Wind turbine and its vibration and noise reduction wind blade

Abstract

The application discloses a wind power blade capable of reducing vibration and noise, which comprises a blade body and a damping belt arranged on a suction surface of the blade body, wherein the damping belt extends along a length direction of a flow separation zone in a span direction of the blade body, extends along a width direction of the flow separation zone in a chord direction of the blade body, and is a damping and / or vibration absorbing material belt used for absorbing turbulent flow kinetic energy of the flow separation zone and a wake zone. The application can reduce the aerodynamic instability of the surrounding airflow and the blade body by absorbing the separated turbulent flow kinetic energy of the flow separation zone through the damping belt and breaking large vortexes formed in the trailing edge flow separation process of the blade body into multiple small vortexes, can simply and conveniently improve the damping and noise reduction performance without changing the original shape and production process flow, avoids increasing the production process difficulty, and can be quickly put into use. The application further discloses a wind driven generator, and the beneficial effects are as above.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of wind power generation, in particular to a vibration and noise reduction wind blade. The present application also relates to a wind power generator. BACKGROUND

[0002] With the continuous development of wind power technology, large-scale development of blades has become a trend.

[0003] The increase in blade length can significantly improve power generation and increase economic efficiency, but the aeroelastic problem brought by long and flexible blades is also increasingly prominent. The aeroelastic problem can cause damage to the wind turbine blade, and the aeroelastic instability phenomenon caused by the lack of sufficient damping can make the fatigue load of the wind turbine too large, causing the service life of the blade to be shortened. In addition, for large blade units on land, the windward area is larger, and the noise level generated by the whole wind wheel is also relatively higher. Moreover, as the development of remote areas is saturated, more and more wind farms begin to approach residential areas, which further leads to the problem of wind turbine noise being more prominent.

[0004] At present, a series of researches on the aeroelastic and noise problems of long and flexible blades have been carried out. Some schemes start from the aerodynamic shape, mainly through optimizing the airfoil and changing the overall shape of the blade to realize the optimization of aeroelasticity and noise; some schemes keep the aerodynamic shape of the blade unchanged, and improve the aeroelastic and noise characteristics of the blade by optimizing the blade material.

[0005] However, although the method of changing the aerodynamic shape of the blade can improve the aeroelastic characteristics from the source, after the optimization of the airfoil and the change of the overall shape of the blade (blade tip wing, bionic blade, etc.), the use of new standard airfoils and the change of the overall shape of the blade will have a great impact on the aerodynamic characteristics of the blade. On the other hand, due to the complex shape of the blade with special shape (such as wavy bionic blade), it has high process production difficulty and is difficult to be manufactured and processed by existing process technology. The research and development of new materials with high stiffness and vibration and noise reduction characteristics requires a long time investment, and the research and development and application cycle is too long. It can be seen that the methods for realizing the vibration and noise reduction of wind blades in the prior art all have problems of production process implementation and long research and development test cycle, and there is an urgent need for a simple and rapid implementation vibration and noise reduction measure in actual production.

[0006] Therefore, how to simply and conveniently improve the vibration and noise reduction performance of the wind blade, avoid increasing the production process difficulty, and at the same time be able to be quickly put into use, is a technical problem faced by those skilled in the art. SUMMARY

[0007] The present application aims to provide a wind blade with vibration and noise reduction function, which can improve the vibration and noise reduction function simply and conveniently without changing the original shape and production process, and can be put into use quickly without increasing the difficulty of production process. The present application also aims to provide a wind power generator.

[0008] To solve the above technical problems, the present application provides a wind blade with vibration and noise reduction function, which comprises a blade body and a first vibration reduction band arranged on the suction surface of the blade body. The first vibration reduction band extends along the length direction of a flow separation zone of the blade body in the span direction of the blade body, and extends along the width direction of the flow separation zone in the chord direction of the blade body. The first vibration reduction band is a vibration reduction material band, which is used to absorb the separation turbulent flow energy of the flow separation zone.

[0009] Preferably, the distribution starting position of the first vibration reduction band in the chord direction of the blade body is located before the separation point of the flow separation zone.

[0010] Preferably, the distribution width of the first vibration reduction band in the chord direction of the blade body accounts for 3% to 5% of the chord length of the suction surface of the blade body.

