CN113029480A - Blade fatigue testing method and blade fatigue testing system of wind generating set - Google Patents
Blade fatigue testing method and blade fatigue testing system of wind generating set Download PDFInfo
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Abstract
The invention provides a blade fatigue testing method and a blade fatigue testing system of a wind generating set, wherein the blade fatigue testing method comprises the following steps: determining a target load containing a mean value of the blade to be tested; determining a test load containing a mean value by adjusting the position of an excitation point, the position of a counterweight and the size of the counterweight, so that the ratio of the test load to a target load is in a preset range; horizontally mounting the blades, mounting a vibration exciter and balancing the weight; and starting the vibration exciter to vibrate the testing area of the blade, so that the plurality of sections in the testing area reach section strain corresponding to the testing load. The invention provides a blade fatigue testing method and a blade fatigue testing system of a wind generating set, which enable the testing load to be closer to the actual load, thereby enabling the testing result to be more accurate and shortening the testing period.
Description
Technical Field
The invention relates to a blade fatigue testing method and a blade fatigue testing system of a wind generating set.
Background
With the gradual increase of the single-machine capacity of the wind generating set, the blades are continuously enlarged, so the design value of the blades is closer to the limit of materials, and the safety of the blades is more and more challenged.
For blades, especially for large blades, fatigue testing of full-scale blades is a critical link to verifying blade reliability. The blade fatigue test mainly verifies the service life of the blade, provides a test bending moment in a mode of loading bending moment or force on the blade section in an excitation mode through the corresponding relation between a target bending moment and the test bending moment, and obtains the fatigue damage of the blade through strain data of materials. Therefore, blade fatigue testing requires the establishment of bending moments (or loads) versus strain.
As shown in fig. 1, the load of a wind turbine blade 1 is generally decomposed into two directions, i.e. a flapwise direction 2 and a flapwise direction 3, so that fatigue tests are performed according to the load directions, wherein the fatigue tests are usually accelerated tests because the fatigue loads in the flapwise direction are large, i.e. the fatigue test loads are amplified on the basis of the design loads in order to make up for the difference from the loads borne by the actual operating state of the blade. However, such an amplification may result in the fatigue test load in the blade shimmy direction being comparable to the limit load, and even exceeding the limit load, and therefore, in order to reduce the load level of the blade fatigue test, it is necessary to increase the number of test fatigue times, which is generally around 400 ten thousand times, which makes the test cycle of the blade very long, generally around 3 months.
The existing blade fatigue test mainly adopts a resonance method, a balance weight needs to be added on a blade in the test process so as to achieve the required test load, in the existing test, the mean load generated by the gravity of the self weight of the blade, the balance weight and the like is not taken into consideration, the actual load level of the blade cannot be truly reflected, and particularly, under the condition that the blade is developed to be large-scale, the influence of gravity bending moment on the test is more and more great, so that the test result is not accurate.
In addition, when the fatigue test is carried out in the shimmy direction, because the shimmy fatigue test load is larger, a method for increasing the test times to reduce the test load is adopted, so that the shimmy fatigue test times are increased, and the test period is prolonged.
Disclosure of Invention
In order to solve the problems of inaccurate test and long test period of the existing blade fatigue test, the invention provides the blade fatigue test method and the blade fatigue test system of the wind generating set, so that the test load is closer to the actual load, the test result is more accurate, and the test period is shortened.
One aspect of the invention provides a blade fatigue testing method for a wind generating set, which comprises the following steps: s1, determining the target load containing the mean value of the blade to be tested; s2, determining a test load containing a mean value by adjusting the position of the excitation point, the position of the counterweight and the size of the counterweight, so that the ratio of the test load to the target load is in a preset range; s3, horizontally mounting the blade, mounting an exciter according to the position of the excitation point adjusted in the step S2, and balancing the weight according to the position and the size of the weight adjusted in the step S2; and S4, starting a vibration exciter to vibrate the testing area of the blade, so that a plurality of sections in the testing area reach section strain corresponding to the testing load.
