CN115059731B - Spring pendulum type collision tuned mass damper applied to fan and design method - Google Patents

Spring pendulum type collision tuned mass damper applied to fan and design method Download PDF

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CN115059731B
CN115059731B CN202210545741.2A CN202210545741A CN115059731B CN 115059731 B CN115059731 B CN 115059731B CN 202210545741 A CN202210545741 A CN 202210545741A CN 115059731 B CN115059731 B CN 115059731B
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damper
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spring
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CN115059731A (en
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徐军
刘鑫祺
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Hunan University
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
    • F16F15/06—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/022—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using dampers and springs in combination
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
    • F16F15/0232—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means with at least one gas spring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
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Abstract

The invention discloses a spring pendulum type collision tuned mass damper applied to a fan and a design method thereof. The invention has the advantages of good vibration damping (vibration) performance, good robustness and the like.

Description

Spring pendulum type collision tuned mass damper applied to fan and design method
Technical Field
The invention mainly relates to the technical field of wind power, in particular to a spring pendulum type collision tuned mass damper applied to a fan and a design method.
Background
In recent years, wind energy has come to be widely used with increasing awareness of energy demand and environmental protection. Compared with a land fan, the offshore wind driven generator has the advantages of small pollution, short construction period, low operation cost and the like.
As the scale of the offshore wind turbine structure increases, the requirements on the safety of the structure become higher. The offshore wind turbine is required to bear not only the pneumatic load under the action of pulsating wind, but also the load generated under the action of sea waves, ocean currents, sea ice, even earthquakes and the like. Due to adverse environmental conditions at sea, offshore wind turbines can generate large vibrations during operation, and instruments in wind turbines are often sensitive to acceleration, so that severe vibrations are very likely to cause equipment failure and damage; further, the long-term exposure to large vibrations may lead to fatigue failure. Therefore, the method has important significance for the vibration control research of the offshore wind turbine structure.
The input cost of the wind turbine generator can be greatly improved by means of improving the strength and the rigidity of the fan to resist external loads. For vibration control, there are three basic control strategies: passive, semi-active and active. Which is widely used because of its simple passive form and no need for energy input. However, the conventional passive Damper has many disadvantages, for example, a Tuned Mass Damper (TMD) is taken as an example, firstly, the conventional TMD vibrator has large displacement, but the cabin space is limited; secondly, under the condition of frequency detuning, the damping effect of TMD is greatly weakened, even the control capability is lost, and the robustness is poor.
Disclosure of Invention
The technical problem to be solved by the invention is as follows: aiming at the technical problems in the prior art, the invention provides a spring pendulum type collision tuned mass damper which has good vibration (shock) damping performance and good robustness and is applied to a fan and a design method thereof.
In order to solve the technical problems, the technical scheme provided by the invention is as follows:
the top end of the spring is fastened on an offshore wind turbine, the bottom end of the spring is connected with the mass block, the viscous damper is installed below the mass block, stoppers are installed on two sides of the mass block, and a viscoelastic layer is arranged on one side, in contact with the mass block, of each stopper.
Preferably, the stopper is a stopper plate.
Preferably, the viscoelastic layer is VHB rubber or HEDR rubber.
The invention also discloses a design method of the spring pendulum type collision tuned mass damper applied to the fan, which comprises the following steps:
1) Establishing a single-pile offshore wind turbine tower frame and a single-pile integral simplified model, and analyzing and processing to obtain a normalized first-order vibration type polynomial expression;
2) Establishing an integral dynamic model of the single-pile type offshore wind turbine and the spring pendulum type collision tuned mass damper based on an Euler-Lagrange equation;
3) Generating a stable random pulsating wind field and an irregular wave field based on a spectral expression method;
4) Under the combined action of a stable random pulsating wind field and an irregular wave field, performing parameter optimization on the spring pendulum type collision tuned mass damper by taking the standard deviation of the fan steady-state time-course response as a target to obtain the optimal frequency ratio and the optimal damping ratio of the spring pendulum type collision tuned mass damper;
5) For given collision rigidity and recovery coefficient, adjusting collision parameters to improve control effect; and carrying out robustness analysis on the spring pendulum type collision tuned mass damper under different collision intervals, analyzing the control effect of the spring pendulum type collision tuned mass damper when the frequency is detuned, and obtaining the parameters of the spring pendulum type collision tuned mass damper when the spring pendulum type collision tuned mass damper is applied to the offshore wind turbine.