[0011] Preferably, the first vibration reduction band is uniformly distributed in the span direction of the blade body.

[0012] Preferably, the wind blade with vibration and noise reduction function further comprises a second vibration reduction band arranged on the suction surface of the blade body. The second vibration reduction band extends along the length direction of a trailing edge vortex shedding zone of the blade body in the span direction of the blade body, and extends along the width direction of the trailing edge vortex shedding zone in the chord direction of the blade body. The second vibration reduction band is a vibration reduction material band, which is used to break the large vortex flow formed during the trailing edge flow separation process of the blade body into multiple small vortex flows.

[0013] Preferably, the distribution starting position of the second vibration reduction band in the chord direction of the blade body is located at the trailing edge of the blade body.

[0014] Preferably, the distribution width of the second vibration reduction band in the chord direction of the blade body accounts for at least 20% of the chord length of the suction surface of the blade body.

[0015] Preferably, the second vibration reduction band is non-uniformly distributed in the span direction of the blade body.

[0016] Preferably, the first vibration reduction band and the second vibration reduction band each comprise a damping material layer for consuming vibration energy through internal elastic deformation of the material, and / or a resonance material sheet for consuming vibration energy through elastic vibration of the material itself.

[0017] The application further provides a wind power generator, comprising a base and a wind blade connected with the base, wherein the wind blade is the vibration and noise reduction wind blade according to any one of the above.

[0018] The vibration and noise reduction wind blade provided by the application mainly comprises a blade body and a first vibration reduction strip. The blade body is the main structure of the vibration and noise reduction wind blade. The first vibration reduction strip is arranged on the suction surface of the blade body. Specifically, the first vibration reduction strip extends along the length direction of the flow separation zone of the blade body in the span direction of the blade body, and simultaneously, the first vibration reduction strip extends along the width direction of the flow separation zone in the chord direction of the blade body. The flow separation zone is the transition position of the flow of the air current on the blade body from laminar flow to turbulent flow, or the flow separation starting position of the laminar flow and the turbulent flow, and is usually a band-shaped region distributed along the span direction of the blade body in the region close to the leading edge of the blade body. For wind blades with different airfoils, the distribution regions of the flow separation zones are not the same under different incoming flows and attack angles. The first vibration reduction strip extends along the length direction and the width direction of the flow separation zone on the suction surface of the blade body, so as to ensure that the effective range of the first vibration reduction strip falls within the flow separation zone. In addition, the first vibration reduction strip is a vibration reduction material strip, which is mainly used to absorb the separation turbulent flow energy of the flow separation zone through the characteristics of the vibration reduction material, so as to reduce the instability of the separation turbulent flow, and further reduce the aeroelastic instability of the air current and the blade body. Meanwhile, after the separation turbulent flow energy of the flow separation zone is reduced, the pressure pulsation in the conversion process of the laminar flow and the turbulent flow is also reduced, which has an inhibitory effect on the tonal noise generated by the separation turbulent flow. In this way, the vibration and noise reduction wind blade provided by the application can absorb the separation turbulent flow energy of the flow separation zone on the blade body through the characteristics of the vibration reduction material during the operation of the blade body, so as to reduce the instability of the separation turbulent flow, reduce the aeroelastic instability of the air current and the blade body, and simultaneously inhibit the tonal noise generated by the separation turbulent flow. Compared with the prior art, the vibration and noise reduction wind blade provided by the application only needs to install the first vibration reduction strip in a specific region on the blade body, without any changes to the aerodynamic shape and raw materials of the blade body. Therefore, the vibration and noise reduction performance can be simply and conveniently improved without changing the original shape and production process, the production process difficulty is avoided to be increased, and the vibration and noise reduction wind blade can be quickly put into use. BRIEF DESCRIPTION OF DRAWINGS

[0019] In order to more clearly illustrate the technical solutions in the embodiments of the application or the prior art, the following will briefly introduce the drawings needed to be used in the embodiments or the prior art description. Obviously, the drawings in the following description only belong to the embodiments of the application, and for those skilled in the art, other drawings can also be obtained without creative labor on the basis of the provided drawings.

[0020] Figure 1 A schematic diagram of the overall structure of the suction surface of a wind turbine blade in one embodiment of the present application.