Preferably, step S1 may include: obtaining an average value-containing equivalent fatigue load under 1000 ten thousand fatigue times according to the material of the blade to be tested; carrying out test fatigue number conversion on the equivalent fatigue load with the mean value under the fatigue number of 1000 ten thousand times to obtain the equivalent fatigue load with the mean value under the test fatigue number; and (4) performing safety coefficient conversion on the equivalent fatigue load containing the mean value under the test fatigue times to determine a target load.
Preferably, the mean equivalent fatigue load M at 1000 ten thousand fatigue times can be obtained by the expression (1)eqj，
Wherein R isk,cIs the compressive strength of the material, gammam，short termIs the fractional coefficient of the material, Sk,AiFor fatigue-testing load amplitude, S, determined by fatigue-load spectrumk,MiTo pass fatigue loadAnd (4) fatigue test load mean value determined by the load spectrum.
Preferably, the mean value-containing equivalent fatigue load M under the test fatigue number can be obtained by the expression (2)eq，
Wherein N isjFor testing fatigue number, N0The fatigue times are 1000 ten thousand times, and m is the S-N curve slope value of the material fatigue test.
Preferably, step S2 may include: determining the vibration mode of the blade by adjusting the position of an excitation point, the position of a counterweight and the size of the counterweight; according to the self weight and the size of the balance weight of the blade, the actual gravity load in the blade fatigue test is obtained, and the mean value of the test load is determined; and amplifying the amplitude of the blade vibration mode by adjusting the calibration position and the calibration load, so that the ratio of the test load to the target load is in a preset range, and determining the test load.
Preferably, the test load M may be determined by expression (3)eqt，
Wherein R isk,cIs the compressive strength of the material, gammam，short termIs the fractional coefficient of the material, Sk，AtFor the amplified amplitude, Sk，MtIs the mean value of the test load.
Preferably, step S4 may include: and carrying out single-point loading on the blade according to the calibration position and the calibration load to obtain a linear relation between the calibration load and the blade strain, and converting the linear relation to obtain the section strain of each section corresponding to the test load.
Preferably, the step S4 may further include: and in the testing process, carrying out damage statistics according to the testing load and the target load, so that the actual vibration times of each section reach the required testing fatigue times.
The invention also provides a blade fatigue test system of the wind generating set, which comprises the following components: the load determining device determines a target load containing a mean value of the blade to be tested, and determines a test load containing the mean value by adjusting the position of an excitation point, the position of a counterweight and the size of the counterweight so that the ratio of the test load to the target load is in a preset range; the vibration exciter is arranged on the blade at the position of the vibration exciting point obtained by adjustment, so that the testing area of the blade vibrates; a weight member having a weight size obtained by the adjustment and mounted to the blade at a weight position obtained by the adjustment; a sensor that senses strain of the blade and outputs a sensing signal to the control device; and the control device controls the exciting force of the vibration exciter so that the plurality of sections in the test area reach section strain corresponding to the test load.
Preferably, the load determining means also determines the mean value of the test load from the self-weight of the blade and the size of the counterweight, and amplifies the amplitude of the mode shape of the blade.
According to the blade fatigue testing method and the blade fatigue testing system of the wind generating set, the target load and the testing load containing the mean value can be obtained through load conversion, and therefore the testing fatigue state of the blade is closer to the actual fatigue load state of the blade by considering the influence of the mean value.
In addition, according to the blade fatigue testing method and the blade fatigue testing system of the wind generating set, the blade fatigue testing times can be effectively reduced, and the blade testing time can be shortened under the same excitation load.
