CN113700600B - Cross elastic vibration-resistant and damage-resistant device for large wind turbine blade and large wind turbine blade - Google Patents
Cross elastic vibration-resistant and damage-resistant device for large wind turbine blade and large wind turbine blade Download PDFInfo
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- CN113700600B CN113700600B CN202111128482.5A CN202111128482A CN113700600B CN 113700600 B CN113700600 B CN 113700600B CN 202111128482 A CN202111128482 A CN 202111128482A CN 113700600 B CN113700600 B CN 113700600B
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- 230000003068 static effect Effects 0.000 description 8
- 238000000034 method Methods 0.000 description 4
- KFLQGJQSLUYUBF-WOJBJXKFSA-N Phyllanthin Chemical compound C([C@H](COC)[C@@H](COC)CC=1C=C(OC)C(OC)=CC=1)C1=CC=C(OC)C(OC)=C1 KFLQGJQSLUYUBF-WOJBJXKFSA-N 0.000 description 3
- KFLQGJQSLUYUBF-PMACEKPBSA-N Phyllanthin Natural products C([C@@H](COC)[C@H](COC)CC=1C=C(OC)C(OC)=CC=1)C1=CC=C(OC)C(OC)=C1 KFLQGJQSLUYUBF-PMACEKPBSA-N 0.000 description 3
- 238000009434 installation Methods 0.000 description 3
- 230000002035 prolonged effect Effects 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000010248 power generation Methods 0.000 description 2
- 238000011160 research Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000012141 concentrate Substances 0.000 description 1
- 239000008358 core component Substances 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000002787 reinforcement Effects 0.000 description 1
- 230000009897 systematic effect Effects 0.000 description 1
Classifications
-
- 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
- F03D1/00—Wind motors with rotation axis substantially parallel to the air flow entering the rotor
- F03D1/06—Rotors
- F03D1/065—Rotors characterised by their construction elements
- F03D1/0675—Rotors characterised by their construction elements of the blades
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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
- F16F15/067—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 using only wound springs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2260/00—Function
- F05B2260/96—Preventing, counteracting or reducing vibration or noise
- F05B2260/964—Preventing, counteracting or reducing vibration or noise by damping means
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/70—Wind energy
- Y02E10/72—Wind turbines with rotation axis in wind direction
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Sustainable Energy (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Wind Motors (AREA)
Abstract
The invention relates to a cross elastic vibration-resistant and damage-resistant device for a large wind turbine blade and the large wind turbine blade, wherein the vibration-resistant and damage-resistant device comprises a support body, a first spring, a second spring, a third spring and a fourth spring, one ends of the first spring, the second spring, the third spring and the fourth spring are respectively connected to the support body, all the springs and the support body are on the same plane, the directions of the first spring and the third spring are the same, the second spring and the fourth spring are on the same straight line and are perpendicular to the first spring, and connecting pieces for connecting the inner wall of the wind turbine blade are arranged at the other ends of the first spring, the second spring, the third spring and the fourth spring. Compared with the prior art, the invention has the advantages of improving the vibration resistance and damage resistance of the blade tip part and the like.
Description
Technical Field
The invention relates to a cross elastic vibration-resistant and damage-resistant device for a large wind turbine blade and the large wind turbine blade.
