CN117989089A - Mounting structure and mounting method of pendulum type inertial volume tuned mass damper - Google Patents
Mounting structure and mounting method of pendulum type inertial volume tuned mass damper Download PDFInfo
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Abstract
The invention discloses a mounting structure and a mounting method of a pendulum type inertial-to-volume tuned mass damper, wherein the mounting structure of the pendulum type inertial-to-volume tuned mass damper comprises a tower barrel and the pendulum type inertial-to-volume tuned mass damper mounted in the tower barrel. Because the inertial device is arranged on the lower cover, the inertial device achieves the effect of grounding at one end by utilizing the characteristic that the annular pulley rail does not swing together with the tower barrel and adopting guide rope transmission, and the mass block provides control force of reverse resonance.
Description
Technical Field
The invention relates to the technical field of wind power generation equipment, in particular to a mounting structure and a mounting method of a pendulum type inertial-to-volume tuned mass damper.
Background
In recent years, the wind power generation industry in China, particularly the wind power equipment manufacturing industry, is rapidly rising, and the wind power generation industry has become a place where the global wind power generation is most active. In order to improve the power generation efficiency and meet the running requirement of the wind turbine in low wind speed areas, the wind turbine is developed in the forward direction of large megawatt, the tower structure of the wind turbine is gradually increased, the self-vibration frequency of the wind turbine is reduced due to the flexibility of the wind turbine, and the wind turbine is gradually close to the external load frequency of wind, waves and the like, so that the resonance of the wind turbine tower is easily caused. Excessive vibration not only reduces the fatigue life of the tower, but also has a larger influence on the performance of the generator set, and reduces the overall life of the fan and the power generation efficiency. Therefore, the fan is developed in the direction of large megawatts, so that the problem of excessive vibration of the tower must be solved.
The tuned mass damper (Tuned MASS DAMPER, TMD for short) adjusts the vibration frequency of the mass block to be close to the main frequency of the vibration of the fan tower, and the energy transfer from the fan tower to the mass damper is realized through the interaction between the tuned mass damper and the fan tower, so that the transfer purpose is achieved. While tuned mass dampers are classified into supported TMDs and suspended TMDs, supported TMDs generally require placement on top of the wind turbine, but the wind turbine top nacelle space is limited and is not conducive to placement. Therefore, the suspension TMD is arranged inside the fan tower, but the frequency of the suspension TMD can be adjusted only through the swing length, and the swing angle of the suspension TMD is very small due to the extremely limited space inside the tower, and the control force is very limited under a small swing angle, so that the vibration reduction effect is not ideal.
In order to solve the above problems, please refer to the patent CN113062649B of the present application, the inventor team of the present application designed a method for installing a pre-stress tuned mass damper based on parameter design calculation, the pre-stress tuned mass damper (PTMD for short) hangs a mass block through a pre-stress cable between the tower top and a flange close to the tower top, the mass block is connected with a plurality of dampers with equal circumference of the tower wall, and further uses the inertia force generated by the mass block to dissipate energy, and the frequency of the mass block is doubly tuned through pre-stress and hanging height, under the service environment, when the horizontal amplitude of the top of the tower is smaller, the vibration damper mass block will rapidly generate corresponding horizontal vibration under the action of the inertia force, and under the action of the pre-stress cable, the inertia force generated by the motion of the vibration damper mass block will react to the structure itself, thereby generating vibration damping effect; in addition, various parameters of the prestress tuning mass damper can be adaptively determined by combining parameters of the wind turbine tower structure, a theoretical basis is provided for engineering design, and the prestress tuning mass damper is convenient to select, install and use.
However, in practical application, the applicant finds that the prestress tuning mass damper is not only very heavy in mass block and inconvenient to install and maintain, but also very easy to produce fatigue damage in the long-term service process of the prestress inhaul cable, so that the control effect is greatly weakened, and great potential safety hazards exist. Therefore, the applicant hopes that the vibration reduction mass block and the inertia capacity device are combined through the inhaul cable system to achieve the purpose of light control, and meanwhile springs which are obliquely arranged are connected between the vibration reduction mass block and the tower cylinder wall through universal hinges, so that the purpose of double tuning frequency is achieved, and the influence of prestress on the fatigue performance of the inhaul cable is reduced.
Disclosure of Invention
The invention provides an installation structure and an installation method of a pendulum type inertial tuned mass damper, aiming at solving the technical problems that the weight of a mass block of the existing prestress tuned mass damper is heavy and a prestress inhaul cable is easy to generate fatigue damage.