In addition, according to the blade fatigue testing method and the blade fatigue testing system of the wind generating set, the vibration mode and the frequency of the blade are obtained by considering the positions, the weight and the dead weight of the blade at the excitation point and the counterweight point, and the mode theory analysis is performed, the actual load of each section position of the blade in the vibration process is obtained, the blade testing load is obtained, and the actual vibration load of a testing area can be controlled within the design load range in the design stage of the testing theory through continuous iteration optimization.
In addition, according to the blade fatigue testing method and the blade fatigue testing system of the wind generating set, in the fatigue testing process, the specific positions and weights of the excitation points and the matching points are accurately calculated in advance, so that adjustment and optimization are not needed in the testing stage, and testing resources and time are saved.
Drawings
FIG. 1 is a schematic diagram illustrating the load resolution direction of a blade fatigue test.
FIG. 2 is a flow chart illustrating a blade fatigue testing method according to an embodiment of the invention.
Fig. 3 is a schematic view illustrating positions of an exciter and a weight installation of a blade fatigue testing method according to an embodiment of the present invention.
The reference numbers illustrate:
1: blade, 2: waving direction, 3: shimmy direction, 4: excitation point position, 5: a counterweight position.
Detailed Description
The present invention will be described more fully hereinafter with reference to specific examples, which, however, are merely illustrative of preferred embodiments of the invention, and the scope of the invention is not limited thereto.
As shown in FIG. 2, a blade fatigue testing method of a wind turbine generator set according to an embodiment of the invention may include the steps of:
s1: and determining the target load containing the mean value of the blade to be tested.
In order to consider the influence of the dead weight of the blade and the mean value load generated by the balance weight on the blade in the test process, when determining the target load of the blade to be tested, firstly, the mean value-containing equivalent fatigue load under 1000 ten thousand fatigue times can be obtained according to the material of the blade to be tested; then, carrying out conversion of the testing fatigue times on the obtained average value-containing equivalent fatigue load under 1000 ten thousand fatigue times to obtain the average value-containing equivalent fatigue load under the testing fatigue times; and (4) performing safety coefficient conversion on the equivalent fatigue load containing the mean value under the test fatigue times so as to obtain the final target load.
As an example, it can be converted by expression (1)Mean value-containing equivalent fatigue load M under 1000 ten thousand fatigue timeseqj，
Wherein R isk,cIs the compressive strength of the material, gammam，short termIs the fractional coefficient of the material, Sk,AiFor fatigue-testing load amplitude, S, determined by fatigue-load spectrumk,MiIs the mean fatigue test load determined by the fatigue load spectrum. In the case where the basic parameters of the blade to be tested are determined, with a corresponding fatigue load spectrum (Markov matrix), the above-mentioned parameter R can be determinedk,c、γm，short term、Sk,AiAnd Sk,MiTherefore, the mean equivalent fatigue load under 1000 ten thousand fatigue times can be calculated.
Since the mean equivalent fatigue load at 1000 ten thousand fatigue times is obtained from the above expression (1), the fatigue times can be converted to obtain the mean equivalent fatigue load at the required test fatigue times. For example, the mean equivalent fatigue load M under 1000 ten thousand fatigue times can be obtained by the expression (2)eqjPerforming test fatigue frequency conversion to obtain an equivalent fatigue load M containing the mean value under the test fatigue frequencyeq，
Wherein N isjFor testing fatigue number, N0The fatigue times are 1000 ten thousand times, and m is the S-N curve slope value of the material fatigue test. Here, the corresponding S-N curve slope value m of the material fatigue test and the test fatigue times N can be obtained according to the blade materialjThe setting may be based on empirical or expected values, for example, 200 ten thousand times.
Mean value-containing equivalent fatigue load M under test fatigue timeseqWhen the safety factor is converted, the proper value can be selected according to the actual situationTo amplify the target load, for example, the safety factor may be about 1.328.
