CN113062649B - Pre-stress tuned mass damper installation method based on parameter design calculation - Google Patents

Pre-stress tuned mass damper installation method based on parameter design calculation Download PDF

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CN113062649B
CN113062649B CN202110346170.5A CN202110346170A CN113062649B CN 113062649 B CN113062649 B CN 113062649B CN 202110346170 A CN202110346170 A CN 202110346170A CN 113062649 B CN113062649 B CN 113062649B
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CN113062649A (en
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刘纲
雷振博
杨庆山
陈奇
杜昊天
王晖
刘淇
贺成华
郭宇飞
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    • E—FIXED CONSTRUCTIONS
    • E04—BUILDING
    • E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
    • E04H9/00—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate
    • E04H9/02—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate withstanding earthquake or sinking of ground
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    • E04—BUILDING
    • E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
    • E04H12/00—Towers; Masts or poles; Chimney stacks; Water-towers; Methods of erecting such structures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D13/00—Assembly, mounting or commissioning of wind motors; Arrangements specially adapted for transporting wind motor components
    • F03D13/20—Arrangements for mounting or supporting wind motors; Masts or towers for wind motors
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    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
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    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
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Abstract

The invention discloses a method for installing a prestress tuned mass damper based on parameter design calculation, which comprises the following steps of: s1, calculating to obtain parameters of the wind turbine tower structure; s2, calculating parameters of the pre-stress tuned mass damper according to the obtained parameters of the wind turbine tower structure; and S3, selecting a corresponding pre-stress tuned mass damper, and installing the pre-stress tuned mass damper on the wind turbine tower. By adopting the method for installing the prestress tuned mass damper based on parameter design calculation, provided by the invention, various parameters of the prestress tuned mass damper can be adaptively determined by combining parameters of a tower structure of a wind turbine, a theoretical basis is provided for engineering design, and the selection, installation and application and popularization of the prestress tuned mass damper are facilitated.

Description

Pre-stress tuned mass damper installation method based on parameter design calculation
Technical Field
The invention relates to the technical field of wind power generation equipment, in particular to a method for installing a pre-stress tuned mass damper based on parameter design calculation.
Background
In order to improve the power generation efficiency and adapt to the running requirements of wind turbine generators in low wind speed areas, the wind turbine is developed in the direction of large megawatt, the tower structure of the wind turbine tower gradually becomes high and flexible, so that the self-vibration frequency of the wind turbine is reduced, and the self-vibration frequency of the wind turbine tower gradually approaches to the external load frequency of wind, waves and the like, so that the resonance of the wind turbine tower is easily caused. The excessive vibration not only reduces the self fatigue life of the tower, but also has great influence on the performance of the generator set, and can reduce the whole service life of the fan and reduce the generating efficiency. Therefore, the development of the wind turbine in the direction of large megawatt must solve the problem of excessive vibration of the tower.
In recent years, more scholars and engineers propose various theoretical conceptual designs of passive vibration reduction techniques and devices for fans, which are mainly divided into two types, namely Tuned Liquid Dampers (TLD) and Tuned Mass Dampers (TMD).
The tuned liquid damper is a typical and effective passive structure vibration reduction control device, and the principle of vibration reduction control is to fix a water tank on a controlled structure, and to form vibration reduction force by the dynamic pressure difference generated on two sides of the inner wall of a container by the liquid in the water tank shaking. However, the biggest bottleneck in the application of tuned liquid dampers to wind turbine towers is that the control force is difficult to calculate accurately due to irregular fluid fluctuation in the water tank, so the theory of the device is to be further improved.
The tuned mass damper adjusts the vibration frequency of the mass block to be close to the main vibration frequency of the fan tower, and energy is transferred from the fan tower to the mass damper through the interaction between the tuned mass damper and the fan tower, so that the transfer purpose is achieved. And harmonious mass damper divide into supporting formula TMD and suspension type TMD, and supporting formula TMD generally need arrange in the top of fan, but fan top cabin space is limited, is unfavorable for arranging. Therefore, the suspended TMD is arranged inside the fan tower, but the frequency of the suspended TMD can be adjusted only by the swing length, the swing angle of the suspended TMD is very small due to the extremely limited space inside the tower, and the control force provided under the small swing angle is very limited, so that the damping effect is not ideal.