[0021] Figure 2 A schematic diagram of the overall structure of the suction surface of a wind turbine blade in one embodiment of the present application. Figure 1

[0022] Figure 3 A schematic diagram of the overall structure of the suction surface of a wind turbine blade in one embodiment of the present application. Figure 1

[0023] Figure 4 A schematic diagram of the distribution of the second damping strip in one embodiment of the present application.

[0024] Figure 5 A schematic diagram of the distribution of the second damping strip in one embodiment of the present application.

[0025] Figure 6 A schematic diagram of the distribution of the second damping strip in one embodiment of the present application.

[0026] Figure 7 A schematic diagram of the specific structure of the damping material layer in one embodiment of the present application.

[0027] Figure 8 A schematic diagram of the specific structure of the resonance material sheet in one embodiment of the present application.

[0028] In one embodiment of the present application, Figure 1 In one embodiment of the present application, Figure 8 In one embodiment of the present application,

[0029] Flow separation region - a, separation point - al, trailing edge vortex shedding region - b;

[0030] Blade body - 1, first damping strip - 2, second damping strip - 3, damping material layer - 4, resonance material sheet - 5. DETAILED DESCRIPTION

[0031] The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments of the present application. Based on the embodiments in the present application, all other embodiments obtained by a person of ordinary skill in the art without creative labor fall within the scope of protection of the present application.

[0032] Please refer to Figure 1 , Figure 1 A schematic diagram of the overall structure of the suction surface of a wind turbine blade in one embodiment of the present application.

[0033] In one embodiment of the present application, the damping and noise reduction wind turbine blade mainly comprises a blade body 1 and a first damping strip 2.

[0034] ​​The blade body 1 is a main structure of the vibration and noise reduction wind blade.

[0035] The first vibration reduction band 2 is arranged on the suction surface of the blade body 1, and specifically, the first vibration reduction band 2 extends along the length direction of the flow separation area a of the blade body 1 in the span direction of the blade body 1, and at the same time, the first vibration reduction band 2 extends along the width direction of the flow separation area a in the chord direction of the blade body 1. The flow separation area a is a transition position of the airflow on the blade body 1 from laminar flow to turbulent flow, or a flow separation starting position of laminar flow and turbulent flow, and is usually a band-shaped area distributed along the span direction of the blade body 1 near the leading edge region of the blade body 1. For wind blades of different airfoils, the distribution area of the flow separation area a is not the same under different incoming flows and attack angles. The first vibration reduction band 2 extends along the length direction and the width direction of the flow separation area a on the suction surface of the blade body 1, respectively, to ensure that the action range of the first vibration reduction band 2 falls within the flow separation area a. Moreover, the first vibration reduction band 2 is a vibration reduction material band, which is mainly used to absorb the separated turbulent flow energy of the flow separation area a through the vibration reduction material characteristics, so as to reduce the instability of the separated turbulent flow, and further reduce the aeroelastic instability of the airflow and the blade body 1; at the same time, after the separated turbulent flow energy of the flow separation area a is reduced, the pressure pulsation in the conversion process of laminar flow and turbulent flow is also reduced, which has an inhibitory effect on the tonal noise generated by the separated turbulent flow.

[0036] Therefore, the vibration and noise reduction wind blade provided by the embodiment can absorb the separated turbulent flow energy of the flow separation area a on the blade body 1 through the vibration reduction material characteristics during the operation of the blade body 1, so as to reduce the instability of the separated turbulent flow, reduce the aeroelastic instability of the airflow and the blade body 1, and at the same time, inhibit the tonal noise generated by the separated turbulent flow.

[0037] Compared with the prior art, the vibration and noise reduction wind blade provided by the embodiment only needs to install the first vibration reduction band 2 in a specific area on the blade body 1, without any changes to the aerodynamic shape and raw materials of the blade body 1, so that the vibration and noise reduction performance can be simply and conveniently improved without changing the original shape and production process, thereby avoiding increasing the difficulty of the production process, and at the same time, the vibration and noise reduction wind blade can be quickly put into use.

[0038] As mentioned above, the distribution area of the flow separation zone a is not the same for different blade bodies 1 under different incoming flows and attack angles. In actual design, the position of the flow separation zone a can be obtained by simulation or experiment under the design conditions, i.e. the operating incoming flow and attack angle, for a typical airfoil (e.g. a 18% or 21% relative thickness airfoil). The chordwise separation position of each spanwise position section of the typical airfoil can be obtained by interpolation, and the overall flow separation position in the spanwise range where the first damping band 2 needs to be used is finally confirmed.