The technical scheme is as follows:
The first aspect of the application relates to a mounting structure of a pendulum inertial-volume tuned mass damper, which comprises a tower cylinder and the pendulum inertial-volume tuned mass damper, wherein the tower cylinder comprises a cylinder body with a cylindrical structure, and an upper cover and a lower cover respectively covering the upper end and the lower end of the cylinder body;
The pendulum type inertial volume tuning mass damper comprises a mass pendulum, an annular pulley rail, at least one set of inertial volume balancing components and at least two sets of spring damping components which are circumferentially arranged around the mass pendulum, wherein the mass pendulum comprises a mass block which is hoisted on an upper cover through a mass block sling, and the annular pulley rail is hoisted on the upper cover through a plurality of pulley rail slings and surrounds the periphery of the mass block in the horizontal direction at equal height;
The inertial balance assembly comprises two pulleys mounted on the annular pulley rail and two inertial balance devices mounted at the lower cover, the two pulleys of each inertial balance assembly are oppositely arranged at two sides of the mass block, the two inertial balance devices of each inertial balance assembly are respectively positioned below the corresponding pulleys and are connected with the mass block, the two guide ropes of each inertial balance assembly can be respectively and slidably supported on the corresponding pulleys, the two pulleys of each inertial balance assembly are respectively provided with a pull rope stretched between the annular pulley rail and the lower cover, the two pull ropes of each inertial balance assembly are positioned on the same plane with the two guide ropes, and all the pulleys are uniformly distributed around the mass block along the circumferential direction;
the spring damping assemblies comprise dampers and lateral springs, and two ends of each damper and each lateral spring are respectively connected with the mass block and the cylinder body.
According to the mounting structure of the pendulum type inertial mass tuned mass damper, the mass block is hung on the upper cover through the mass block sling, and the annular pulley rail is arranged at the equal height of the mass block through the pulley rail sling, so that the annular pulley rail and the tower can be prevented from swinging together, and the mass block and the annular pulley rail can move relatively;
The mass block is connected with the inertial device on the lower cover through a guide rope supported on the pulley, and meanwhile, a guy rope is arranged for balancing the force of the guide rope acting on the annular pulley rail to connect the pulley with the lower cover;
Because the inertial device is arranged on the lower cover, the inertial device achieves the effect of grounding at one end by utilizing the characteristic that the annular pulley rail does not swing together with the tower barrel and adopting guide rope transmission, and the mass block provides control force of reverse resonance; compared with the traditional prestress tuned mass damper, the pendulum type inertial tuned mass damper mounting structure has the advantages that the sling for suspending the mass pendulum does not need prestress, so that the fatigue damage resistance is stronger, and the service life is longer.
The second aspect of the application relates to a method for installing the pendulum inertial-to-volume tuned mass damper, which comprises the following steps:
S1, calculating parameters of a fan tower;
s2, calculating parameters of the pendulum inertial mass tuned mass damper according to the parameters of the obtained fan tower;
s3, selecting a corresponding pendulum inertial volume tuning mass damper, and mounting the pendulum inertial volume tuning mass damper on a fan tower;
The fan tower consists of a plurality of tower barrels which are connected in sequence, and the pendulum inertial volume tuning mass damper is arranged in one tower barrel positioned at the uppermost part;
In the step S1, parameters of the fan tower include a shape function of the first-order vibration of the fan tower, a generalized mass m s and a generalized stiffness k s of the fan tower;
In the step S2, the parameters of the pendulum type inertial tuned mass damper include the mass m d of the mass, the apparent mass m i of the inertial device, the suspension height h of the mass, the stiffness design value k i of the lateral spring, and the damping design value c d of the damper.
By adopting the installation method of the pendulum type inertial-energy tuned mass damper, various parameters of the pendulum type inertial-energy tuned mass damper can be adaptively determined by combining parameters of a fan tower, a theoretical basis is provided for engineering design, and the pendulum type inertial-energy tuned mass damper is convenient to select, install and use.
Drawings
Fig. 1 is a schematic structural view of embodiment 1;
fig. 2 is a schematic structural view of embodiment 2;
FIG. 3 is a schematic diagram of a rack and pinion inertial device;
FIG. 4 is a schematic structural view of a wind turbine tower;
FIG. 5 is a schematic diagram of an equivalent of an actual wind turbine tower as a generalized single degree of freedom architecture;
FIG. 6 shows the variation law of the power amplification factor with the frequency ratio;
FIG. 7 is a graph of wind load time course;
FIG. 8 is a graph of wind load spectrum;
FIG. 9 is a graph of tower top velocity response;
FIG. 10 is a graph of tower top acceleration response;
FIG. 11 is a graph of the power amplification factor amplitude versus pendulum mass variation law;
fig. 12 is a graph showing the variation law of the amplitude of the dynamic amplification coefficient with the apparent mass of inertia.
Detailed Description
The invention is further described below with reference to examples and figures.
Example 1:
As shown in fig. 1 and 3, a mounting structure of a pendulum type inertial-volume tuned mass damper mainly includes a tower 1 and a pendulum type inertial-volume tuned mass damper mounted in the tower 1. Wherein, the tower 1 is a tower 1 at the highest position of the fan tower.