Therefore, in order to solve the above problems, the inventor team designed a completely new pre-stressed tuned mass damper (PS-TMD), but at present, the design and installation of the pre-stressed tuned mass damper are affected by multiple factors, and often a complex finite element model needs to be established, which is more labor-intensive and inconvenient for practical application. It is urgent to solve the above problems.
Disclosure of Invention
In order to solve the technical problems, the invention provides a prestress tuned mass damper installation method based on parameter design and calculation.
The technical scheme is as follows:
a prestress tuned mass damper installation method based on parameter design calculation is carried out according to the following steps:
s1, calculating to obtain parameters of the wind turbine tower structure;
s2, calculating parameters of the pre-stress tuned mass damper according to the obtained parameters of the wind turbine tower structure;
s3, selecting a corresponding pre-stress tuned mass damper, and installing the pre-stress tuned mass damper on a wind turbine tower;
the wind turbine tower structure comprises a tower and a cabin arranged at the top of the tower, blades are rotatably arranged on the cabin, and the tower is composed of a plurality of sections of towers which are sequentially connected through flange plates;
the tuned mass damper is characterized by comprising a mass block hung between the tower top and a flange plate closest to the tower top through a prestressed stay cable, wherein a plurality of dampers are arranged along the circumferential direction of the mass block, and two ends of each damper are respectively and elastically supported between the outer wall of the mass block and the inner wall of a corresponding tower barrel;
in step S1, the parameters of the wind turbine tower structure include a shape function of the first-order vibration of the tower
Figure BDA0003000756720000021
And generalized mass m of wind turbine tower structuresAnd generalized stiffness ks；
In step S2, parameters of the pre-stressed tuned mass damperNumber of masses m comprising a prestressed tuned mass damperdSuspension height h' of the tuned mass damper under prestress, fundamental circular frequency omega of the tuned mass damper under prestressdPrestress value f of prestress inhaul cable and viscous damping coefficient c of each damperd。
The tuned mass damper with the prestress is adopted, the mass block is suspended by the prestress stay cable between the tower top and the close flange plate of the tuned mass damper with the prestress, the mass block is connected with the wall of the tower barrel through a plurality of dampers which equally divide the circumference, energy is dissipated by using the inertia force generated by the mass block, the frequency of the mass block is doubly tuned by the prestress and the suspension height, under the service environment, when the horizontal amplitude of the top of the tower is small, the vibration damping mass block rapidly generates corresponding horizontal vibration under the action of the inertia force, and under the action of the prestress stay cable, the inertia force generated by the motion of the vibration damping mass block reacts on the structure, so that the vibration damping effect is generated; by adopting the method, various parameters of the pre-stressed tuned mass damper can be adaptively determined by combining parameters of a tower structure of the wind turbine, a theoretical basis is provided for engineering design, and the model selection, installation and use popularization of the pre-stressed tuned mass damper are facilitated.
Preferably, the step S1 includes the steps of:
s11, simplifying the actual wind turbine tower structure into an equivalent single-degree-of-freedom system dynamic model of the wind turbine tower structure: simplifying a wind turbine tower structure into a cantilever beam structure, taking the center point of the bottom surface of the tower of the wind turbine tower structure as the origin of a coordinate system, taking the vertical direction of the tower as a z axis, the downwind direction of the wind turbine as an x axis, the crosswind direction of the wind turbine as a y axis, taking the concentrated mass of an engine room and blades positioned at the top of the tower as M, the total height of the tower as H, the mass density M (z) of the tower and the bending rigidity EI (z) of the tower changing along the z axis direction;
s12, obtaining a shape function of the first-order vibration of the tower according to the step S11:
Figure BDA0003000756720000031
in the formula (1), t represents time, t is expressed by s, x (z, t) represents the displacement of a z section at the moment t, and x (H, t) represents the displacement of a tower top at the moment t;
according to the deflection of the free end of the cantilever beam in the mechanics of materials under concentrated load, the method comprises the following steps:
Figure BDA0003000756720000032
wherein, P represents concentration force, the unit is N, EI represents the bending rigidity of the tower section;
the formula (2) can be substituted for the formula (1):
Figure BDA0003000756720000033
step 13, calculating to obtain the generalized mass m of the wind turbine tower structuresAnd generalized stiffness ks：
According to the generalized distribution flexible theory, generalized mass msAnd generalized stiffness ksCan be expressed as:
Figure BDA0003000756720000041
in the formula (4), the generalized mass msIn kg, generalized stiffness ksIn units of N/m, m (z) represents the distribution mass of the wind turbine tower along the z-axis direction, m (z) is in units of kg/m, g represents the gravitational acceleration, and g is in units of m/s2，
Figure BDA0003000756720000042
The value of the shape function at the top of the column was 1.