Preferably, the specific process of step 2) is:
the Euler-Lagrange equation is:
Figure BDA0003652542090000021
wherein T is kinetic energy, V is potential energy, q is the degree of freedom of the fan and the damper,
Figure BDA0003652542090000022
representing the velocity of each degree of freedom;
the overall dynamics model equation is obtained through derivation:
Figure BDA0003652542090000031
wherein M, C, K respectively represent mass, rigidity, damping matrix, Q wind 、Q wave Respectively the wind load and wave load to which the system is subjected, F being the force generated by the damper.
Preferably, in step 3), the stable random pulsating wind field adopts an IEC Kaimal spectral model, and generates a wind load by applying a phyllo-momentum theory, and an autocorrelation power spectral function of the wind load is written as:
Figure BDA0003652542090000032
where f denotes the frequency in Hz, σ u As a standard deviation, the expression can be written as σ u ＝TI·U 0 TI is turbulence intensity, U 0 Is the average wind speed, L u Is an integral scale parameter, wherein L u ＝8.10Δ u ，Δ u Is a turbulence scale parameter.
Preferably, in step 3), the irregular wave field adopts a Jonswap spectrum, and the wave force is calculated based on a small amplitude wave theory and a morrison equation, and the spectrum model function of the irregular wave field is expressed as:
Figure BDA0003652542090000033
wherein H s And T p Respectively, the prominent wave height and the peak period, f p ＝1/T p Is the peak frequency, when f is less than or equal to f p When σ =0.07, when f > f p When, σ =0.09; γ represents a peak shape coefficient.
Preferably, in step 5), the collision parameters include a collision interval and a frequency ratio.
Preferably, the frequency ratio is less than or equal to 0.9, and the collision interval is less than or equal to 0.1m.
Preferably, after the step 5), a step 6) is further included, under the stop working condition, the earthquake load is introduced, and according to the parameters obtained in the step 5), multiple working conditions are selected to be compared with the traditional damper TMD, so that the reasonability of the damper and the parameter setting is verified.
Compared with the prior art, the invention has the advantages that:
compared with the traditional passive damper, the spring pendulum type collision tuned mass damper has the characteristics of small oscillator displacement, more damping and energy consumption mechanisms, excellent robustness and the like; the spring pendulum type collision tuned mass damper has two nonlinear mechanisms of collision and spring pendulum, is provided with a viscous damper element, greatly enhances the vibration (shock) energy consumption capacity, has better robustness than the conventional mass tuned damper, and has better vibration (shock) damping performance in a low-frequency region when the frequency imbalance is large, so that the offshore wind turbine has good vibration (shock) damping effect under the actions of wind, waves and earthquakes.
Drawings
FIG. 1 is a schematic view of a model of a controlled offshore wind turbine configuration according to the present invention.
Fig. 2 is a schematic diagram of SPPTMD structure according to the present invention.
FIG. 3 is a diagram of SPPTMD parameter optimization in the present invention.
FIG. 4 is a comparison graph of SPPTMD and TMD robustness analysis in the present invention.
FIG. 5 is a comparative verification diagram of the shutdown condition of the present invention.
FIG. 6 is a flow chart of a method of the present invention in an embodiment.
Illustration of the drawings: 1. a spring; 2. a mass block; 3. a viscous damper; 4. a stopper; 5. a viscoelastic layer; 6. and (4) connecting the blocks.
Detailed Description
The invention is further described below with reference to the figures and the specific embodiments of the description.