It should be understood that expressions (1) and (2) above are merely intended as parameters for a blade-based material (e.g., R)k,c、γm，short term、Sk,Ai、Sk,MiAnd M, etc.) to calculate the mean value-containing equivalent fatigue load M under the fatigue times of 1000 ten thousand times and the test fatigue timeseqjAnd MeqThe mean value-containing equivalent fatigue load may also be calculated based on the material parameters of the blade in various other suitable manners, but the invention is not limited to this, and for example, the mean value-containing equivalent fatigue load may be calculated based on an equation obtained by appropriately deforming or adjusting the expressions (1) and (2) based on the test factors to be considered in the actual test.
As described above, the target load considering the mean value can be obtained by the equivalent fatigue load including the mean value. Here, since the mean load is generated by the self weight of the blade and the weight on the blade, by considering the mean load, the self weight of the blade and the weight on the blade (including the weight of the exciter and the weight member) can be made to obtain a more accurate target load.
S2: and determining the test load containing the mean value by adjusting the position of the excitation point, the position of the counterweight and the size of the counterweight, so that the ratio of the test load to the target load is in a preset range.
In the process of determining the excitation point and the counterweight, the blade vibration mode can be optimized by continuously adjusting the excitation point position, the counterweight position and the counterweight size, and meanwhile, preferably, the blade vibration mode amplitude can be amplified by adjusting the calibration position and the calibration load, the test load level in the test area is controlled, so that the ratio of the test load to the target load is in a preset range, the test load (including the mean load and the amplitude load) is determined, and the adjusted excitation point position, the counterweight size, the calibration position and the calibration load are obtained.
Here, the weight of the exciter that vibrates the blade may be taken into account when calculating the assembly weight. Since the mean component in the test load is derived from the dead weight of the blade and the counterweight on the blade, the actual gravity load in the fatigue test of the blade can be obtained when the location of the excitation point, the location of the counterweight and the size of the counterweight are determined, thereby determining the mean of the test load.
The ratio of the test load to the target load may be defined as an overload factor for the test load, which is typically within a predetermined design range, e.g., may be 1.01 to 1.20. The actual amplitude requirement of the test load in the test process, namely the amplitude of the blade vibration mode amplified by the calibration load, can be obtained through the overload coefficient conversion.
As an example, the test load M may be obtained by expression (3)eqt，
Wherein R isk,cIs the compressive strength of the material, gammam，short termIs the fractional coefficient of the material, Sk，AtFor the amplified amplitude, Sk，MtIs the mean value of the test load.
Here, too, the expression (3) is only used as the calculation test load MeqtAs a preferred example, the test load may be obtained by other various suitable manners based on the material parameters of the blade and the mean value and the amplitude, for example, the test load may be calculated based on an equation obtained by appropriately deforming or adjusting the expression (3) based on the test factors to be considered in the actual test.
The test area referred to above may refer to the effective fatigue verification area of the blade where vibrations occur, preferably the area in the range from the root of the blade to 60% of the total length of the blade.
Furthermore, each cross-section within the test area of the blade can be strained under nominal loads applied to nominal positions on the blade. In general, the nominal position may be closer to the blade tip than the location of the excitation point.
S3: the blade is horizontally attached, the exciter is attached at the excitation point position 4 determined in step S2, and the counterweight is attached at the counterweight position 5 and the counterweight size determined in step S2. In particular, the chordwise direction of the blade may be mounted parallel to the ground.
S4: and starting the vibration exciter to vibrate the testing area of the blade, so that the plurality of sections in the testing area reach section strain corresponding to the testing load.
During testing, the blade may first be calibrated in order to obtain a cross-sectional strain corresponding to the test load. Specifically, the blade may be subjected to single-point loading according to the calibration position and the calibration load determined above, so as to obtain a linear relationship between the calibration load and the blade strain, and obtain the section strain of each section of the blade corresponding to the test load when the blade vibrates through conversion of the linear relationship. That is, when the linear relationship between the calibration load and each of the sectional strains of the blade and the test load are determined, the sectional strain corresponding to the test load can be obtained by using the same linear relationship. Here, the calibration load and the calibration position for determining the linear relationship of the load and the blade strain may also be different from those determined in step S2, for example, the magnitude and the applied position of the load may be adjusted. In addition, besides the method of single point loading by the calibration load, the linear relationship between the load and the blade strain can also be determined by other methods, and is not particularly limited.