The tower 1 comprises a cylindrical body 1a with a cylindrical structure, and an upper cover 1b and a lower cover 1c respectively covering the upper end and the lower end of the cylindrical body 1a, wherein the upper cover 1b and the lower cover 1c preferably adopt a flange structure (not shown in the figure), so that reliable connection between adjacent towers 1 can be ensured, and the cable and equipment can be conveniently passed through.
In this embodiment, the pendulum type inertial volume tuning mass damper comprises a mass pendulum 3, an annular pulley rail 4, a set of inertial volume balancing components and two sets of spring damping components circumferentially arranged around the mass pendulum 3, wherein the mass pendulum 3 comprises a mass block 3a which is hoisted on an upper cover 1b through a mass block sling 3b, the annular pulley rail 4 is hoisted on the upper cover 1b through a plurality of pulley rail slings 8, and the annular pulley rail 4 surrounds the periphery of the mass block 3a in the horizontal direction and is arranged at the same height as the mass block 3 a.
The inertial balance components comprise two pulleys 5 arranged on the annular pulley rail 4 and two inertial devices 7 arranged at the lower cover 1c, the two pulleys 5 of the inertial balance components are oppositely arranged at two sides of the mass block 3a, the two inertial devices 7 of the inertial balance components are respectively positioned below the corresponding pulleys 5 and are respectively connected with the mass block 3a, the two guide cables 9 of the inertial balance components can be respectively and slidably supported on the corresponding pulleys 5, and a pull cable 10 stretched between the annular pulley rail 4 and the lower cover 1c is arranged beside the two pulleys 5 of each inertial balance component, namely: the cable 10 provides a continuous pulling force to the annular pulley rail 4, so that the force of the pulley 5 acting on the annular pulley rail 4 can be balanced, and the annular pulley rail 4 is prevented from moving horizontally. And, two guys 10 and two guide ropes 9 of inertial balance subassembly are in the coplanar, make the application of force of each guy 10 more balanced, two pulleys 5 along circumference evenly distributed in the periphery of quality piece 3a, namely: two pulleys 5 are symmetrically arranged on both sides of the mass 3 a.
The spring damping assembly comprises a damper 11 and a lateral spring 12, and both ends of each damper 11 and each lateral spring 12 are respectively connected with the mass block 3a and the cylinder body 1 a.
Therefore, the mass 3a is suspended on the upper cover 1b by the mass slings 3b, and the annular pulley rail 4 is provided at the equal height of the mass 3a by the pulley rail slings 8, so that the annular pulley rail 4 and the tower 1 can be prevented from swinging together, and the mass 3a and the annular pulley rail 4 can move relatively. The mass 3a is connected to the inertial device 7 on the lower cover 1c via a guide cable 9 supported on the pulley 5, and a cable 10 is provided to connect the annular pulley rail 4 to the lower cover 1c and in close proximity to the pulley 5 in order to balance the force of the guide cable 9 acting on the annular pulley rail 4. Because the inertial device 7 is arranged on the lower cover 1c, the inertial device 7 achieves the effect of grounding one end by utilizing the guide rope 9 by utilizing the characteristic that the annular pulley rail 4 does not swing together with the tower 1, and meanwhile, the mass block 3a provides a control force of reverse resonance, and meanwhile, the inertial device 7 has a mass amplification effect, so that the pendulum inertial tuned mass damper can effectively adjust the inertial characteristic of the structure and absorb vibration energy on the premise of not obviously increasing the mass of the mass pendulum 3a, and realizes light weight design; and compared with the prestress tuned mass damper, the pendulum type inertial-to-volume tuned mass damper mounting structure has the advantages that the sling for suspending the mass pendulum does not need prestress, so that the fatigue damage resistance is stronger, and the service life is longer.
Wherein, the damper 11 plays the effect of providing damping to the swing of the mass 3a, and the side direction spring 12 plays the effect of adjusting the frequency of the mass pendulum 3, owing to be provided with the side direction spring 12, the length of the mass sling 3b freely sets up according to specific use, and flexibility is high. In addition, the damper 11 and the lateral spring 12 of each group of spring damping assemblies are adjacently arranged, so that a better matching effect can be achieved.
Referring to fig. 3, the inertial device 7 is preferably a rack and pinion inertial device, which includes a rack 7a, a flywheel 7b, and a gear set driven between the rack 7a and the flywheel 7b, and the rack 7a is connected to a corresponding guide rope 9.
When the rack 7a moves relatively to the inertial device 7 under the action of the guide rope 9, the rack 7a can be converted into rotation of the flywheel 7b through the gear set.
Specifically, the gear set includes a first gear 7c engaged with the rack gear 7a, a second gear 7d rotated in synchronization with the first gear 7c, and a third gear 7e rotated in synchronization with the flywheel 7b, the second gear 7d being engaged with the third gear 7e, wherein the outer diameters of the first gear 7c and the third gear 7e are each smaller than the outer diameter of the second gear 7 d.