By adopting the method, the parameter calculation method of the wind turbine tower structure is determined.
Preferably, the step S2 includes the steps of:
step S21 of calculating to obtain pre-stress tuned mass damperMass md：
md＝ams (5)
In the formula (5), a is an intermediate parameter, the value range of a is 1-3 percent, and m is massdThe unit of (a) is kg;
step S22, calculating a suspension height h' of the pre-stressed tuned mass damper:
h′＝bh (6)
in the formula (6), b is an intermediate parameter, the value range of b is 1/4-1/2, the suspension height h 'represents the distance from the mass block of the prestressed tuned mass damper to the tower top, the unit of h' is m, h represents the distance from the flange plate closest to the tower top, and the unit of h is m;
step S23, calculating to obtain the fundamental circle frequency omega of the prestress tuned mass damperd：
According to the structural dynamics principle and a dynamics analysis model of the wind turbine tower and the pre-stress tuned mass damper, obtaining a motion equation of a system:
Figure BDA0003000756720000043
in the formula (7), csFor representing the damping coefficient of the wind turbine tower structure, for the steel low-damping tower, c is generally taken to simplify the calculation s0, F (t) is an external load, cdRepresenting damping coefficient, xsDisplacement at column top, xdDisplacement of mass, kdRepresents the lateral stiffness of the damper;
according to a formula (7) and a structural dynamics principle, the fundamental circular frequency omega of the wind turbine tower with the prestressed tuned mass dampersCan be expressed as:
Figure BDA0003000756720000051
in the formula (8), ωsThe unit of (d) is rad/s;
according to the formula (7) and the structure dynamics principle, the prestress is tunedFundamental circular frequency ω of mass damperdCan be expressed as:
Figure BDA0003000756720000052
in the formula (9), ωdThe unit of (d) is rad/s;
step S24, calculating to obtain a prestress value f of the prestress stay cable:
assuming that f (t) is in the form of a sinusoidal load, it can be expressed as:
F(t)＝P0sinωt (10)
in the formula (10), P0Representing the amplitude of the sinusoidal load, omega being the load frequency;
substituting the formula (10) into the formula (7), solving the motion equation of the system to obtain the power amplification coefficient eta of the system:
Figure BDA0003000756720000053
in the formula (11), beta represents the load frequency omega and the basic circle frequency omega of the wind turbine tower with the pre-stress tuned mass dampersMu represents the fundamental circular frequency omega of the prestressed tuned mass damperdThe frequency omega of the basic circle of the wind turbine tower with the prestressed tuned mass dampersAnd α and γ each represent a damping parameter ratio, which is expressed as:
Figure BDA0003000756720000061
the optimal frequency ratio mu is combined with the theory of the existing tuned liquid damper and the structure dynamics principleoptIs represented by the following formula:
Figure BDA0003000756720000062
due to the fact thatopt＝ωd/ωsTherefore:
Figure BDA0003000756720000063
substituting equations (8) and (9) into equation (14) to obtain the prestress f of the prestress tuned mass damper as:
Figure BDA0003000756720000064
in formula (15), the unit of the prestress f is N;
step 25, calculating to obtain the viscous damping coefficient c of each damperd：
Combining the theory of the existing tuned liquid damper and equation (11), the following expression is obtained:
Figure BDA0003000756720000065
in the formula (16), η and β represent a power amplification factor and a damping ratio, respectively, and βMAnd betaNIs the branch point frequency ratio, and the expression is:
Figure BDA0003000756720000066
in the formula (17), μ represents a frequency ratio, and γ and α both represent tuning parameter ratios;
from equations (16) and (17) we can derive:
Figure BDA0003000756720000071
in formula (18), ζ ═ cd/(mdωs) By solving equation (18), we can obtain:
Figure BDA0003000756720000072
in the formula (19), the viscous damping coefficient c of each damperdThe unit of (A) is N/m/s.
By adopting the method, the calculation method of each parameter of the pre-stress tuned mass damper is determined, and each parameter of the pre-stress tuned mass damper can be adaptively determined by combining the parameters of the tower structure of the wind turbine.