Background
As the energy problem becomes more serious in the 21 st century, the use of wind energy in various countries has reached a rapid development stage. The wind turbine blade is a core component for converting wind energy into mechanical energy, and the reliability of the wind turbine blade plays a vital role in the safe operation of the wind turbine. The working environment of the wind power machine is very complex due to the fact that the wind speed and the wind direction change are not constant. The rotor is exposed to a series of complex loads such as aerodynamic loads, centrifugal loads, gravitational loads, etc. for a long period of time. The tower has its own natural frequency and the generator operates to produce a vibration frequency that can cause fatigue damage if the blade frequency resonates with any of these frequencies. One of the main factors of blade damage is that the blade resonates, which aggravates the fatigue of the blade material, and its effective service life is reduced, even if serious, the blade is damaged and broken directly. The load applied to the mechanism can be amplified due to resonance phenomenon, the machine body or the blades can be severely dithered to influence the power generation efficiency, and even the power generation efficiency is seriously damaged, so that the structural power design of the blades is particularly critical. Modal analysis is a common method for modern structural dynamic characteristic research and is also an important application of a system identification method in the field of engineering vibration. According to the research result of the inherent vibration characteristics, resonance caused by the fact that external excitation is the same as self-vibration frequency can be effectively avoided, and damage to a mechanical structure is prevented.
Many systematic studies have been made on the natural frequency and mode shape of wind turbines at home and abroad. And there is very little additional reinforcement and vibration resistance on the blade structure. The structure of the blade which is most easily damaged in the wind turbine is very necessary to strengthen, resist vibration and damage on the structure, and particularly in a complex environment, the wind turbine blade is likely to resonate with the external environment, so that the wind turbine is damaged, and the service life of the wind turbine is reduced.
Disclosure of Invention
The invention aims to provide a cross elastic vibration-resistant damage-resistant device for a large wind turbine blade and the large wind turbine blade.
The aim of the invention can be achieved by the following technical scheme:
The utility model provides a large-scale wind turbine blade cross elasticity vibration resistance and damage device, includes support body, first spring, second spring, third spring and fourth spring, and first spring, second spring, third spring and fourth spring's one end is connected to the support body respectively, and all springs and support body are on a plane, and the direction of first spring and third spring is the same, and second spring and fourth spring are on a straight line and perpendicular with first spring, all be equipped with the connecting piece that is used for connecting wind turbine blade inner wall on first spring, second spring, third spring and the other end of fourth spring.
The connecting pieces on the first spring, the second spring and the third spring are cone connecting pieces, and the connecting piece on the fourth spring is column connecting piece.
The first spring and the third spring are in a straight line.
The basic stiffness of the first spring, the second spring, the third spring and the fourth spring is 1500N/m 3--20000N/m3.
The basic stiffness of the first spring, the second spring, the third spring and the fourth spring is 10000N/m 3.
The supporting body cube,
A large wind turbine blade provided with two anti-vibration and anti-damage devices as described in any one of the above, wherein the anti-vibration and anti-damage devices are parallel to the blade cross section of the blade.
One vibration-resistant and damage-resistant device is arranged at the position of 0.47-0.5 of the relative blade height, and the other vibration-resistant and damage-resistant device is arranged at the position of 0.86-0.91 of the relative blade height.
The first spring is connected to the inner wall of the top end of the pressure surface, the third spring is connected to the inner wall of the top end of the suction surface, and the second spring is connected to the inner wall of the leading edge of the phyllanthin.
The fourth spring is connected to the pressure surface inner wall.
Compared with the prior art, the invention has the following beneficial effects:
1) Each wind turbine blade is provided with two cross elastic vibration-resistant and damage-resistant devices, and through modal analysis, the natural frequency of the wind turbine blade is improved and is higher than most frequencies in the environment, so that the possibility of damage of the wind turbine caused by resonance of the wind turbine blade is reduced.
2) The wind turbine blade with the cross elastic vibration-resistant and damage-resistant device is provided, and the mode analysis shows that the maximum deformation of the wind turbine blade is greatly reduced when the wind turbine blade resonates, so that the wind turbine blade has stronger resonance resistance, the damage of the resonance to the wind turbine blade is reduced, and the service life of the wind turbine is prolonged.
3) Compared with the wind turbine blade without the cross elastic vibration-resistant and damage-resistant device, the maximum deformation of the wind turbine blade mode without the cross elastic vibration-resistant and damage-resistant device is located at the blade tip, and the maximum deformation of the wind turbine blade mode with the cross elastic vibration-resistant and damage-resistant device moves from the blade tip to the middle of the blade. The most fragile blade tip is enhanced in vibration resistance and damage resistance, and the service life of the wind turbine is prolonged.