After the section strain corresponding to the test load is determined, the vibration exciter is started to enable the blade to vibrate, and the vibration exciting amount applied to the blade by the vibration exciter can be adjusted to enable each section strain to reach the section strain corresponding to the test load, so that the blade fatigue test is completed.
In addition, in the testing process, in order to achieve the required testing fatigue times, damage statistics can be carried out. Specifically, the actual vibration times can be converted according to the Miner criterion according to the test load and the target load, so that the actual vibration times of each section of the blade can reach the required test fatigue times.
As an example, the actual number of vibrations may be reduced according to expression (4):
wherein N isfFor actual vibration times, N for test fatigue times, σfFor test load, σ is the target load, and m is the material fatigue test S-N curve slope value.
The mean load is considered in the blade fatigue testing method, so that the amplitude of the blade in the testing process can be reduced, the testing fatigue times are reduced, the testing period is shortened, and the testing efficiency is improved. In a fatigue test performed for the blade shimmy direction, the number of test fatigue times may be less than 200 ten thousand times. In a fatigue test for the blade flap direction, the number of test fatigue times may be less than 100 ten thousand.
The blade fatigue testing method can be used for carrying out fatigue testing on the blade flapping direction or the blade shimmy direction.
The invention also provides a blade fatigue testing system of the wind generating set, which comprises a load determining device, a vibration exciter, a counterweight, a sensor and a control device.
The load determining means may be operable to determine a target load comprising a mean value for the blade to be tested and determine the test load comprising the mean value by adjusting the location of the excitation point, the location of the counterweight and the size of the counterweight such that the ratio of the test load to the target load is within a predetermined range.
As an example, the load determination means may calculate the target load including the mean value using the expressions (1) and (2) described above; and then, adjusting the amplitude and the mean value parameter in the expression (3) by adjusting the position of the excitation point, the position of the counterweight and the size of the counterweight by using the expression (3) so that the ratio of the test load to the target load is in a preset range, thereby determining the test load containing the mean value required in the test process, and outputting or storing the determined test load and the position of the excitation point, the position of the counterweight and the size of the counterweight corresponding to the test load.
Preferably, the load determining means may further determine a mean value of the test load according to the self weight of the blade and the size of the weight, and amplify the magnitude of the blade mode shape, thereby determining the test load according to the determined mean value and the amplified magnitude.
The exciter may be mounted to the blade at an excitation point position adjusted by the load determining means, and an excitation force is applied to the blade during testing to cause the test region of the blade to vibrate.
The weight member may have a weight size adjusted by the load determining means and be mounted to the blade at a weight position adjusted by the load determining means for adding weight to the blade.
The sensor may sense the strain of the blade and output a sensing signal to the control device.
The control device may control the excitation force of the vibration exciter according to the sensing signal such that the plurality of sections in the test region attain a section strain corresponding to the test load.
Here, the section strain corresponding to the test load (hereinafter referred to as "test load strain") may be obtained in advance from the above-described linear relationship of the load and the blade strain (for example, determined by the calibration load and the calibration section strain corresponding thereto), and input or stored into the control device. The control device can compare a sensing signal transmitted back by the sensor with a preset test load strain, determine whether the current blade strain is consistent with the preset test load strain, and if so, keep the current state of the vibration exciter; and if the strain of the blade is inconsistent with the preset test load strain, adjusting the excitation force of the vibration exciter until the strain of the blade is consistent with the preset test load strain.