Assuming that the radius of the first gear 7c is r 1, the radius of the second gear 7d is r 2, the radius of the third gear 7e is r 3, the moment of inertia of the flywheel 7b is I, and the acceleration of the connection point of the rack 7a and the guide rope 9 isThe acceleration of the end of the inertial device 7 away from the rack 7a is/>The output forces at the two ends of the inertial device 7 are as follows:
In connection with newton's second law, from the above equation, the apparent mass m in of the inertial device 7 is:
From the above equation, it is known that the apparent mass m in of the inertial device 7 is far greater than the actual mass thereof due to the conversion of the physical mass to the moment of inertia, and by the amplification of the gear ratio, which is the root cause of the mass amplification effect thereof.
The damper 4 is preferably a viscous damper, which not only can provide stable and reliable additional damping, but also can play a role in guiding and limiting, and can also be used as a composite vibration reduction 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 large vibration.
Example 2:
Referring to fig. 2 and 3, the structure of the present embodiment is substantially the same as that of embodiment 1, except that: the pendulum type inertial volume tuning mass damper comprises two inertial volume balancing assemblies and more spring damping assemblies.
Through setting up two sets of inertial volume balance components, can realize the shock attenuation in two directions (x direction and y direction) to obtain better shock attenuation effect. Likewise, more spring damping assemblies can provide more reliable damping of the oscillation of the mass 3a and ensure stability of the frequency of the mass pendulum 3.
Example 3:
Referring to fig. 1-5, a method for installing a pendulum inertial tuned mass damper according to embodiment 1 or embodiment 2 is performed according to the following steps:
S1, calculating parameters of the fan tower.
The fan tower is composed of a plurality of tower barrels 1 which are connected in sequence, and a pendulum inertial volume tuning mass damper is arranged in one tower barrel 1 positioned at the uppermost part. The nacelle 2 is mounted on top of a wind turbine tower, and the blades 6 are rotatably mounted on the nacelle 2.
The parameters of the wind turbine tower include a shape function of the first order vibration of the wind turbine tower, the generalized mass m s and the generalized stiffness k s of the wind turbine tower.
Specifically, step S1 includes the steps of:
S11, simplifying a fan tower into an equivalent single-degree-of-freedom system dynamics model of the fan tower:
Simplifying a fan tower into a cantilever beam structure, taking the bottom surface center point of the fan tower as a coordinate system origin, taking the vertical direction of the fan tower as a z axis, taking the downwind direction of a wind turbine as an x axis, taking the crosswind direction of the wind turbine as a y axis, taking the concentrated mass of a cabin 2 and a blade 6 positioned at the top of the fan tower as M, taking the total height of the fan tower as H, taking the mass density M (z) of the fan tower, and taking the bending rigidity EI (z) of the fan tower along the z axis direction;
s12, obtaining a shape function of first-order vibration of the tower according to the step S11:
In the formula (1), t represents time, the unit of t is s, x (z, t) represents displacement of a z section at the time t, and x (H, t) represents displacement of the top of the fan tower at the time t.
The deflection under the concentrated load of the free end of the cantilever beam of the material mechanics can be known:
In the formula (2), P represents concentrated force, the unit is N, and EI represents bending rigidity of a section of the fan tower;
substitution of formula (2) into formula (1) yields:
S13, calculating to obtain generalized mass m s and generalized rigidity k s of the fan tower:
According to the generalized distribution flexibility theory, the generalized mass m s and the generalized stiffness k s are expressed as:
In the formula (4), the unit of the generalized mass m s is kg, the unit of the generalized rigidity k s is N/m, m (z) represents the distributed mass of the fan tower along the z-axis direction, the unit of m (z) is kg/m, g represents the gravitational acceleration, the unit of g is m/s 2, The shape function value of the top of the fan tower is shown as 1.
S2, calculating parameters of the pendulum inertial mass tuned mass damper according to the obtained parameters of the fan tower.
In step S2, the parameters of the pendulum type inertial mass tuned mass damper include the mass m d of the mass 3a, the apparent mass m i of the inertial mass device 7, the suspension height h of the mass 3a, the stiffness design value k i of the lateral spring 12, and the damping design value c d of the damper 11.