Drawings
FIG. 1 is a schematic view of a 5MW wind turbine blade incorporating a cross elastic vibration and damage resistant device of the present invention;
FIG. 2 is a schematic view of a cross-section of a blade;
FIG. 3 is a schematic view of an installation of an anti-vibration and anti-loss device;
FIG. 4 is a graph showing the comparison of the maximum deflection of the mode frequency and the first third-order mode in different spring base stiffness and the cross vibration and damage resistance device without being added in the static state of the wind turbine, wherein (a) is a graph showing the comparison of the first-order mode frequency and the first-order mode frequency of the cross vibration and damage resistance device without being added in different spring base stiffness in the static state of the wind turbine, (b) is a graph showing the comparison of the second-order mode frequency and the second-order mode frequency of the cross vibration and damage resistance device without being added in different spring base stiffness in the static state of the wind turbine, and (c) is a graph showing the comparison of the third-order mode frequency and the third-order mode frequency of the cross vibration and damage resistance device without being added in the static state of the wind turbine; (d) A line graph is formed by comparing the maximum deformation of the front third-order mode under different spring rates of the wind turbine in a static state with the maximum deformation of the front third-order mode without the cross vibration-resistant and damage-resistant device;
FIG. 5 is a graph showing the comparison of the maximum deformation of the mode frequency and the first third-order mode with the cross vibration and damage resistance device not added under the rated working state of the wind turbine, wherein (a) is a graph showing the comparison of the first-order mode frequency and the first-order mode frequency without the cross vibration and damage resistance device added under the rated working state of the wind turbine, (b) is a graph showing the comparison of the second-order mode frequency and the second-order mode frequency without the cross vibration and damage resistance device added under the rated working state of the wind turbine, (c) is a graph showing the comparison of the third-order mode frequency and the third-order mode frequency without the cross vibration and damage resistance device added under the rated working state of the wind turbine, and (d) is a graph showing the comparison of the maximum deformation of the first third-order mode frequency and the maximum deformation of the third-order mode without the cross vibration and damage resistance device added under the rated working state of the wind turbine;
FIG. 6 is a plot of the maximum deformation versus leaf height position of a spring at 10000N/m 3 base stiffness for a wind turbine at rest or nominal operating conditions versus an unadditized cross vibration and damage resistant device.
Wherein: 1. the blade comprises a blade main body, 2, vibration-resistant and damage-resistant devices, 3, vibration-resistant and damage-resistant devices, 4, 5, 7, cone connecting pieces, 6, a first spring, 8, a second spring, 9, column connecting pieces, 10, a supporting body, 11, phyllin, 12, a third spring, 13, a fourth spring, A, phyllin front edge inner wall, B, suction surface top end inner wall, C, phyllin rear edge inner wall, D, phyllin front edge inner wall and connecting lines of a phyllin front edge inner wall, a pressure surface top end inner wall and a suction surface top end inner wall are perpendicularly intersected with a pressure surface one-point inner wall, E and a pressure surface top end inner wall.
Detailed Description
The invention will now be described in detail with reference to the drawings and specific examples. The present embodiment is implemented on the premise of the technical scheme of the present invention, and a detailed implementation manner and a specific operation process are given, but the protection scope of the present invention is not limited to the following examples.
The cross elastic vibration-resistant and damage-resistant device for the large wind turbine blade comprises a supporting body 10, a first spring 6, a second spring 8, a third spring 12 and a fourth spring 13, wherein one ends of the first spring 6, the second spring 8, the third spring 12 and the fourth spring 13 are respectively connected to the supporting body 10, all the springs and the supporting body are on the same plane, the directions of the first spring 6 and the third spring 12 are the same, the second spring 8 and the fourth spring 13 are on the same straight line and are perpendicular to the first spring 6, and connecting pieces for connecting the inner wall of the wind turbine blade are arranged at the other ends of the first spring 6, the second spring 8, the third spring 12 and the fourth spring 13. The support body 10 is square.