According to the blade fatigue testing method and the blade fatigue testing system of the wind generating set, the target load and the testing load containing the mean value can be obtained through load conversion, and therefore the testing fatigue state of the blade is closer to the actual fatigue load state of the blade by considering the influence of the mean value.
In addition, according to the blade fatigue testing method and the blade fatigue testing system of the wind generating set, the blade fatigue testing times can be effectively reduced, and the blade testing time can be shortened under the same excitation load.
In addition, according to the blade fatigue testing method and the blade fatigue testing system of the wind generating set, the vibration mode and the frequency of the blade are obtained by considering the positions, the weight and the dead weight of the blade at the excitation point and the counterweight point, and the mode theory analysis is performed, the actual load of each section position of the blade in the vibration process is obtained, the blade testing load is obtained, and the actual vibration load of a testing area can be controlled within the design load range in the design stage of the testing theory through continuous iteration optimization.
In addition, according to the blade fatigue testing method and the blade fatigue testing system of the wind generating set, in the fatigue testing process, the specific positions and weights of the excitation points and the matching points are accurately calculated in advance, so that adjustment and optimization are not needed in the testing stage, and testing resources and time are saved.
While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it will be understood by those of ordinary skill in the art that various changes in form and details may be made therein without departing from the spirit and scope of the present invention as defined by the following claims.
Claims (10)
1. A blade fatigue testing method of a wind generating set is characterized by comprising the following steps:
s1, determining the target load containing the mean value of the blade to be tested;
s2, determining a test load containing a mean value by adjusting the position of the excitation point, the position of the counterweight and the size of the counterweight, so that the ratio of the test load to the target load is in a preset range;
s3, horizontally mounting the blade, mounting an exciter according to the position of the excitation point adjusted in the step S2, and balancing the weight according to the position and the size of the weight adjusted in the step S2;
and S4, starting a vibration exciter to vibrate the testing area of the blade, so that a plurality of sections in the testing area reach section strain corresponding to the testing load.
2. The blade fatigue testing method of the wind generating set according to claim 1, wherein the step S1 includes:
obtaining an average value-containing equivalent fatigue load under 1000 ten thousand fatigue times according to the material of the blade to be tested;
carrying out test fatigue number conversion on the equivalent fatigue load with the mean value under the 1000 ten thousand fatigue numbers to obtain the equivalent fatigue load with the mean value under the test fatigue number;
and performing safety coefficient conversion on the equivalent fatigue load containing the mean value under the test fatigue times to determine the target load.
3. The blade fatigue testing method of the wind generating set according to claim 2, wherein the mean equivalent fatigue load M with the fatigue number of 1000 ten thousand times is obtained through the expression (1)eqj，
Wherein R isk,cIs the compressive strength of the material, gammam，short termIs the fractional coefficient of the material, Sk,AiFor fatigue-testing load amplitude, S, determined by fatigue-load spectrumk,MiIs the mean fatigue test load determined by the fatigue load spectrum.
4. The blade fatigue testing method of the wind generating set according to claim 3, wherein the mean equivalent fatigue load M under the test fatigue times is obtained through expression (2)eq，
Wherein N isjFor said test of fatigue times, N0The fatigue times are 1000 ten thousand times, and m is the S-N curve slope value of the material fatigue test.
5. The blade fatigue testing method of the wind generating set according to claim 1, wherein the step S2 includes:
determining the vibration mode of the blade by adjusting the position of an excitation point, the position of a counterweight and the size of the counterweight;
according to the self weight and the size of the balance weight of the blade, the actual gravity load in the blade fatigue test is obtained, and the mean value of the test load is determined;
and amplifying the amplitude of the blade vibration mode by adjusting the calibration position and the calibration load, so that the ratio of the test load to the target load is in a preset range, and determining the test load.
6. Method for testing the fatigue of a blade of a wind park according to claim 5, wherein the test load M is determined by expression (3)eqt，
Wherein R isk,cIs the compressive strength of the material, gammam，short termIs the fractional coefficient of the material, Sk，AtFor the amplified amplitude, Sk，MtIs the mean value of the test load.