As shown in fig. 1 and 2, the Spring Pendulum type impact Tuned Mass Damper (SPPTMD) applied to an offshore wind turbine according to an embodiment of the present invention includes a Spring 1, a Mass block 2, and a viscous Damper 3, wherein a top end of the Spring 1 is fastened on a connecting block 6 of the offshore wind turbine, a bottom end of the Spring 1 is connected with the Mass block 2, the viscous Damper 3 is installed below the Mass block 2, both sides of the Mass block 2 are installed with stoppers 4, and a viscoelastic layer 5 is disposed on a side of the stopper 4 contacting the Mass block 2. Compared with the traditional passive damper, the spring pendulum type collision tuned mass damper has the characteristics of small vibrator displacement, more vibration damping and energy consumption mechanisms, excellent robustness and the like; the spring pendulum type collision tuned mass damper has two nonlinear mechanisms of collision and spring pendulum, is provided with the viscous damper 3 element, greatly enhances the vibration (shock) energy consumption capacity, has better robustness than the conventional mass tuned damper, and has better vibration (shock) damping performance in a low-frequency region when the frequency imbalance is large, so that the offshore wind turbine has good vibration (shock) damping effect under the actions of wind, wave and earthquake. The pneumatic damping in the average wind direction of the offshore wind turbine is large, so that the response can be well controlled; and lateral pneumatic damping is small, and vibration is large, so that the damper is arranged only in the lateral direction of the fan to control the lateral vibration of the offshore fan.
In a specific embodiment, the viscous damper 3 is composed of a connecting body, an end cover, a damping medium, a cylinder body, a piston and the like, wherein the connecting body is hinged with the mass block 2, when the mass block 2 moves, friction is generated between damping medium molecules and between the piston and the damping medium, the medium generates huge damping when passing through a piston hole, the resultant force generated by the actions is damping force, and the kinetic energy of vibration (shock) can be converted into heat to be dissipated.
In one embodiment, the viscoelastic material is Very High Bond (VHB Rubber) or High Energy Dissipation Rubber (HEDR Rubber).
As shown in fig. 6, an embodiment of the present invention further discloses a design method of the spring pendulum type impact tuned mass damper applied to the offshore wind turbine, which specifically includes the steps of:
1) Establishing an NREL 5MW single-pile offshore wind turbine tower and single-pile integral simplified model by using Abaqus software, performing linear perturbation frequency analysis, taking a first-order mode of the tower and the single-pile integral, introducing Matlab for processing, and fitting into a normalized first-order mode polynomial expression; the first-order vibration mode can be understood as the vibration shape of the whole tower and the pile foundation in a first mode;
2) Establishing an integral dynamic model of the NREL 5MW single-pile type offshore wind turbine and the spring pendulum type collision tuned mass damper considering the soil effect based on an Euler-Lagrange equation;
3) And generating a stable random pulsating wind field and an irregular wave field based on a spectral expression method. The method comprises the steps of generating generalized wind load based on a phyllotactic-momentum theory by considering the aerodynamic damping of an average wind direction; generating generalized wave load based on a small amplitude wave theory and a Morison equation;
4) Under the combined action of wind and wave loads, carrying out parameter optimization on SPPTMD by taking the standard deviation of the steady-state time-course response of the fan as a target to obtain an optimal frequency ratio and an optimal damping ratio;
5) For a given crash stiffness and restitution coefficient (fastening material, shape), it is necessary to adjust the crash spacing and frequency to improve the control. Carrying out robustness analysis on SPPTMD and TMD under different collision intervals, analyzing the control effect of the SPPTMD and the TMD during frequency detuning, and giving a design suggestion of the SPPTMD applied to the offshore wind turbine;
6) Under the shutdown condition, introducing earthquake load, selecting various working conditions according to the parameter setting suggestion, comparing the working conditions with the traditional damper TMD, and verifying the rationality of the damper and the parameter setting.