In some embodiments, the connections on the first, second and third springs 6, 8, 12 are tapered connections and the connection on the fourth spring 13 is a post connection 9.
In some embodiments, the first spring 6 and the third spring 12 are in a straight line.
In some embodiments, the base stiffness of the first spring 6, the second spring 8, the third spring 12 and the fourth spring 13 is 1500N/m 3--20000N/m3. In one embodiment, the base stiffness of the first spring 6, the second spring 8, the third spring 12 and the fourth spring 13 is 10000N/m 3.
A large-scale wind turbine blade is provided with two vibration-resistant and damage-resistant devices, and the vibration-resistant and damage-resistant devices are parallel to the blade section of the blade. One vibration-resistant and damage-resistant device is arranged at the position of 0.47-0.5 of the relative blade height, and the other vibration-resistant and damage-resistant device is arranged at the position of 0.86-0.91 of the relative blade height. The first spring 6 is connected to the pressure surface tip inner wall, the third spring 12 is connected to the suction surface tip inner wall, and the second spring 8 is connected to the phyllanthin leading edge inner wall. The fourth spring 13 is connected to the pressure surface inner wall.
Specifically, fig. 1 shows a schematic structural view of a horizontal axis wind turbine blade body 1 and cross elastic vibration and damage resistant devices 2 and 3 of the present invention, and two cross elastic vibration and damage resistant devices are disposed on one wind turbine blade. Two cross elastic vibration-resistant and damage-resistant devices are respectively arranged at the positions of 0.48 and 0.89 of the height of the opposite blade. The installation method of the two devices is the same.
Fig. 2 and 3 show a schematic view of the leaf element of the inventive installation cross elastic anti-vibration and anti-damage device, which consists of four springs 6, 8, 12, 13, a support body 10, three cone connections 4, 5, 7 and a column connection 9. The outer profile curve ABC of the phyllin is a suction surface, and the outer profile curve AEC of the phyllin is a pressure surface. The chord line is a straight line AC between the front edge point A and the rear edge point C, the pressure surface top end inner wall E is the point at which the pressure surface inner wall is farthest from the chord line in a vertical manner, and the suction surface top end inner wall B is the point at which the suction surface inner wall is farthest from the chord line in a vertical manner. Wherein the three cone connectors 4, 5 and 7 are respectively positioned on the inner wall B at the top end of the suction surface of the wind turbine blade, the inner wall E at the top end of the pressure surface and the inner wall A at the front edge of the phyllanthin. A perpendicular to BE at point A intersects the pressure surface at point D on the inner wall. AD is perpendicular to BE, and D is a point on the inner wall of the pressure surface. A post connection 9 is provided to connect the spring end to the inner wall D. The springs 6, 8, 12, 13 are in a free state, either under compression or under tension, and the spring base stiffness is 1500N/m 3--20000N/m3. Wherein the base stiffness is defined as the pressure value that produces normal deformation of the base unit. The support 10 is 40×40 square of x40 mm. Wherein the three cone connectors 4, 5, 7 are smoothly connected with the inner wall of the wind turbine blade, and the springs 6, 8, 12, 13 are also smoothly and fixedly connected with the four connectors 4, 5, 7, 9 and the supporting body 6.