7. The blade fatigue testing method of the wind generating set according to claim 1, wherein the step S4 includes:
and carrying out single-point loading on the blade according to the calibration position and the calibration load to obtain a linear relation between the calibration load and the blade strain, and converting the linear relation to obtain the section strain of each section corresponding to the test load.
8. The blade fatigue testing method of the wind generating set according to claim 1, wherein the step S4 further comprises: and in the testing process, carrying out damage statistics according to the testing load and the target load, so that the actual vibration times of each section reach the required testing fatigue times.
9. A blade fatigue testing system of a wind generating set, characterized in that the blade fatigue testing system comprises:
a load determining device that determines a target load including a mean value of a blade to be tested, and determines a test load including a mean value by adjusting a position of an excitation point, a position of a counterweight, and a size of the counterweight so that a ratio of the test load to the target load is within a predetermined range;
the vibration exciter is arranged on the blade at the position of the vibration exciting point obtained by adjustment, so that the testing area of the blade vibrates;
a weight having a weight size obtained by the adjusting and mounted to the blade at a weight position obtained by the adjusting;
a sensor that senses strain of the blade and outputs a sensing signal to a control device;
a control device that controls an excitation force of the vibration exciter according to the sensing signal so that a plurality of sections in the test region reach a section strain corresponding to the test load.
10. The blade fatigue testing system of a wind generating set according to claim 9, wherein the load determining means further determines a mean value of the test load according to the self weight of the blade and the size of the weight, and amplifies the amplitude of the mode shape of the blade.
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104978453A (en) * | 2015-06-18 | 2015-10-14 | 广东明阳风电产业集团有限公司 | Fan authentication test system analysis platform |
| CN105466672A (en) * | 2014-09-12 | 2016-04-06 | 中航惠腾风电设备股份有限公司 | Fatigue test method of wind wheel blade and application of method in full-size fatigue test |
| CN105701337A (en) * | 2015-12-31 | 2016-06-22 | 北京金风科创风电设备有限公司 | Fatigue life prediction method and device for wind turbine generator |
| CN107038311A (en) * | 2017-04-21 | 2017-08-11 | 中国科学院工程热物理研究所 | A kind of resonant Fatigue Testing Loads collocation method of pneumatic equipment bladess |
| CN110231162A (en) * | 2019-07-22 | 2019-09-13 | 上海电气风电集团有限公司 | The method for testing fatigue of wind electricity blade |
-
2019
- 2019-12-23 CN CN201911337847.8A patent/CN113029480B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105466672A (en) * | 2014-09-12 | 2016-04-06 | 中航惠腾风电设备股份有限公司 | Fatigue test method of wind wheel blade and application of method in full-size fatigue test |
| CN104978453A (en) * | 2015-06-18 | 2015-10-14 | 广东明阳风电产业集团有限公司 | Fan authentication test system analysis platform |
| CN105701337A (en) * | 2015-12-31 | 2016-06-22 | 北京金风科创风电设备有限公司 | Fatigue life prediction method and device for wind turbine generator |
| CN107038311A (en) * | 2017-04-21 | 2017-08-11 | 中国科学院工程热物理研究所 | A kind of resonant Fatigue Testing Loads collocation method of pneumatic equipment bladess |
| CN110231162A (en) * | 2019-07-22 | 2019-09-13 | 上海电气风电集团有限公司 | The method for testing fatigue of wind electricity blade |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN113624428A (en) * | 2021-07-27 | 2021-11-09 | 中国科学院工程热物理研究所 | Resonance type double-shaft fatigue loading method for wind turbine blade |
| CN113624428B (en) * | 2021-07-27 | 2023-11-10 | 中国科学院工程热物理研究所 | Wind turbine blade resonance type double-shaft fatigue loading method |
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