Specifically, step S2 includes the steps of:
S21, calculating to obtain the mass m d of the mass block 3a of the pendulum inertial-energy tuned mass damper:
md＝μms (5)
In the formula (5), mu is an intermediate parameter, the value range of mu is 1% -3%, and the unit of the mass m d of the mass block 3a is kg;
s22, calculating the suspension height h of the mass block 3a of the pendulum type inertial-energy 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 3a to the top of the fan tower, the unit of h is m, the unit of h 'represents the distance from the nearest lower cover 1c to the top of the fan tower, and the unit of h' is m;
s23, calculating to obtain lateral rigidity k d of a mass block 3a of the pendulum type inertial-energy tuned mass damper:
S24, calculating to obtain the apparent mass m in of the inertial device 7 of the pendulum inertial tuned mass damper:
min＝εms (8)
In the formula (8), epsilon is an intermediate parameter, and is determined according to an economical principle, and the smaller epsilon is more economical on the premise of ideal control effect;
S25, calculating to obtain a stiffness design value k i of the lateral spring 12 of the pendulum type inertial energy tuning mass damper:
According to the structural dynamics principle and a dynamics analysis model of the fan tower and the pendulum inertial volume tuned mass damper, a motion equation of the system is obtained:
In the formula (9), the amino acid sequence of the compound, Shape function value corresponding to the installation height of the inertial device 7,/>For a steel low damping fan tower, for simplicity of calculation, c s＝0,Feff (t) is usually taken to represent the equivalent generalized load, c d represents the damping coefficient, x s (t) represents the top displacement of the fan tower, and x d (t) represents the displacement of the mass 3 a;
According to the formula (9) and the fixed point theory, the stiffness design value of the lateral spring 12 of the pendulum type inertial-volume tuned mass damper is obtained as follows:
In the formula (10), sigma represents an intermediate parameter, which is expressed as
S26, calculating the self-oscillation frequency omega s of the tower (1) and the self-oscillation frequency omega d of the pendulum inertial volume tuned mass damper:
Assuming that the form of F eff (t) is sinusoidal, this can be expressed as:
Feff(t)＝Psin(ωt) (12)
In the formula (12), P represents a sinusoidal load amplitude, and omega represents a load frequency;
s27, calculating a power amplification factor R, substituting the formula (12) into the formula (9), and solving a motion equation of the system to obtain the power amplification factor R of the system:
In the formula (13), ζ represents the damping ratio of the pendulum type inertial volume tuned mass damper, α represents the ratio of the self-vibration frequency of the pendulum type inertial volume damper to the self-vibration frequency of the tower 1, β represents the ratio of the external load frequency to the self-vibration frequency of the tower 1, and η represents the ratio of the total stiffness of the pendulum type inertial volume tuned mass damper to the generalized stiffness of the tower 1;
wherein, the expressions of xi and eta are respectively:
S28, solving a left branch resonance point abscissa beta P and a right branch resonance point abscissa beta Q corresponding to the amplitude of the power amplification factor R:
in the formula (15), τ represents an intermediate parameter, which is expressed as
S29, solving a damping design value c d of a damper 11 of the pendulum type inertial volume tuned mass damper:
Taking the square of R 2 on both sides of equation (13), taking the derivative of R 2 about beta 2, and substituting beta=beta P and beta=beta Q into the formula to make the derivative equal to zero, thus obtaining the square of the damping ratio of the resonance point of the left branch And the right branch resonance point damping ratio squared/>Is represented by the expression:
For a pair of And/>After averaging, the square root of the arithmetic is opened to obtain the design damping ratio ζ opt:
substituting (17) into equation (14) to obtain a damping design value c d of the damper (11):
cd＝2ξoptminωd (18)
In the expression (18), the unit of the damping design value c d is N/(m/s).
S3, selecting a corresponding pendulum inertial volume tuned mass damper, and mounting the pendulum inertial volume tuned mass damper on a fan tower.
Specifically, on the basis of the parameters of the basic fan tower, the mass m d of the mass block 3a of the pendulum inertial mass damper, the apparent mass m i of the inertial mass device 7, the suspension height h of the mass block 3a, the stiffness design value k i of the lateral spring 12, and the damping design value c d of the damper 11 are determined. The pendulum type inertial volume tuned mass damper is arranged on the fan tower, so that an excellent damping effect can be achieved on the fan tower structure.
Comparative example 1:
The vibration reduction effect of a fan provided with a pendulum type inertial volume tuned mass damper (PTMDI for short) is analyzed by taking a fan of a certain 5MW as a research object. The height of the tower of the fan from the ground is 87.6m, the basic diameter of the tower cylinder 1 is 6m, the thickness is 0.027m, the top diameter is 3.87m, the thickness is 0.019m, the elastic modulus is 210GPa, the shear modulus is 80.8GPa, and the density is 8500kg/m 3. The mass of blade 6 is 110000kg, the mass of nacelle 2 is 240000kg, and the mass and stiffness distribution of the distributed tower are shown in Table 1.
Table 1 parameters of a 5MW fan tower
The generalized mass m s＝4.13×105 kg of the generalized single-degree-of-freedom system is obtained through calculation, the generalized stiffness k s＝1.91×106 N/m is obtained, and the first-order frequency f s =0.343 Hz is obtained.
The control effect of the PTMD under three different additional mass counterweights is calculated by comparing the PTMD with PTMDI. Wherein, the standard counterweight takes 2% of the generalized mass of the fan, and the inertial apparent mass is the same as the standard counterweight. The calculation results of the optimal frequency ratio alpha opt and the optimal damping ratio zeta opt of PTMD and PTMDI under different working conditions are shown in table 2.