Referring to fig. 3, the springs 6, 8, 12, 13 are arranged in a cross circumferential direction, so that when the wind turbine blade resonates, the springs 6, 8, 12, 13 apply a tensile force or a compressive force to the blade to be distorted, thereby preventing the blade from being distorted due to resonance, improving the resonance frequency, reducing the possibility of resonance with the outside, and prolonging the service life. At the same time, it is also important that the basic stiffness of the springs 6, 8, 12, 13 is at a suitable value, and if the basic stiffness of the springs 6, 8, 12, 13 is too low, the springs 6, 8, 12, 13 arranged circumferentially in a cross will be deformed by lateral twisting when resonance occurs, which causes the cross elastic anti-vibration and anti-damage device to be destroyed. If the base stiffness of the springs 6, 8, 12, 13 is too high, the springs 6, 8, 12, 13 will exert little tension or compression on the blade to be deformed by the twisting, and the amplitude of the twisting of the wind turbine will be very large. Finding the appropriate value of the base stiffness of the springs 6, 8, 12, 13 is also of exceptional importance for the invention.
The wind turbine blade with and without cross elastic vibration-proof and damage-proof device is subjected to modal analysis under the selection conditions of static and rated working running speeds 1.266rad/s and different spring basic stiffness. The front third order modal frequencies may be considered as the natural frequencies of the wind turbine blade, since the front third order concentrates the main energy of the vibrations. And as shown in fig. 4 and 5, the comparison line graph of the front third-order modal frequency and the maximum deformation of the wind turbine under different spring stiffness and the non-mounted cross vibration-resistant and damage-resistant device under the normal working state of the wind turbine and the comparison line graph of the front third-order modal frequency and the maximum deformation of the wind turbine under different spring stiffness and the non-mounted cross vibration-resistant and damage-resistant device are respectively shown. From modal analysis calculations, it was found that when the spring base stiffness was below 1500N/m 3, the spring would experience lateral torsional failure at resonance. When the basic stiffness of the spring is higher than 20000N/m 3, the wind turbine is distorted too much. The device according to the invention is therefore suitable for use with a spring base stiffness of between 1500N/m 3--20000N/m3. Through (a), (b) and (c) of fig. 4 and (a), (b) and (c) of fig. 5, it is found that the front third-order modal frequency of the wind turbine without the cross vibration and damage resisting device is about 0.6HZ when the wind turbine is rotating and static, and the front third-order modal frequency of the wind turbine without the cross vibration and damage resisting device is about 2.5-2.7HZ when the wind turbine is rotating and static under different basic rigidity. Therefore, when the cross vibration-resistant and damage-resistant device is not added, the natural frequency of the wind turbine is about 0.6HZ, and when the cross elastic vibration-resistant and damage-resistant device is added, the natural frequency of the wind turbine is changed into 2.5-2.7HZ under different basic rigidities, and the natural frequency is improved by about 77%. Meanwhile, the third-order modal frequency in front of the wind turbine is increased along with the increase of the basic rigidity, and the increase amplitude is small. It is found from fig. 4 (d) and fig. 5 (d) that the maximum deflection of the stationary wind turbine blade at resonance is reduced by about 26% -40%. The maximum deformation of the wind turbine blade is reduced by about 20-40% during rated operation. This reduces the possibility of substantial damage to the wind turbine blade due to resonance and increases the service life of the wind turbine.
In addition, because the application range of the spring base stiffness is large, the spring is analyzed under 10000N/m 3 base stiffness, and the same conclusion is drawn under other applicable base stiffness conditions. FIG. 6 is a plot of the maximum deformation versus leaf height for a spring at 10000N/m 3 base stiffness for a wind turbine at rest or nominal operating conditions versus an unconnected cross anti-vibration and anti-loss device. It can be seen that the maximum deformation of the blade moves from the tip position to the middle of the blade when the cross vibration-resistant and damage-resistant device is additionally arranged and compared with the blade which is not additionally arranged, so that the fragile tip of the blade is protected when the blade resonates, and the service life of the wind turbine is prolonged.
The foregoing is merely a preferred embodiment of the present invention, and the present invention is not limited to the above examples, but is not limited to the scope of the present invention, and it will be understood that other modifications and variations, which are directly derived or conceivable by those skilled in the art, should be considered to be included in the scope of the present invention without departing from the spirit and concept of the present invention.