In a specific embodiment, in step 1), a beam unit is used in an Abaqus software to establish an integral model of a tower and a single pile, and the tower top fixes concentrated mass including blades, a hub and a nacelle. Linear perturbation frequency analysis in the Abaqus software is used to derive the displacement by taking the first order vibrational mode of the structure. And reading the displacement by using Matlab, converting the origin of coordinates into the intersection point of the sea level and the structure, adopting a polynomial fitting method, normalizing, and fitting a 1-6 order polynomial to obtain a normalized mode shape of a first-order vibration mode of the structure.
In a specific embodiment, the specific process of step 2) is:
the euler-lagrange equation for a controlled offshore wind turbine is:
Figure BDA0003652542090000061
wherein T is the kinetic energy of the system, V is the potential energy of the system, q is the displacement of the degrees of freedom of the fan and the damper,
Figure BDA0003652542090000062
representing the velocity of each degree of freedom;
and (3) deriving a system kinetic equation:
Figure BDA0003652542090000063
m, C, K respectively represent the mass, rigidity and damping matrix of the system, Q wind 、Q wave Respectively the wind load and the wave load to which the system is subjected, F being the force generated by the damper.
In a specific embodiment, in step 3), the stable random pulsating wind field adopts an IEC Kaimal spectral model, and generates a wind load by applying a phyllo-momentum theory, and an autocorrelation power spectral function of the wind load is as follows:
Figure BDA0003652542090000064
where f denotes the frequency in Hz, σ u For standard deviation, its expression can be written as σ u ＝TI·U 0 TI is turbulence intensity, U 0 Is the average wind speed, L u For integral scale parameters, usually written as L u ＝8.10Δ u ，Δ u Is a parameter of the turbulence scale, is taken as delta u ＝0.7·min(60m,H hub )。
In a specific embodiment, in step 3), the irregular wave field adopts a Jonswap spectrum, and calculates the wave force based on a small amplitude wave theory and a morrison equation, and the spectrum model function of the irregular wave field is expressed as:
Figure BDA0003652542090000065
wherein H s And T p Respectively, the prominent wave height and the peak period, f p ＝1/T p Is the peak frequency, when f is less than or equal to f p When σ =0.07, when f > f p When, σ =0.09; γ represents a peak shape coefficient, and can be derived from the following formula:
Figure BDA0003652542090000071
in a concrete exampleIn the embodiment, in the steps 4) -6), FIGS. 3 and 4 are examples under actual parameters, and the collision stiffness is set to be 1e4N/m 1.5 The coefficient of restitution was 0.5.
The damper parameters are five in total and are respectively as follows: crash stiffness, restitution coefficient, crash interval, frequency ratio, damping ratio. Wherein the analysis assumes that the material and shape are known, i.e. the crash stiffness and restitution coefficients are known; the optimum damping ratio was found by analysis to be substantially fixed around 0.09, and therefore 0.09.
The parameter settings are therefore the frequency ratio and interval settings. The frequency ratio is related to the length of the spring pendulum, so the set parameter is the initial length l of the spring pendulum 0 And collision interval g p 。
Parameter selection (for frequency ratio and collision interval): according to fig. 4, parameter setting opinions are given to make the control effect thereof superior to that of the conventional TMD: the frequency ratio is less than or equal to 0.9, and the collision interval is less than or equal to 0.1m. The introduction of seismic loads for the verification of the shutdown condition, as shown in fig. 5, proves that SPPTMD under the statistical condition can be superior to TMD within the above parameter interval.
In a specific embodiment, the parameter setting mode in step 5) takes the internal resonance effect of the spring pendulum into account, and the SPPTMD maintains the internal resonance performance at each parameter adjustment.
In one embodiment, step 6) is illustrated, for example:
cases 1 to 4 show the shutdown conditions for introducing seismic loads, different damper parameter combinations are set according to the suggestions and compared with the conventional TMD.
Taking the average wind speed of 12m/s, the turbulence degree of 10%, the excellent wave height of 3m and the spectrum peak period of 10s, and adopting El Centrol seismic waves as seismic waves.