Preferably, the dampers are all viscous dampers. By adopting the structure, the viscous damper not only can provide stable and reliable additional damping, but also can play a role in guiding and limiting, and can be used as a composite vibration damping element to avoid the frequency imbalance problem caused by a large swing angle, thereby realizing the double tuning function of the annular mass block under the large-amplitude vibration.
Compared with the prior art, the invention has the beneficial effects that:
according to the installation method of the pre-stressed tuned mass damper based on parameter design calculation, the pre-stressed tuned mass damper suspends a mass block through a pre-stressed cable between a tower top and a close flange, the mass block is connected with a plurality of dampers which are equally divided into circumferences on the wall of a tower, energy is dissipated through inertia force generated by the mass block, the frequency of the mass block is doubly tuned through pre-stress and suspension height, under the service environment, when the horizontal amplitude of the top of the tower is small, the vibration reduction mass block can rapidly generate corresponding horizontal vibration under the action of the inertia force, and under the action of the pre-stressed cable, the inertia force generated by the motion of the vibration reduction mass block can react on a structure, so that the vibration reduction effect is generated; in addition, various parameters of the tuned mass damper under prestress can be adaptively determined by combining parameters of a tower structure of the wind turbine, a theoretical basis is provided for engineering design, and the tuned mass damper under prestress is convenient to select, install, use and popularize.
Drawings
FIG. 1 is a schematic illustration of a wind turbine tower construction;
FIG. 2 is a schematic view of the mounting structure of the pre-stressed tuned mass damper with the nacelle and the flange;
FIG. 3 is a schematic diagram of an equivalent single degree of freedom architecture with actual wind turbine tower structural key locations;
FIG. 4 is a model of a dynamic analysis of a wind turbine tower and a pre-stressed tuned mass damper.
Detailed Description
The present invention will be further described with reference to the following examples and the accompanying drawings.
As shown in FIGS. 1 and 2, the wind turbine tower structure comprises a tower 1 and a nacelle 2 mounted on the top of the tower, blades 6 are rotatably mounted on the nacelle 2, and the tower 1 is composed of a plurality of tower barrels 1a connected in sequence through flange plates 1 b. The tuned mass damper with prestress comprises a mass block 3 which is hung between the tower top (namely a cabin 2) and a flange plate closest to the tower top 1b through a prestress stay cable 5, a plurality of dampers 4 are arranged along the circumferential direction of the mass block 3, and two ends of each damper 4 are respectively and elastically supported between the outer wall of the mass block 3 and the inner wall of the corresponding tower barrel 1 a.
The mass block 3 is connected with the wall of the tower barrel 1a through a plurality of dampers 4 which are equally divided into circles, so that energy is dissipated through the inertia force generated by the mass block 3, the frequency of the mass block 3 is doubly tuned through prestress and suspension height, in a service environment, when the horizontal amplitude of the top of the tower barrel 1 is small, the mass block 3 rapidly generates corresponding horizontal vibration under the action of the inertia force, and under the action of the prestress cable, the inertia force generated by the motion of the mass block 3 reacts on the structure, so that a vibration damping effect is generated.
Furthermore, the dampers 4 are preferably viscous dampers, which not only can provide stable and reliable additional damping, but also can play a role in guiding and limiting, and can be used as a composite vibration damping element to avoid frequency imbalance caused by a large swing angle, thereby realizing the double tuning function of the annular mass block under large-amplitude vibration.
Referring to fig. 1-4, the installation method of the prestressed tuned mass damper comprises the following steps:
and S1, calculating to obtain the parameters of the wind turbine tower structure.
Specifically, step S1 includes the steps of:
s11, simplifying the actual wind turbine tower structure into an equivalent single-degree-of-freedom system dynamic model of the wind turbine tower structure: the wind turbine tower structure is simplified into a cantilever beam structure, the central point of the bottom surface of a tower 1 of the wind turbine tower structure is taken as the origin of a coordinate system, the vertical direction of the tower 1 is taken as the z axis, the downwind direction of the wind turbine is taken as the x axis, the crosswind direction of the wind turbine is taken as the y axis (the crosswind direction is vertical to the downwind direction along the horizontal direction, so the y axis is vertical to the x axis on the horizontal plane), the concentrated mass of an engine room 2 and blades 6 positioned at the top of the tower 1 is M, the total height of the tower 1 is H, the mass density M (z) of the tower 1, and the bending rigidity EI (z) of the tower 1 changing along the z axis direction.
