of each parameter of each inertance element in each initial vibration control device according to the H-norm optimization method comprises: constructing an initial single-tuned inertance damper according to the first inertance element and the tuned mass damper; optimizing each parameter of the first inertance element of the initial single-tuned inertance damper according to a first dynamic amplification function, an infinite H-norm, and a second H-norm, to obtain a first inertance coefficient, a first damping coefficient, and a first stiffness; optimizing the initial single-tuned inertance damper according to the first inertance coefficient, the first damping coefficient, and the first stiffness, to obtain a single-tuned inertance damper.

3. The substation vibration control device optimization method of claim 1, wherein, the initial tuned viscous mass damper is constructed based on a tuned mass damper with a second inertance element introduced; the optimization of each parameter of each inertance element in each initial vibration control device according to the H-norm optimization method comprises: constructing an initial tuned viscous mass damper according to the second inertance element and the tuned mass damper; optimizing each parameter of the second inertance element of the initial tuned viscous mass damper according to a second dynamic amplification function, an infinite H-norm, and a second H-norm, to obtain a second inertance coefficient, a second damping coefficient, and a second stiffness; optimizing the initial tuned viscous mass damper according to the second inertance coefficient, the second damping coefficient, and the second stiffness, to obtain a tuned viscous mass damper.

4. The substation vibration control device optimization method of claim 1, wherein, the initial double-tuned inertance system is constructed based on a tuned mass damper with a third inertance element introduced; the optimization of each parameter of each inertance element in each initial vibration control device according to the H-norm optimization method comprises: constructing an initial double-tuned inertance system according to the third inertance element and the tuned mass damper; optimizing each parameter of the third inertance element of the initial double-tuned inertance system according to a third dynamic amplification function, an infinite H-norm, and a second H-norm, to obtain a third inertance coefficient, a third damping coefficient, and a third stiffness; optimizing the initial double-tuned inertance system according to the third inertance coefficient, the third damping coefficient, and the third stiffness, to obtain a double-tuned inertance system.

5. The substation vibration control device optimization method of claim 2, wherein, The parameters of the initial single-tuned inertance damper are optimized according to the first dynamic amplification function, the infinite H-norm and the second H-norm, and the parameters are specifically as follows: The first inertance coefficient, the first damping coefficient and the first stiffness are calculated according to the infinite H-norm optimization method and the second H-norm optimization method, and each maximum value and each minimum value of the first inertance coefficient, the first damping coefficient and the first stiffness are obtained. The infinite H-norm is used to determine the range of the first inertance 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 calculation formula of the infinite H-norm optimization is as follows: findθ opt-∞ (π) minimize D max = ||D(Ω; π, θ) || ∞ = max{D(Ω; π, θ)}. s.t. θ min ≤ θ ≤ θ max where θ opt-∞ (π) denotes an optimal parameter determined by an infinite H norm optimization, D max denotes a maximum value of a frequency response of the first dynamic amplification function, D denotes a first dynamic amplification function, π is a predetermined parameter expressed in a vector in the first dynamic amplification function, β denotes a first inertia coefficient, a first damping coefficient, and a first stiffness, θ min denotes a minimum value of the first inertia coefficient, the first damping coefficient, and the first stiffness, θ max denotes a maximum value of the first inertia coefficient, the first damping coefficient, and the first stiffness; The second H-norm is used to determine the range of the first inertance 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, and the calculation formula of the second H-norm optimization is as follows: findθ opt-2 (π) s.t. θ min ≤ θ ≤ θ max where θ opt-2 (π) denotes the optimal parameter determined by the second H-norm optimization, I denotes the second H-norm of the first dynamic amplification function.

6. The substation vibration control device optimization method of claim 1, wherein, According to the first equivalent mass ratio, the optimization effect of the parameters of the first inertance element is determined when each component in the initial single-tuned inertance damper is introduced into the first inertance element, and the parameters are specifically as follows: According to the first equivalent mass ratio, the optimization effect of the parameters of the first inertance element is determined. If the value of the first equivalent mass ratio is greater than or equal to the first preset threshold, the optimization effect of the parameters of the first inertance element is determined.

7. The substation vibration control device optimization method of claim 1, wherein, According to the second equivalent mass ratio, the optimization effect of the parameters of the second inertance element is determined when each component in the tuned viscous mass damper is introduced into the second inertance element, and the parameters are specifically as follows: According to the second equivalent mass ratio, the optimization effect of the parameters of the second inertance element is determined. If the value of the second equivalent mass ratio is greater than or equal to the second preset threshold, the optimization effect of the parameters of the second inertance element is determined.

8. The substation vibration control device optimization method of claim 1, wherein, According to the third equivalent mass ratio, the optimization effect of the parameters of the third inertance element is determined when each component in the double-tuned inertance system is introduced into the third inertance element, and the parameters are specifically as follows: According to the third equivalent mass ratio, the optimization effect of the parameters of the third inertance element is determined. If the value of the third equivalent mass ratio is greater than or equal to the third preset threshold, the optimization effect of the parameters of the third inertance element is determined.

9. An optimization device of a substation vibration control device, characterized by, The method comprises the following steps: The acquisition module is used to acquire each initial vibration control device in the transformer substation. The initial vibration control device comprises an initial single-tuned inertance damper, an initial tuned viscous mass damper and an initial double-tuned inertance system, and each component in the initial vibration control device is constructed based on a tuned mass damper under the condition that each inertance element is introduced. The optimization module is used to optimize the parameters of each inertance element in each initial vibration control device according to the H-norm optimization method, and each vibration control device is obtained. According to each equivalent mass ratio, the optimization effect of the parameters of each inertance element is determined when each component in the vibration control device is introduced into each inertance element. The first equivalent mass ratio formula is as follows: wherein μ eq1 is the first equivalent mass ratio, β1is the first inertance ratio, μ1is the first mass ratio, is the first position correction factor; The second equivalent mass ratio formula is as follows: wherein μ eq2 is the second equivalent mass ratio, θ2 is the second inertance ratio, is the second position correction factor; The third equivalent mass ratio formula is as follows: μ eq3 = αμ3, wherein μ eq3 is the third equivalent mass ratio, a is the third mass amplification factor, and μ3is the third mass ratio.

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