CN115824606A - Wind power blade double-shaft fatigue loading frequency adjusting device, method and system - Google Patents
Wind power blade double-shaft fatigue loading frequency adjusting device, method and system Download PDFInfo
- Publication number
- CN115824606A CN115824606A CN202211487611.4A CN202211487611A CN115824606A CN 115824606 A CN115824606 A CN 115824606A CN 202211487611 A CN202211487611 A CN 202211487611A CN 115824606 A CN115824606 A CN 115824606A
- Authority
- CN
- China
- Prior art keywords
- blade
- mass
- shimmy
- adjusting device
- wind power
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000000034 method Methods 0.000 title claims abstract description 29
- 238000003860 storage Methods 0.000 claims description 17
- 238000004590 computer program Methods 0.000 claims description 12
- 238000004364 calculation method Methods 0.000 claims description 7
- 150000001875 compounds Chemical class 0.000 claims description 6
- 230000005611 electricity Effects 0.000 claims description 2
- 230000033001 locomotion Effects 0.000 description 17
- 230000005284 excitation Effects 0.000 description 16
- 238000010586 diagram Methods 0.000 description 11
- 238000009661 fatigue test Methods 0.000 description 10
- 238000012360 testing method Methods 0.000 description 8
- 230000006870 function Effects 0.000 description 5
- 238000004519 manufacturing process Methods 0.000 description 5
- 238000012545 processing Methods 0.000 description 5
- 238000013461 design Methods 0.000 description 4
- 238000005452 bending Methods 0.000 description 3
- 238000009826 distribution Methods 0.000 description 3
- 230000007547 defect Effects 0.000 description 2
- 230000009977 dual effect Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000004458 analytical method Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000025518 detection of mechanical stimulus involved in sensory perception of wind Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 230000003287 optical effect Effects 0.000 description 1
- 238000011056 performance test Methods 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Images
Classifications
-
- 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
- Wind Motors (AREA)
Abstract
The invention provides a device, a method and a system for adjusting double-shaft fatigue loading frequency of a wind power blade, wherein the device, the method and the system comprise the following steps: the device comprises a waving direction loading frequency adjusting device, a shimmy direction loading frequency adjusting device, a supporting structure arranged on a foundation and a clamp; the shimmy direction loading frequency adjusting device comprises a first additional mass block; the flapping direction loading frequency adjusting device comprises a second additional mass block; the shimmy direction loading frequency adjusting device is arranged on the supporting structure and is connected with one side of the clamp parallel to the foundation from the direction vertical to the foundation; and/or the waving direction loading frequency adjusting device is arranged on the supporting structure, and the waving direction loading frequency adjusting device is connected with one side, which is vertical to the clamp and close to the foundation, from the direction parallel to the foundation; the independence of the adjusting device in the shimmy direction and the flap direction is realized by arranging the additional mass block on the device outside the blade, and the natural frequencies of the adjusting device cannot influence each other when the frequency is adjusted.
Description
Technical Field
The invention belongs to the technical field of experimental detection of wind generating sets, and particularly relates to a device, a method and a system for adjusting double-shaft fatigue loading frequency of a wind power blade.
Background
The blade is required to have higher fatigue strength and mechanical property due to the fact that the blade runs in a severe environment for a long time, and therefore the fatigue property test of the blade is very necessary. At present, the blade is dynamically loaded by adopting a mass block resonance mode generally, and the loading direction is generally a single shimmy or flap direction. However, along with the design and manufacture of large and ultra-large offshore wind power blades, the loading mode of the eccentric mass block gradually shows the defects of uneven blade load distribution, over-small excitation force, overlong period and the like. The design life of the blade specified in the Chinese national standard GB/T25383 wind generating set-wind wheel blade is more than or equal to 20 years of service life. In practice the useful life of a blade depends to a large extent on its fatigue life, fatigue failure being one of the most significant failure modes of a blade. In order to ensure that the actual service life of the blade is not less than the design life, the fatigue performance test needs to be carried out on the blade before the blade is in service. The fatigue test is the most direct and reliable method for verifying the fatigue life of the blade at present.