Given the viscoelastic layer 5 properties: crash stiffness of 1e4N/m 1.5 The coefficient of restitution was 0.5. According to the results given by the parameter optimization, the optimal damping ratio of the viscous damper 3 is 0.09,
case 1: the frequency ratio was 0.7 and the collision interval was 0.10m, as shown in (a) of FIG. 5;
case 2: the frequency ratio was 0.7, and the collision interval was 0.05m, as shown in (b) of FIG. 5;
case 3: the frequency ratio is 0.6, and the collision interval is 0.05m, as shown in (c) of fig. 5;
case 4: the frequency ratio is 0.5 and the collision interval is 0m, as shown in fig. 5 (d).
The parameter proposal is under normal working conditions under the action of wind waves, and the verification here is under the shutdown working conditions under the earthquake. It is verified here that the damper can still outperform the TMD under the parameter setting recommendations described above.
In one embodiment, the parameter optimization and parameter analysis process is performed by Matlab: firstly, in order to determine the optimal frequency ratio and the optimal damping ratio of the damper, different collision intervals are set on the assumption that the collision stiffness and the recovery coefficient are fixed, and the optimal frequency ratio and the optimal damping ratio of the damper at different collision intervals are obtained. Wherein, the frequency ratio is the ratio of the oscillation frequency in the swing direction to the natural frequency of the structure, and the swing direction frequency is only related to the gravity acceleration and the initial length of the spring 1 for hanging the weight, therefore, the initial length l of the spring 1 is adjusted 0 To adjust the frequency ratio of the damper; in step 5), the vibration damping effect of the damper under different frequency ratios is analyzed on the assumption that the collision stiffness and the restitution coefficient are fixed. And finally, introducing seismic load under the shutdown working condition, comparing the seismic load with the damping effect of the TMD, and analyzing to obtain the damping effect of the SPPTMD configured by the parameters, which is obviously superior to the damping effect of the TMD.
Specifically, the conventional damper usually has the problems of overlarge vibrator displacement and poor robustness. When the frequency of the damper is detuned, its effect is significantly reduced and even the control effect is lost. The spring pendulum type collision tuned mass damper introduced by the invention comprises two nonlinear mechanisms of collision and spring pendulum and a viscous damper 3 element, and the main energy absorption and vibration reduction mechanisms of the damper comprise the following aspects:
(1) Viscous damper 3: the viscous damper 3 is connected with the mass block 2 (also called vibrator), thereby increasing the energy consumption capacity and enhancing the vibration reduction effect; when the fan is excited by external load, the engine room moves to drive the mass block 2 to move, so that friction is generated among damping medium molecules and between the piston and the damping medium, the medium generates huge damping when passing through the piston hole, and the resultant force generated by the actions is damping force and can convert the kinetic energy of vibration (shock) into heat to be dissipated;
(2) Collision: and a stopper 4 is arranged at the boundary of the damper, and a viscoelastic layer 5 is arranged on the inner liner. When the vibrator collides with the stopper 4, the kinetic energy of the vibrator can be absorbed by the relative displacement of the viscoelastic layer 5. For the collision mechanism, which can be described by the Hertz contact model, the collision force can be written as:
Figure BDA0003652542090000091
wherein beta is the collision stiffness, mainly related to the material and geometry of the collider (vibrator and collision boundary); c is crash damping, which can be expressed as:
Figure BDA0003652542090000092
where m1 and m2 are the masses of the collider, ξ is the collision damping ratio, defined as:
Figure BDA0003652542090000093
Figure BDA0003652542090000094
for the restitution of the impinging material (viscoelastic layer 5), the initial height h of the viscoelastic layer 5 can be measured by releasing the beads above its surface 0 And the bounce height h 1 To be determined.