S12, obtaining the shape function of the first-order vibration of the tower 1 according to the step S11:
Figure BDA0003000756720000091
in the formula (1), t represents time, t is expressed by s, x (z, t) represents the displacement of a z section at the moment t, and x (H, t) represents the displacement of a tower top at the moment t;
according to the deflection of the free end of the cantilever beam in the mechanics of materials under concentrated load, the method comprises the following steps:
Figure BDA0003000756720000092
wherein, P represents concentration force, the unit is N, EI represents the bending rigidity of the tower section;
the formula (2) can be substituted for the formula (1):
Figure BDA0003000756720000093
step 13, calculating to obtain the generalized mass m of the wind turbine tower structuresAnd generalized stiffness ks：
According to the generalized distribution flexible theory, generalized mass msAnd generalized stiffness ksCan be expressed as:
Figure BDA0003000756720000094
in the formula (4), the generalized mass msIn kg, generalized stiffness ksIn units of N/m, m (z) represents the distribution mass of the wind turbine tower along the z-axis direction, m (z) is in units of kg/m, g represents the gravitational acceleration, and g is in units of m/s2，
Figure BDA0003000756720000095
The value of the shape function at the top of the column was 1.
And S2, calculating parameters of the pre-stress tuned mass damper according to the obtained parameters of the wind turbine tower structure.
Specifically, step S2 includes the steps of:
step S21, calculating mass m of the prestress tuned mass damperd：
md＝ams (5)
In the formula (5), a is an intermediate parameter, the value range of a is 1% -3%, it should be noted that the value range of a is obtained based on experiments, and the mass m isdThe unit of (a) is kg;
step S22, calculating a suspension height h' of the pre-stressed tuned mass damper:
h′＝bh (6)
in the formula (6), b is an intermediate parameter, the value range of b is 1/4-1/2, it is noted that the value range of b is obtained according to field experience, the suspension height h 'represents the distance from the mass block of the prestress tuned mass damper to the tower top, the unit of h' is m, the unit of h represents the distance from the flange nearest to the tower top, and the unit of h is m;
step S23, calculating to obtain the fundamental circle frequency omega of the prestress tuned mass damperd：
Referring to fig. 4, according to the structural dynamics principle and the dynamics analysis model of the wind turbine tower and the pre-stress tuned mass damper, the motion equation of the system is obtained:
Figure BDA0003000756720000101
in the formula (7), csFor representing the damping coefficient of the wind turbine tower structure, for the steel low-damping tower, c is generally taken to simplify the calculation s0, F (t) is an external load, cdRepresenting damping coefficient, xsDisplacement at column top, xdDisplacement of mass, kdRepresents the lateral stiffness of the damper;
according to a formula (7) and a structural dynamics principle, the fundamental circular frequency omega of the wind turbine tower with the prestressed tuned mass dampersCan be expressed as:
Figure BDA0003000756720000102
in the formula (8), ωsThe unit of (d) is rad/s;
the fundamental circular frequency omega of the prestressed tuned mass damper according to the formula (7) and the structural dynamics principledCan be expressed as:
Figure BDA0003000756720000111
in the formula (9), ωdThe unit of (d) is rad/s;
step S24, calculating to obtain a prestress value f of the prestress stay cable:
assuming that f (t) is in the form of a sinusoidal load, it can be expressed as:
F(t)＝P0sinωt (10)
in the formula (10), P0Representing the amplitude of the sinusoidal load, omega being the load frequency;
substituting the formula (10) into the formula (7), solving the motion equation of the system to obtain the power amplification coefficient eta of the system:
Figure BDA0003000756720000112
in the formula (11), beta represents the load frequency omega and the basic circle frequency omega of the wind turbine tower with the pre-stress tuned mass dampersMu represents the fundamental circular frequency omega of the prestressed tuned mass damperdThe frequency omega of the basic circle of the wind turbine tower with the prestressed tuned mass dampersAnd α and γ each represent a damping parameter ratio, which is expressed as:
Figure BDA0003000756720000113
the optimal frequency ratio mu is combined with the theory of the existing tuned liquid damper and the structure dynamics principleoptIs represented by the following formula:
Figure BDA0003000756720000114
due to the fact thatopt＝ωd/ωsTherefore:
Figure BDA0003000756720000121
substituting equations (8) and (9) into equation (14) to obtain the prestress f of the prestress tuned mass damper as:
Figure BDA0003000756720000122
in formula (15), the unit of the prestress f is N;
step 25, calculating to obtain the viscous damping coefficient c of each damperd：
Combining the theory of the existing tuned liquid damper and equation (11), the following expression is obtained:
Figure BDA0003000756720000123
in the formula (16), η and β represent a power amplification factor and a damping ratio, respectively, and βMAnd betaNIs the branch point frequency ratio, and the expression is:
Figure BDA0003000756720000124
in the formula (17), μ represents a frequency ratio, and γ and α both represent tuning parameter ratios;
from equations (16) and (17) we can derive:
Figure BDA0003000756720000125
in formula (18), ζ ═ cd/(mdωs) By solving equation (18), we can obtain:
Figure BDA0003000756720000126
in the formula (19), the viscous damping coefficient c of each damperdThe unit of (A) is N/m/s.