The blade fatigue test is generally based on the design bending moment along the spanwise direction of the blade, and the single-point excitation is adopted to carry out the pertinence test on the dangerous area of the blade. With the large size of the blade, the single-point loading fatigue test can not meet the actual requirement. The blade test standard requires that the blade must be fatigue tested for at least 40% of the blade cross section, and even the entire length, before it can be shipped. In order to accurately grasp the damage condition of the blade in the designed life period, the quality and the service life of the blade can be effectively verified only by carrying out full-scale fatigue test on the blade under the condition that the test bending moment is closer to the target bending moment. The fatigue test aims at evaluating the fatigue life of the blades of the wind turbine generator and is an important link for realizing the performance certification of the blades. The wind load is a multi-directional time-varying load, and the mode excitation and fatigue mode obtained under single excitation are different from the multi-excitation condition, so that the simulation of the actual multi-excitation vibration environment by adopting a single-axis loading test is incomplete.
In order to adapt to the development trend of producing and manufacturing large and ultra-large offshore wind power blades, the biaxial fatigue loading mode is more and more emphasized. And the multi-directional loading mode is adopted to simultaneously apply exciting force to the blades, so that the wind load can be more truly equivalent, and the blade loading test period is shortened. Most production and manufacturing companies of known blades in the world have double-shaft fatigue testing equipment, the types of the equipment mainly comprise a forced displacement type and a forced resonance type, but the fatigue loading control system in the current corresponding fatigue loading device has the problems of low efficiency, complex control and the like.
In the fatigue test of the blade, it is necessary to perform simple harmonic excitation in accordance with the natural frequency of the blade in the loading direction, thereby generating resonance and loading by the dynamic load generated by the resonance. The following problems exist in the test:
(1) The excitation frequency cannot reach the natural frequency of blade shimmy or flap due to the capacity limitation of the excitation device, so the natural frequency of the blade needs to be adjusted to be within the frequency range of the excitation device;
(2) Because the natural frequencies of the blade in the shimmy and flap directions are different, in a fatigue test, after the motions in the two directions are synthesized, the motion trail of the blade is complex, so that the load distribution of the blade is difficult to analyze and control, and the frequencies in the shimmy and flap directions need to be adjusted to be consistent.
Disclosure of Invention
In order to overcome the defects of the prior art, the invention provides a wind power blade double-shaft fatigue loading frequency adjusting device, which comprises: the swinging direction loading frequency adjusting device, the shimmy direction loading frequency adjusting device, a supporting structure arranged on the foundation and a clamp;
the shimmy direction loading frequency adjusting device comprises a first additional mass block, and the mass of the first additional mass block is determined by a natural frequency adjusting target of the wind power blade in the shimmy direction; the flap direction loading frequency adjusting device comprises a second additional mass block, and the mass of the second additional mass block is determined by a natural frequency adjusting target of the wind power blade in the flap direction;
the clamp is clamped on the outer side of the wind power blade;
the shimmy direction loading frequency adjusting device is arranged on the supporting structure and is connected with one side of the clamp parallel to the foundation from the direction vertical to the foundation; and/or the waving direction loading frequency adjusting device is arranged on the supporting structure, and the waving direction loading frequency adjusting device is connected with one side, perpendicular to the clamp and close to the foundation, of the clamp from the direction parallel to the foundation.
Preferably, the first additional mass and the second additional mass each comprise a plurality of sheet-like structures, which are stacked one above the other.
Preferably, the shimmy direction loading frequency adjusting device further includes: the first balance rod, the first balance fixing device and the first loading connecting rod are of a rod-shaped structure; the first balancing rod is of a plate-shaped structure, and one end of the plate-shaped structure is connected to one side, perpendicular to the clamp and close to the foundation, in a sliding mode through a first loading connecting rod;
one side of the middle part of the plate-shaped structure, which is far away from the clamp, is arranged on the supporting structure;
the first additional mass blocks are divided into two groups, and the two groups have the same mass; the two groups of the clamping devices are respectively fixed at two ends of the plate-shaped structure and are far away from one side of the clamp.
Preferably, one end of the first loading connecting rod facing the clamp is provided with a first sliding block; the first slider slides in the horizontal direction of the jig.
Preferably, the support structure comprises a base;
the base sets up on the ground, first balanced fixing device is fixed in the base is kept away from one side of ground.
Preferably, the first balance fixing device is hinged with the first balance rod.