TABLE 2 calculation results of optimal frequency ratio and damping ratio
Substituting the relevant parameters of the standard counter weight in table 2 into calculation to obtain the change rule of the power amplification factor of the additional PTMDI fan along with the frequency ratio beta, and comparing the change rule with the power amplification factor of the additional PTMD fan, as shown in fig. 6.
As can be seen from fig. 6, in the resonance frequency range, the power amplification coefficient of PTMDI system is obviously reduced compared with that of PTMD system, and the effect of the power amplification coefficient are basically the same outside the resonance frequency range, which proves that the inertial device can effectively enhance the capacity of the mass block to relieve the resonance response of the fan.
By carrying out dynamic analysis on the additional PTMD fan by the same method, the power amplification factor R of the tower top displacement of the additional PTMD fan can be obtained as follows:
The physical meaning of each parameter in the formula (13) is the same, and compared with the formula (13), PTMDI is that the mass ratio of the vibration damper is changed from mu to mu+epsilon due to the addition of the inertial device, so that the additional physical mass of the mass block is indirectly amplified, and the peak value of the power amplification coefficient is obviously reduced.
In order to verify the light control effect of the inertial device, three different groups of wind loads are selected to calculate the displacement, the speed and the acceleration response of the tower top under three different additional masses. The time course and spectrum of wind load are shown in fig. 7 and 8.
From the above graph, the three groups of wind loads have larger and dense energy distribution at the self-vibration frequency of 0.343Hz of the fan, can excite the resonance response of the tower structure, and can effectively test the vibration reduction effect of the vibration control device. Limiting to the article, taking the wind load 1 as an example, the dynamic response time profile of the wind turbine at 20% additional mass is shown in fig. 9 and 10.
As can be seen from fig. 9 and 10, PTMDI achieves a better vibration control effect with a smaller physical mass than the conventional PTMD. Solving the displacement, the speed and the acceleration response of the tower top under the three different additional masses by adopting a Wilson-theta method, respectively measuring PTMDI performance improvement efficiency by using a peak value and a root mean square of the response, and defining parameters lambda and χ:
In the above formula, |Γ PTMD|max and Γ PTMDI|max represent the peak top response values of the PTMD fans and PTMDI fans, respectively, and Γ PTMD|RMS and Γ PTMDI|RMS represent the root mean square of the top response values of the PTMD fans and PTMDI fans, respectively.
The performance improvement efficiency of PTMDI on the tower top displacement, speed and acceleration was calculated by using the conventional PTMD device as a reference object, and the calculation results are shown in table 3.
TABLE 3 PTMDI calculation of Performance improvement efficiency
Comparing the performance improvement efficiency of PTMDI with the different additional masses in table 3, it can be seen that the performance improvement of the PTMD by the inertial device is more remarkable with the decrease of the additional mass (self physical mass) of the PTMD. Therefore, PTMDI can still exert very stable wind-induced vibration response inhibition capability under the condition of small additional physical mass, and the inhibition of the vibration of the tower can be realized by adopting a lightweight damper.
By changing the size of the additional mass (mass pendulum mass), the change rule of the power amplification coefficient amplitude values of the PTMD system and the PTMDI system under the change of the additional mass (mass pendulum mass) is shown in fig. 11.
As can be seen from fig. 11, the power amplification amplitude of the PTMD system increases significantly as the additional mass decreases compared to the PTMDI system. Under the same condition, when the additional mass of the PTMDI system is reduced by 80%, the power amplification amplitude is only changed by 20%. The slope of the two curves and the variation range of the amplitude of the power amplification coefficient can be known, the additional inertia capacity device is beneficial to weakening the influence of the additional mass reduction on the vibration control effect, and the dependence of the vibration control efficiency of the traditional PTMD on the physical quality of the PTMD is obviously reduced.
The variation rule of the power amplification coefficient amplitude of the additional PTMDI fan is obtained by selecting the additional mass with different working conditions and changing the apparent mass of the inertia capacity, and is shown in figure 12.
As can be seen from fig. 12, as the apparent mass of the inertial mass increases, the power amplification coefficients under the three working conditions all show a decreasing trend, and the trend is gradually slowed down, so that the inertial mass lifting effect is more obvious under the condition of small additional mass. In the practical engineering application, smaller additional mass and proper inertial apparent mass can be selected for design according to specific conditions and economical principles.
Therefore, aiming at the problem of larger mass of the mass block of the traditional PTMD, the structure of the current main stream fan tower is combined, and the inertia capacity device is combined with the PTMD through related components to form PTMDI, so that the lightweight wind-induced vibration response control is realized. The fan with the attached PTMDI is simplified into a two-degree-of-freedom system, a motion equation is established through a virtual work principle, and a design expression of the optimal frequency ratio and the damping ratio of PTMDI is deduced based on a fixed point theory. And the effectiveness of PTMDI MW fans is verified by taking a certain 5MW fan as an example, and the influence of the additional mass and the apparent inertial mass on the vibration control effect of the additional mass and the apparent inertial mass is verified:
1. Under the same additional mass condition, PTMDI has better control effect than PTMD, and when the additional mass and the apparent inertial mass are both balanced, the PTMD power amplification factor can be reduced by about 20 percent compared with PTMD.