Claims (5)
1. The large-scale wind turbine blade is characterized in that two cross elastic vibration-resistant and damage-resistant devices are arranged on the large-scale wind turbine blade, the cross elastic vibration-resistant and damage-resistant devices are parallel to the blade section of the blade, the cross elastic vibration-resistant and damage-resistant devices comprise a supporting body (10), a first spring (6), a second spring (8), a third spring (12) and a fourth spring (13), one ends of the first spring (6), the second spring (8), the third spring (12) and the fourth spring (13) are respectively connected to the supporting body (10), all the springs and the supporting body are on the same plane, the directions of the first spring (6) and the third spring (12) are the same, the second spring (8) and the fourth spring (13) are on the same straight line and are perpendicular to the first spring (6), and connecting pieces for connecting the inner walls of the wind turbine blade are arranged at the other ends of the first spring (6), the second spring (8), the third spring (12) and the fourth spring (13);
the connecting pieces on the first spring (6), the second spring (8) and the third spring (12) are cone connecting pieces, and the connecting piece on the fourth spring (13) is a column connecting piece (9);
The first spring (6) and the third spring (12) are in a straight line;
The outer profile curve ABC of the phyllostatin is a suction surface, the outer profile curve AEC of the phyllostatin is a pressure surface, a chord line is a straight line AC between a front edge point A and a rear edge point C, the inner wall E of the top end of the pressure surface is a point at which the inner wall of the pressure surface is farthest from the chord line, the inner wall B of the top end of the suction surface is a point at which the inner wall of the suction surface is farthest from the chord line, three cone connectors are respectively positioned on the inner wall B of the top end of the suction surface, the inner wall E of the top end of the pressure surface and the inner wall of the front edge point A and are connected with BE, a perpendicular line crossing the point A and the pressure surface crosses the inner wall at a point D, and the column connector (9) is connected with the end part of the fourth spring (13) and the point D.
2. The large wind turbine blade according to claim 1, wherein one cross elastic anti-vibration and anti-damage device is arranged at a height of 0.47-0.5 relative to the blade, and the other cross elastic anti-vibration and anti-damage device is arranged at a height of 0.86-0.91 relative to the blade.
3. A large wind turbine blade according to claim 1, wherein the base stiffness of the first (6), second (8), third (12) and fourth (13) springs is 1500N/m 3--20000N/m3.
4. A large wind turbine blade according to claim 3, wherein the base stiffness of the first (6), second (8), third (12) and fourth (13) springs is 10000N/m 3.
5. A large wind turbine blade according to claim 1, wherein the support body (10) is a cube.
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| CN202111128482.5A CN113700600B (en) | 2021-09-26 | 2021-09-26 | Cross elastic vibration-resistant and damage-resistant device for large wind turbine blade and large wind turbine blade |
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| CN113700600B true CN113700600B (en) | 2024-06-28 |
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| CN217602833U (en) * | 2021-09-26 | 2022-10-18 | 上海电力大学 | Wind turbine blade damping device and large wind turbine blade comprising same |
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| WO2011029439A1 (en) * | 2009-09-08 | 2011-03-17 | Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e. V. | Model-based method for monitoring the condition of rotor blades |
| DE102017107912A1 (en) * | 2017-04-12 | 2018-10-18 | Wobben Properties Gmbh | Vibration damping of a wind turbine tower |
| CN111810355A (en) * | 2020-08-05 | 2020-10-23 | 中国华能集团清洁能源技术研究院有限公司 | A kind of horizontal axis wind turbine blade torsional vibration damping device and method |
| CN113090445B (en) * | 2021-04-29 | 2022-06-21 | 中国华能集团清洁能源技术研究院有限公司 | Resistance adding device and method for blade structure of horizontal-axis wind generating set |
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| CN217602833U (en) * | 2021-09-26 | 2022-10-18 | 上海电力大学 | Wind turbine blade damping device and large wind turbine blade comprising same |
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