And S3, selecting a corresponding pre-stress tuned mass damper, and installing the pre-stress tuned mass damper on the wind turbine tower. Specifically, the mass m of the prestress tuned mass damper is determined on the basis of the parameters of the tower structure of the basic wind turbinedSuspension height h', fundamental circle frequency ωdPrestress value f of prestress inhaul cable and viscous damping coefficient c of each damperdThe tuned mass damper with the prestress is arranged on the wind turbine tower, and can play an excellent shock absorption effect on the wind turbine tower structure.
Finally, it should be noted that the above-mentioned description is only a preferred embodiment of the present invention, and those skilled in the art can make various similar representations without departing from the spirit and scope of the present invention.

Claims (2)

1. A prestress tuned mass damper installation method based on parameter design calculation is carried out according to the following steps:
s1, calculating to obtain parameters of the wind turbine tower structure;
s2, calculating parameters of the pre-stress tuned mass damper according to the obtained parameters of the wind turbine tower structure;
s3, selecting a corresponding pre-stress tuned mass damper, and installing the pre-stress tuned mass damper on a wind turbine tower;
the wind turbine tower structure comprises a tower and a cabin arranged at the top of the tower, blades are rotatably arranged on the cabin, and the tower is composed of a plurality of sections of towers which are sequentially connected through flange plates;
the tuned mass damper is characterized by comprising a mass block hung between the tower top and a flange plate closest to the tower top through a prestressed stay cable, wherein a plurality of dampers are arranged along the circumferential direction of the mass block, and two ends of each damper are respectively and elastically supported between the outer wall of the mass block and the inner wall of a corresponding tower barrel;
in step S1, the parameters of the wind turbine tower structure include a shape function of the first-order vibration of the tower
Figure FDA0003311545530000011
And generalized mass m of wind turbine tower structuresAnd generalized stiffness ks；
In step S2, the parameter of the tuned mass damper includes a mass m of the tuned mass damperdSuspension height h' of the tuned mass damper under prestress, fundamental circular frequency omega of the tuned mass damper under prestressdPrestress value f of prestress inhaul cable and viscous damping coefficient c of each damperd；
The step S1 includes the steps of:
s11, simplifying the actual wind turbine tower structure into an equivalent single-degree-of-freedom system dynamic model of the wind turbine tower structure: simplifying a wind turbine tower structure into a cantilever beam structure, taking the center point of the bottom surface of the tower of the wind turbine tower structure as the origin of a coordinate system, taking the vertical direction of the tower as a z axis, the downwind direction of the wind turbine as an x axis, the crosswind direction of the wind turbine as a y axis, taking the concentrated mass of an engine room and blades positioned at the top of the tower as M, the total height of the tower as H, the mass density M (z) of the tower and the bending rigidity EI (z) of the tower changing along the z axis direction;
s12, obtaining a shape function of the first-order vibration of the tower according to the step S11:
Figure FDA0003311545530000021
in the formula (1), t represents time, t is expressed by s, x (z, t) represents the displacement of a z section at the moment t, and x (H, t) represents the displacement of a tower top at the moment t;
according to the deflection of the free end of the cantilever beam in the mechanics of materials under concentrated load, the method comprises the following steps:
Figure FDA0003311545530000022
wherein, P represents concentration force, the unit is N, EI represents the bending rigidity of the tower section;
the formula (2) can be substituted for the formula (1):
Figure FDA0003311545530000023
step 13, calculating to obtain the generalized mass m of the wind turbine tower structuresAnd generalized stiffness ks：
According to the generalized distribution flexible theory, generalized mass msAnd generalized stiffness ksCan be expressed as:
Figure FDA0003311545530000024