2. As can be seen from comparing the power amplification coefficient expressions of PTMD and PTMDI, after the inertial device is added, the effective mass ratio of the vibration reduction system is increased, and the high-efficiency inhibition of the vibration of the tower can be realized after the damper is light.
3. The inertial device is beneficial to weakening the influence of additional mass reduction on the vibration control effect, and remarkably reduces the dependence of the traditional PTMD control efficiency on the mass ratio of the self mass to the fan.
4. Compared with the condition of larger additional mass, the effect of the inertial device on the small additional mass is improved more obviously, and the larger the apparent mass of the inertial device is, the better the vibration reduction effect is.
Finally, it should be noted that the above description is only a preferred embodiment of the present invention, and that many similar changes can be made by those skilled in the art without departing from the spirit and scope of the invention as defined in the appended claims.
Claims (5)
1. The utility model provides a mounting structure of pendulum-type is used to hold tuned mass damper, includes a tower section of thick bamboo (1) and pendulum-type is used to hold tuned mass damper, a tower section of thick bamboo (1) is including barrel (1 a) that is tubular structure and upper cover (1 b) and lower cover (1 c) that cover respectively in barrel (1 a) upper and lower both ends, its characterized in that:
The pendulum type inertial volume tuning mass damper comprises a mass pendulum (3), an annular pulley rail (4), at least one set of inertial volume balancing components and at least two sets of spring damping components circumferentially arranged around the mass pendulum (3), wherein the mass pendulum (3) comprises a mass block (3 a) which is hoisted on an upper cover (1 b) through a mass block sling (3 b), and the annular pulley rail (4) is hoisted on the upper cover (1 b) through a plurality of pulley rail slings (8) and surrounds the periphery of the mass block (3 a) in the horizontal direction at equal heights;
The inertial balance assemblies comprise two pulleys (5) arranged on the annular pulley rail (4) and two inertial devices (7) arranged at the lower cover (1 c), the two pulleys (5) of each inertial balance assembly are oppositely arranged at two sides of the mass block (3 a), the two inertial devices (7) of each inertial balance assembly are respectively positioned below the corresponding pulleys (5) and are respectively connected with the mass block (3 a), the two guide ropes (9) of each inertial balance assembly can be respectively and slidably supported on the corresponding pulleys (5), the two guys (10) tensioned between the annular pulley rail (4) and the lower cover (1 c) are respectively arranged beside the two pulleys (5) of each inertial balance assembly, the two guys (10) of each inertial balance assembly are positioned on the same plane with the two guide ropes (9), and all the pulleys (5) are uniformly distributed around the mass block (3 a) along the circumferential direction;
the spring damping assembly comprises a damper (11) and a lateral spring (12), and two ends of each damper (11) and each lateral spring (12) are respectively connected with the mass block (3 a) and the cylinder body (1 a).
2. The mounting structure of a pendulum inertial mass damper of claim 1, wherein: the inertial container device (7) is a gear-rack inertial container device, the gear-rack inertial container device comprises a rack (7 a), a flywheel (7 b) and a gear set which is driven between the rack (7 a) and the flywheel (7 b), and the rack (7 a) is connected with a corresponding guide rope (9).
3. A method of installing a pendulum inertial mass damper according to claim 1 or 2, characterized by the steps of:
S1, calculating parameters of a fan tower;
s2, calculating parameters of the pendulum inertial mass tuned mass damper according to the parameters of the obtained fan tower;
s3, selecting a corresponding pendulum inertial volume tuning mass damper, and mounting the pendulum inertial volume tuning mass damper on a fan tower;
The fan tower is composed of a plurality of tower barrels (1) which are connected in sequence, and the pendulum inertial volume tuning mass damper is arranged in the tower barrel (1) positioned at the uppermost part;
In the step S1, parameters of the fan tower include a shape function of the first-order vibration of the fan tower, a generalized mass m s and a generalized stiffness k s of the fan tower;
In the step S2, the parameters of the pendulum type inertial volume tuned mass damper include the mass m d of the mass block (3 a), the apparent mass m i of the inertial volume device (7), the suspension height h of the mass block (3 a), the stiffness design value k i of the lateral spring (12) and the damping design value c d of the damper (11).