[0039] As shown in Figure 2 , Figure 3 , Figure 2 is a partial structural schematic view of Figure 1 , Figure 3 is a cross-sectional structural schematic view of Figure 1 .

[0040] In an alternative embodiment of the first damping band 2, considering the separation characteristics of laminar flow and turbulent flow in the flow separation zone a, the first damping band 2 extends from the leading edge to the trailing edge in the chordwise direction of the blade body 1, and the distribution starting position of the first damping band 2 is located before the separation point a1 of the flow separation zone a. Specifically, for the blade body 1, the distribution area of the flow separation zone a on each cross section of the blade body 1 can change, and the starting position of the flow separation zone a on each cross section of the blade body 1 also changes accordingly, i.e. the starting position in the chordwise direction is different, which is the separation point a1. By setting the distribution starting position of the first damping band 2 in the chordwise direction of the blade body 1 before the separation point a1 of the flow separation zone a, a better flow control effect can be obtained, and the pre-absorption effect of the separated turbulent flow energy of the flow separation zone a can be achieved.

[0041] Generally, the distribution width of the first damping band 2 in the chordwise direction of the blade body 1 accounts for 3% to 5% of the chord length of the suction surface of the blade body 1. By setting the distribution range of the first damping band 2 to be basically negligible compared to the chordwise dimension of the blade body 1, the original airfoil profile curvature can be changed significantly, and the separated turbulent flow energy can be better absorbed and the instability of the boundary layer can be better suppressed.

[0042] In addition, the first damping band 2 is uniformly distributed in the spanwise direction of the blade body 1, i.e. it forms a continuous and uniformly distributed linear distribution from the inner end to the outer end in the spanwise direction of the blade body 1. By setting the first damping band 2, the separated turbulent flow energy in the entire flow separation zone a can be more evenly absorbed, thereby further reducing the instability of the separated turbulent flow and ultimately further reducing the aeroelastic instability of the airflow and the blade body 1.

[0043] In another specific embodiment of the present invention, the vibration-damping and noise-reducing wind turbine blade includes a blade body 1 and a first damping band 2, as well as a second damping band 3. The second damping band 3 is also disposed on the suction surface of the blade body 1. Specifically, the second damping band 3 extends along the length direction of the trailing edge vortex shedding zone b in the spanwise direction of the blade body 1, and simultaneously extends along the width direction of the trailing edge vortex shedding zone b in the chordwise direction of the blade body 1. The trailing edge vortex shedding zone b is the location where vortices are formed during the flow separation process at the trailing edge of the blade body 1, or the location where the vortex separates from the blade body 1 after formation. It is typically a band-shaped region distributed along the spanwise direction of the blade body 1 near the trailing edge region. The second damping band 3 extends along both the length and width directions of the trailing edge vortex shedding zone b on the suction surface of the blade body 1, ensuring that the effective range of the second damping band 3 falls within the trailing edge vortex shedding zone b. Furthermore, the second damping strip 3 is a damping material strip, mainly used to absorb the vortex kinetic energy of the trailing edge vortex shedding zone b through the characteristics of the damping material, thereby breaking the large vortex formed during the flow separation process along the trailing edge of the blade body 1 into multiple small vortices, thereby destroying the spanwise coherence of the airfoil and converting the low-frequency noise generated in the trailing edge vortex zone into high-frequency noise, which is beneficial to reducing the overall broadband noise of the blade; at the same time, by using the damping material characteristics of the second damping strip 3 to absorb part of the vibration of the vortex and the blade body 1, it can also reduce the aeroelastic instability of the airflow and the blade body 1 to a certain extent.