(3) Internal resonance effect: the vibration modes of the spring pendulum (the spring 1 and the vibrator) can be divided into radial vibration and pendulum vibration, and the frequencies are respectively expressed as:
Figure BDA0003652542090000095
and &>
Figure BDA0003652542090000096
Wherein k is s Denotes the stiffness coefficient, m, of the spring 1 p Indicating the suspension mass of the pendulum spring,/ 0 Showing the resting length of the spring when it is suspending a weight. When the ratio of the frequency of the radial vibration to the frequency of the pendulum vibration is close to 2, the two modes are strongly coupled, the vibration of one mode becomes a driving force for exciting the vibration of the other mode, and energy can be transmitted from the pendulum vibration mode to the radial vibration mode, so that the vibration reduction effect is generated. From the energy point of view, the damper absorbs the kinetic energy of the cabin to damp (shake), and when internal resonance occurs, the kinetic energy absorbed by the damper swinging to the vibration mode can be transferred to the radial vibration mode, so that the vibration absorption capacity is enhanced.
(4) The restoring force of the pendulum spring (the force of the spring 1 on the mass 2) for the system is equivalent to adding positive stiffness, and also produces a damping effect. When the displacement of the vibrator is small and no collision occurs, energy is consumed mainly by the viscous damper 3; when the displacement of the vibrator is large, the vibrator is in contact collision with the viscoelastic layer 5, and energy is consumed mainly by the viscous damper 3 and the viscoelastic layer 5 together.
The above is only a preferred embodiment of the present invention, and the protection scope of the present invention is not limited to the above-mentioned embodiments, and all technical solutions belonging to the idea of the present invention belong to the protection scope of the present invention. It should be noted that modifications and embellishments within the scope of the invention may be made by those skilled in the art without departing from the principle of the invention.

Claims (9)

1. A design method of a spring pendulum type collision tuned mass damper applied to a fan is characterized in that the damper comprises a spring (1), a mass block (2) and a viscous damper, the top end of the spring (1) is fastened on an offshore fan, the bottom end of the spring (1) is connected with the mass block (2), the viscous damper is installed below the mass block (2), two sides of the mass block (2) are provided with limiting stoppers (4), and one side of each limiting stopper (4) in contact with the mass block (2) is provided with a viscoelastic layer (5);
the design method comprises the following steps:
1) Establishing a single-pile offshore wind turbine tower frame and a single-pile integral simplified model, and analyzing and processing to obtain a normalized first-order vibration type polynomial expression;
2) Establishing an integral dynamic model of the single-pile type offshore wind turbine and the spring pendulum type collision tuned mass damper based on an Euler-Lagrange equation;
3) Generating a stable random pulsating wind field and an irregular wave field based on a spectral expression method;
4) Under the combined action of a stable random pulsating wind field and an irregular wave field, performing parameter optimization on the spring pendulum type collision tuned mass damper by taking the standard deviation of the steady-state time-course response of the fan as a target to obtain the optimal frequency ratio and the optimal damping ratio of the spring pendulum type collision tuned mass damper;
5) For given collision rigidity and recovery coefficient, adjusting collision parameters to improve control effect; and carrying out robustness analysis on the spring pendulum type collision tuned mass damper under different collision intervals, analyzing the control effect of the spring pendulum type collision tuned mass damper when the frequency is detuned, and obtaining the parameters of the spring pendulum type collision tuned mass damper when the spring pendulum type collision tuned mass damper is applied to the offshore wind turbine.
2. The design method according to claim 1, wherein the specific process of step 2) is as follows:
the Euler-Lagrange equation is:
Figure FDA0004083714640000011
wherein T is kinetic energy, V is potential energy, q is the degree of freedom of the fan and the damper,
Figure FDA0004083714640000012
representing the velocity of each degree of freedom;
the overall dynamic model equation is derived as follows:
Figure FDA0004083714640000021
wherein M, C, K respectively represent mass, rigidity, damping matrix, Q wind 、Q wave Respectively wind load and wave load borne by the system, wherein F is force generated by the damper;
Figure FDA0004083714640000024
representing the acceleration in each degree of freedom.