4. A method of installing a pendulum inertial mass damper according to claim 3, wherein step S1 comprises the steps of:
S11, simplifying a fan tower into an equivalent single-degree-of-freedom system dynamics model of the fan tower:
Simplifying a fan tower into a cantilever beam structure, taking the bottom surface center point of the fan tower as a coordinate system origin, taking the vertical direction of the fan tower as a z axis, taking the downwind direction of a wind turbine as an x axis, taking the crosswind direction of the wind turbine as a y axis, taking the concentrated mass of a cabin (2) and a blade (6) positioned at the top of the fan tower as M, taking the total height of the fan tower as H, taking the mass density M (z) of the fan tower, and taking the bending rigidity EI (z) of the fan tower along the z axis direction;
s12, obtaining a shape function of first-order vibration of the tower according to the step S11:
In the formula (1), t represents time, the unit of t is s, x (z, t) represents displacement of a z section at the time t, and x (H, t) represents displacement of the top of the fan tower at the time t;
the deflection under the concentrated load of the free end of the cantilever beam of the material mechanics can be known:
In the formula (2), P represents concentrated force, the unit is N, and EI represents bending rigidity of a section of the fan tower;
substitution of formula (2) into formula (1) yields:
S13, calculating to obtain generalized mass m s and generalized rigidity k s of the fan tower:
According to the generalized distribution flexibility theory, the generalized mass m s and the generalized stiffness k s are expressed as:
In the formula (4), the unit of the generalized mass m s is kg, the unit of the generalized rigidity k s is N/m, m (z) represents the distributed mass of the fan tower along the z-axis direction, the unit of m (z) is kg/m, g represents the gravitational acceleration, the unit of g is m/s 2, The shape function value of the top of the fan tower is shown as 1.
5. The method of installing a pendulum inertial mass damper according to claim 4, wherein step S2 comprises the steps of:
S21, calculating to obtain the mass m d of a mass block (3 a) of the pendulum inertial-energy tuned mass damper:
md＝μms (5)
In the formula (5), mu is an intermediate parameter, the value range of mu is 1% -3%, and the unit of the mass m d of the mass block (3 a) is kg;
S22, calculating the suspension height h of a mass block (3 a) of the pendulum type inertial-energy 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 (3 a) to the top of the fan tower, the unit of h is m, the unit of h 'represents the distance from the nearest lower cover (1 c) to the top of the fan tower, and the unit of h' is m;
s23, calculating lateral rigidity k d of a mass block (3 a) of the pendulum type inertial-energy tuned mass damper:
s24, calculating to obtain the apparent mass m in of the inertial device (7) of the pendulum inertial tuned mass damper:
min＝εms (8)
in the formula (8), epsilon is an intermediate parameter;
S25, calculating to obtain a rigidity design value k i of the lateral spring (12) of the pendulum type inertial-energy tuned mass damper:
According to the structural dynamics principle and a dynamics analysis model of the fan tower and the pendulum inertial volume tuned mass damper, a motion equation of the system is obtained:
In the formula (9), the amino acid sequence of the compound, Representing a shape function value corresponding to the installation height of the inertial device (7)/>, andFor a steel low-damping fan tower, for simplicity of calculation, c s＝0,Feff (t) is generally taken to represent equivalent generalized load, c d represents damping coefficient, x s (t) represents top displacement of the fan tower, and x d (t) represents displacement of the mass block (3 a);
according to the formula (9) and the fixed point theory, the rigidity design value of the lateral spring (12) of the pendulum type inertial-volume tuned mass damper is obtained as follows:
In the formula (10), sigma represents an intermediate parameter, which is expressed as
S26, calculating the self-oscillation frequency omega s of the tower (1) and the self-oscillation frequency omega d of the pendulum inertial volume tuned mass damper:
Assuming that the form of F eff (t) is sinusoidal, this can be expressed as:
Feff(t)＝Psin(ωt) (12)
In the formula (12), P represents a sinusoidal load amplitude, and omega represents a load frequency;
s27, calculating a power amplification factor R, substituting the formula (12) into the formula (9), and solving a motion equation of the system to obtain the power amplification factor R of the system:
In the formula (13), ζ represents the damping ratio of the pendulum type inertial volume tuned mass damper, α represents the ratio of the self-vibration frequency of the pendulum type inertial volume damper to the self-vibration frequency of the tower (1), β represents the ratio of the external load frequency to the self-vibration frequency of the tower (1), and η represents the ratio of the total stiffness of the pendulum type inertial volume tuned mass damper to the generalized stiffness of the tower (1);
wherein, the expressions of xi and eta are respectively:
S28, solving a left branch resonance point abscissa beta P and a right branch resonance point abscissa beta Q corresponding to the amplitude of the power amplification factor R:
in the formula (15), τ represents an intermediate parameter, which is expressed as
S29, solving a damping design value c d of a damper (11) of the pendulum type inertial-energy tuned mass damper:
Taking the square of R 2 on both sides of equation (13), taking the derivative of R 2 about beta 2, and substituting beta=beta P and beta=beta Q into the formula to make the derivative equal to zero, thus obtaining the square of the damping ratio of the resonance point of the left branch And the right branch resonance point damping ratio squared/>Is represented by the expression:
For a pair of And/>After averaging, the square root of the arithmetic is opened to obtain the design damping ratio ζ opt:
substituting (17) into equation (14) to obtain a damping design value c d of the damper (11):
cd＝2ξoptminωd (18)。
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