[0044] In one optional embodiment of the second damping band 3, considering that vortices mainly form and detach within the trailing edge vortex shedding zone b near the trailing edge, in this embodiment, the second damping band 3 extends from the trailing edge to the leading edge in the chordal direction of the blade body 1, and the starting position of the distribution of the second damping band 3 in the chordal direction of the blade body 1 is located on the trailing edge of the blade body 1. Specifically, for the blade body 1, the distribution area of ​​the trailing edge vortex shedding zone b on each cross-section of the blade body 1 may vary to some extent, and the ending position of the trailing edge vortex shedding zone b on each cross-section of the blade body 1 will also vary accordingly, that is, the ending position in the chordal direction is different. Accordingly, the ending position of the distribution of the second damping band 3 in the chordal direction of the blade body 1 can be adjusted according to the actual flow conditions. Generally, the distribution range of the second damping band 3 in the chordal direction of the blade body 1 needs to occupy at least 20% of the chord length starting from the trailing edge. For different airfoils and their operating conditions, this coverage area can be appropriately increased.

[0045] like Figures 4-6 As shown, Figure 4 This is a schematic diagram of one distribution structure of the second damping strip 3. Figure 5 This is a schematic diagram of another distribution structure for the second damping band 3. Figure 6 This is a schematic diagram of another distribution structure for the second damping band 3.

[0046] In addition, the second damping band 3 is distributed in a non-uniform strip shape in the spanwise direction of the blade body 1, that is, in the spanwise direction of the blade body 1, from the inner end to the outer end, a discontinuous zigzag shape, a discontinuous curved shape, or a continuous shape with multiple zigzag shapes, multiple circular arc shapes, or other irregular shapes connected together is formed. In this way, by virtue of the non-uniform distribution of the second damping band 3, the spanwise coherence of the airfoil can be destroyed, and the large vortex flow generated during the flow separation process along the trailing edge of the blade body 1 can be broken into small vortex flows more frequently and more effectively.

[0047] In an optional embodiment of the first damping band 2 and the second damping band 3, considering the original aerodynamic shape characteristics of the blade body 1, the root is thicker and has higher structural strength, and the tip is thinner and has lower structural strength, especially in the 1 / 3 range near the tip of the blade body 1, this part is the largest part of the deformation, vibration and noise of the blade body 1. In view of this, in this embodiment, the first damping band 2 and the second damping band 3 are arranged in the 1 / 3 range near the tip of the suction surface of the blade body 1 on the basis of keeping the original aerodynamic shape of the blade body 1 unchanged, so as to concentrate on damping and noise reduction of this part of the blade body 1. Of course, the specific distribution position and range of the first damping band 2 and the second damping band 3 on the blade body 1 can also be adjusted according to the actual situation, for example, the first damping band 2 and the second damping band 3 can be distributed on the suction surface of the blade body 1 in the half part near the tip.

[0048] In addition, in another optional embodiment of the first damping band 2 and the second damping band 3, the first damping band 2 and the second damping band 3 each include a damping material layer 4 for consuming vibration energy through internal elastic deformation of the material, or each include a resonance material sheet 5 for consuming vibration energy through elastic vibration of the material itself, or both include the damping material layer 4 and the resonance material sheet 5.

[0049] As shown in Figure 7 , Fig. 4 is a schematic view of the specific structure of the damping material layer 4. Figure 7

[0050] ​Wherein, for the damping material layer 4, the main mechanism is to convert the kinetic energy of the non-steady turbulent flow and the vibration energy of the blade body 1 into the elastic potential energy inside the material, thereby reducing the overall instability. When setting, the damping material layer 4 only needs to be covered on the suction surface of the blade body 1 to enhance the structural damping performance. Generally, the damping material layer 4 can be selected from a coating material mixed with high molecular resin and other auxiliary materials, or a coating material mixed with metal base, ceramic base, or other special materials with damping characteristics. For example, the first damping band 2 can use the damping material layer 4 to absorb the turbulent flow kinetic energy of the boundary layer separation through the bending deformation of the blade body 1, and convert it into internal energy through the internal friction process, thereby reducing the instability of the separated flow.

[0051] As shown in Figure 8 , the specific structure of the resonance material sheet 5 is shown in Figure 8 .

[0052] For the resonance material sheet 5, the main mechanism is to absorb the non-steady airflow and the vibration of the blade body 1 and consume it through the elastic vibration of the material itself, thereby reducing the aeroelastic instability of the airflow and the blade body 1. When setting, the resonance material sheet 5 only needs to be covered on the suction surface of the blade body 1 to enhance the structural damping performance. Generally, the resonance material sheet 5 can be selected from a sheet type elastic sheet such as a metal type, a ceramic type, and a rubber type. For example, the first damping band 2 can use the resonance material sheet 5 to absorb the non-steady airflow and the vibration energy of the blade body 1 and consume it through the elastic vibration of the material itself, thereby reducing the aeroelastic instability of the airflow and the blade body 1; the second damping band 3 can use the resonance material sheet 5 to absorb part of the vibration energy of the airflow and the blade body 1, thereby reducing the instability of the airfoil itself and the vortex airflow to a certain extent.