3. The design method as claimed in claim 2, wherein in step 3), the stable random pulsating wind field adopts IEC Kaimal spectral model and applies the phylline-momentum theory to generate wind load, and the autocorrelation power spectral function is written as:
Figure FDA0004083714640000022
where f denotes the frequency in Hz, σ u Is the standard deviation, the expression of which is written as σ u ＝TI·U 0 TI is turbulence intensity, U 0 Is the average wind speed, L u Is an integral scale parameter, wherein L u ＝8.10Δ u ，Δ u Is a turbulence scale parameter.
4. The design method according to claim 3, wherein in step 3), the irregular wave field adopts Jonswap spectrum, and calculates wave force based on small amplitude wave theory and Morrison's equation, and its spectral model function is expressed as:
Figure FDA0004083714640000023
wherein H s And T p Respectively representing the effective wave height and the spectral peak period, f p ＝1/T p Is the peak frequency, when f is less than or equal to f p When σ =0.07; when f > f p When, σ =0.09; gamma denotes the peak shapeAnd (4) the coefficient.
5. The design method according to any one of claims 1 to 4, wherein in step 5), the collision parameters include a collision interval and a frequency ratio.
6. The design method according to claim 5, wherein the frequency ratio is ≦ 0.9 and the collision interval is ≦ 0.1m.
7. The design method according to any one of claims 1 to 4, characterized by further comprising a step 6) after the step 5), introducing seismic load under a shutdown condition, and selecting multiple conditions according to the parameters obtained in the step 5) to compare with the traditional damper TMD so as to verify the reasonableness of the damper and the parameter setting.
8. Method of designing according to claim 1, characterized in that the stop (4) is a stop plate.
9. The design method according to claim 1 or 2, characterized in that the viscoelastic layer (5) is a VHB rubber or a HEDR rubber.
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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003307251A (en) * 2002-04-15 2003-10-31 Tokkyokiki Corp Damping device
CN202913524U (en) * 2012-10-29 2013-05-01 广东电网公司电力科学研究院 Multi-dimensional collision energy consumption quality swinging damper
CN107338885A (en) * 2017-08-24 2017-11-10 沈阳建筑大学 A kind of power transmission tower shock absorber and its preparation and application
CN107701635A (en) * 2017-06-19 2018-02-16 中国人民解放军国防科学技术大学 Broad band low frequency locally resonant structure with super damping characteristic
CN110296182A (en) * 2019-06-28 2019-10-01 西安理工大学 A kind of tuning quality damper vibration damping system being incorporated to nonlinear energy trap
CN112227550A (en) * 2020-10-21 2021-01-15 浙江建科减震科技有限公司 Frequency modulation mass damper capable of being assembled in modularization mode
CN113239483A (en) * 2021-04-27 2021-08-10 中国华能集团清洁能源技术研究院有限公司 Integral cost reduction optimization design method for offshore wind turbine supporting structure

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003307251A (en) * 2002-04-15 2003-10-31 Tokkyokiki Corp Damping device
CN202913524U (en) * 2012-10-29 2013-05-01 广东电网公司电力科学研究院 Multi-dimensional collision energy consumption quality swinging damper
CN107701635A (en) * 2017-06-19 2018-02-16 中国人民解放军国防科学技术大学 Broad band low frequency locally resonant structure with super damping characteristic
CN107338885A (en) * 2017-08-24 2017-11-10 沈阳建筑大学 A kind of power transmission tower shock absorber and its preparation and application
CN110296182A (en) * 2019-06-28 2019-10-01 西安理工大学 A kind of tuning quality damper vibration damping system being incorporated to nonlinear energy trap
CN112227550A (en) * 2020-10-21 2021-01-15 浙江建科减震科技有限公司 Frequency modulation mass damper capable of being assembled in modularization mode
CN113239483A (en) * 2021-04-27 2021-08-10 中国华能集团清洁能源技术研究院有限公司 Integral cost reduction optimization design method for offshore wind turbine supporting structure

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