in the formula (4), the generalized mass msIn kg, generalized stiffness ksIn units of N/m, m (z) represents the distribution mass of the wind turbine tower along the z-axis direction, m (z) is in units of kg/m, g represents the gravitational acceleration, and g is in units of m/s2，
Figure FDA0003311545530000025
A value representing a shape function of the column top, which is 1;
the step S2 includes the steps of:
step S21, calculating mass m of the prestress tuned mass damperd：
md＝ams (5)
In the formula (5), a is an intermediate parameter, the value range of a is 1-3 percent, and m is massdThe unit of (a) is kg;
step S22, calculating a suspension height h' of the pre-stressed tuned mass damper:
h′＝bh (6)
in the formula (6), b is an intermediate parameter, the value range of b is 1/4-1/2, the suspension height h 'represents the distance from the mass block of the prestressed tuned mass damper to the tower top, the unit of h' is m, h represents the distance from the flange plate closest to the tower top, and the unit of h is m;
step S23, calculating to obtain the fundamental circle frequency omega of the prestress tuned mass damperd：
According to the structural dynamics principle and a dynamics analysis model of the wind turbine tower and the pre-stress tuned mass damper, obtaining a motion equation of a system:
Figure FDA0003311545530000031
in the formula (7), csFor representing the damping coefficient of the wind turbine tower structure, for the steel low-damping tower, c is generally taken to simplify the calculations0, F (t) is an external load, cdRepresenting damping coefficient, xsDisplacement at column top, xdDisplacement of mass, kdRepresents the lateral stiffness of the damper;
according to a formula (7) and a structural dynamics principle, the fundamental circular frequency omega of the wind turbine tower with the prestressed tuned mass dampersCan be expressed as:
Figure FDA0003311545530000032
in the formula (8), ωsThe unit of (d) is rad/s;
the fundamental circular frequency omega of the prestressed tuned mass damper according to the formula (7) and the structural dynamics principledCan be expressed as:
Figure FDA0003311545530000033
in the formula (9), ωdThe unit of (d) is rad/s;
step S24, calculating to obtain a prestress value f of the prestress stay cable:
assuming that f (t) is in the form of a sinusoidal load, it can be expressed as:
F(t)＝P0sinωt (10)
in the formula (10), P0Representing the amplitude of the sinusoidal load, omega being the load frequency;
substituting the formula (10) into the formula (7), solving the motion equation of the system to obtain the power amplification coefficient eta of the system:
Figure FDA0003311545530000041
in the formula (11), beta represents the load frequency omega and the basic circle frequency omega of the wind turbine tower with the pre-stress tuned mass dampersMu represents the fundamental circular frequency omega of the prestressed tuned mass damperdAnd the basic circle of the fan tower frame after the prestressed tuned mass damper is addedFrequency omegasAnd α and γ each represent a damping parameter ratio, which is expressed as:
Figure FDA0003311545530000042
the optimal frequency ratio mu is combined with the theory of the existing tuned liquid damper and the structure dynamics principleoptIs represented by the following formula:
Figure FDA0003311545530000043
due to the fact thatopt＝ωd/ωsTherefore:
Figure FDA0003311545530000044
substituting equations (8) and (9) into equation (14) to obtain the prestress f of the prestress tuned mass damper as:
Figure FDA0003311545530000045
in formula (15), the unit of the prestress f is N;
step 25, calculating to obtain the viscous damping coefficient c of each damperd：
Combining the theory of the existing tuned liquid damper and equation (11), the following expression is obtained:
Figure FDA0003311545530000051
in the formula (16), η and β represent a power amplification factor and a damping ratio, respectively, and βMAnd betaNIs the branch point frequency ratio, and the expression is:
Figure FDA0003311545530000052
in the formula (17), μ represents a frequency ratio, and γ and α both represent tuning parameter ratios;
from equations (16) and (17) we can derive:
Figure FDA0003311545530000053
in formula (18), ζ ═ cd/(mdωs) By solving equation (18), we can obtain:
Figure FDA0003311545530000054
in the formula (19), the viscous damping coefficient c of each damperdThe unit of (A) is N/m/s.
2. The parametric design computation-based pre-stressed tuned mass damper installation method as claimed in claim 1, wherein: the dampers are all viscous dampers.
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