[0053] In summary, the damping and noise reduction wind turbine blade provided by the embodiment can simply and conveniently improve the damping and noise reduction performance without changing the original shape and production process, avoid increasing the production process difficulty, and quickly put into use. Since the existing blade shape design, structure design, and process production process are not changed, the influence on the entire design and production process is small, and the installation process of the first damping band 2 and the second damping band 3 is simple and convenient, which is easy to operate. The first damping band 2 and the second damping band 3 can simultaneously suppress the tonal noise generated by flow separation and the broadband noise generated by the trailing edge vortex shedding. In addition, the first damping band 2 and the second damping band 3 can be used in the produced or completed blade, which has strong universality and does not affect the aerodynamic characteristics, power generation performance, and economy of the original blade.

[0054] The embodiment also provides a wind power generator, mainly comprising a base and a wind blade connected with the base, wherein, since the wind blade adopts all the technical solutions of the wind blade with vibration and noise reduction function, the wind power generator provided by the embodiment has all the technical effects brought by the technical solutions of the above-mentioned embodiments, which will not be repeated here.

[0055] The above description of disclosed embodiments enables one of ordinary skill in the art to make or use the application. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein can be applied to other embodiments without departing from the spirit or scope of the application. Thus, the present application is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A damped and noise-reduced wind blade comprising a blade body (1), characterized in that, The wind turbine blade further comprises a first damping strip (2) arranged on the suction surface of the blade body (1), the first damping strip (2) extending along the length direction of the flow separation region (a) of the blade body (1) in the span direction of the blade body (1), the first damping strip (2) extending along the width direction of the flow separation region (a) in the chord direction of the blade body (1), and the first damping strip (2) being a damping material strip for absorbing the separated turbulent flow energy of the flow separation region (a); the wind turbine blade further comprises a second damping strip (3) arranged on the suction surface of the blade body (1), the second damping strip (3) extending along the length direction of the trailing edge vortex shedding region (b) of the blade body (1) in the span direction of the blade body (1), the second damping strip (3) extending along the width direction of the trailing edge vortex shedding region (b) in the chord direction of the blade body (1), and the second damping strip (3) being a damping material strip for breaking the large vortex flow formed during the trailing edge flow separation of the blade body (1) into a plurality of small vortex flows; the first damping strip (2) and the second damping strip (3) each comprise a damping material layer (4) for consuming vibration energy through internal elastic deformation of the material and / or a resonance material sheet (5) for consuming vibration energy through elastic vibration of the material itself.

2. A vibration and noise reducing wind blade according to claim 1, characterized in that The first damping strip (2) is distributed in the chord direction of the blade body (1) starting from a position before the separation point (a1) of the flow separation region (a).

3. A vibration and noise reducing wind blade according to claim 2, characterized in that The distribution width of the first damping strip (2) in the chord direction of the blade body (1) accounts for 3% to 5% of the chord length of the suction surface of the blade body (1).

4. The vibration and noise reducing wind blade of claim 1, wherein, The first damping strip (2) is uniformly distributed in the span direction of the blade body (1).

5. A vibration and noise reducing wind blade according to any of claims 1 to 4, characterised in that The second damping strip (3) is distributed in the chord direction of the blade body (1) starting from the trailing edge of the blade body (1).

6. A vibration and noise reducing wind blade according to claim 5, characterized in that The distribution width of the second damping strip (3) in the chord direction of the blade body (1) accounts for at least 20% of the chord length of the suction surface of the blade body (1).

7. A vibration and noise reducing wind blade according to any of claims 1 to 4, characterised in that The second damping strip (3) is non-uniformly distributed in the span direction of the blade body (1).

8. A wind driven electrical generator comprising a base and a wind blade connected to the base, characterised in that, The wind turbine blade is specifically the damping and noise reduction wind turbine blade according to any one of claims 1 to 7.

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