Preferably, the flap-direction loading frequency adjusting apparatus further includes: the second balance rod, the second balance fixing device and the second loading connecting rod are of rod-shaped structures; the second balance rod is of a plate-shaped structure, and one end of the plate-shaped structure is connected to one side, parallel to the foundation, of the clamp in a sliding mode through a second loading connecting rod;
the middle part of the plate-shaped structure is arranged on the supporting structure towards one side of the clamp;
the second additional mass blocks are at least two groups, and the masses of the two groups are the same; the two groups of the clamping devices are respectively fixed at two ends of the plate-shaped structure and are far away from one side of the clamp.
Preferably, one end of the second loading connecting rod far away from the second balance rod comprises a second sliding block; the second sliding block slides along the vertical direction of the clamp.
Preferably, the support structure comprises: the device comprises a base and a supporting plate which is positioned at one end of the base and is vertical to the base;
the base is arranged on the foundation, and the second balance fixing device is fixed on one side, far away from the base, of the supporting plate.
Preferably, the second balance fixing device is hinged with the second balance rod.
Based on the same invention concept, the invention also provides a wind power blade double-shaft fatigue loading frequency adjusting method, which comprises the following steps:
calculating the mass of a first additional mass block in the wind power blade double-shaft fatigue loading frequency adjusting device based on the swing natural frequency to be achieved; the mass of the first additional mass block is used as the additional mass in the flapping direction to adjust the natural frequency of the wind power blade in the flapping direction;
and/or the presence of a gas in the gas,
calculating the mass of a second additional mass block in the wind power blade double-shaft fatigue loading frequency adjusting device based on the shimmy natural frequency to be achieved; adjusting the natural frequency of the wind power blade in the shimmy direction by taking the mass of the second additional mass block as the additional mass in the shimmy direction;
the shimmy natural frequency or the flap natural frequency is obtained by calculation according to basic parameters of the wind power blade; the wind power blade double-shaft fatigue loading frequency adjusting device is the wind power blade double-shaft fatigue loading frequency adjusting device.
Preferably, the basic parameters of the wind power blade include: the blade mass, the rigidity of the wind power blade in the shimmy direction and the blade rigidity of the wind power blade in the flapping direction.
Preferably, the mass of the first additional mass is calculated as follows:
in the formula (I), the compound is shown in the specification,
in order to be the natural frequency of the shimmy,
for the blade stiffness in the shimmy direction,
as to the mass of the blade, the blade is,
is the mass of the first additional mass.
Preferably, the mass of the second additional mass is calculated as follows:
in the formula (I), the compound is shown in the specification,
in order to wave the natural frequency,
in order to impart directional blade stiffness,
as to the mass of the blade, the blade is,
the mass of the second additional mass.
Based on the same invention concept, the invention also provides a wind power blade double-shaft fatigue loading frequency adjusting system, which comprises:
the flapping natural frequency calculating module is used for calculating the mass of a first additional mass block in the wind power blade double-shaft fatigue loading frequency adjusting device based on the to-be-achieved flapping natural frequency;
the shimmy natural frequency calculating module is used for calculating the mass of a second additional mass block in the wind power blade double-shaft fatigue loading frequency adjusting device based on the shimmy natural frequency to be achieved;
the shimmy natural frequency or the flap natural frequency is obtained by calculation according to basic parameters of the wind power blade; the wind power blade double-shaft fatigue loading frequency adjusting device is the wind power blade double-shaft fatigue loading frequency adjusting device.
Based on the same invention concept, the invention also provides computer equipment for adjusting the double-shaft fatigue loading frequency of the wind power blade, which comprises the following steps: one or more processors;
a memory for storing one or more programs;
when the one or more programs are executed by the one or more processors, the wind turbine blade biaxial fatigue loading frequency adjustment method is realized.
Based on the same inventive concept, the invention further provides a computer-readable storage medium for adjusting the wind turbine blade double-shaft fatigue loading frequency, wherein a computer program is stored on the computer-readable storage medium, and when the computer program is executed, the wind turbine blade double-shaft fatigue loading frequency adjusting method is realized.
Compared with the closest prior art, the invention has the following beneficial effects:
the invention provides a device, a method and a system for adjusting double-shaft fatigue loading frequency of a wind power blade, wherein the device, the method and the system comprise the following steps: the device comprises a waving direction loading frequency adjusting device, a shimmy direction loading frequency adjusting device, a supporting structure arranged on a foundation and a clamp; the shimmy direction loading frequency adjusting device comprises a first additional mass block, and the mass of the first additional mass block is determined by a natural frequency adjusting target of the wind power blade in the shimmy direction; the flap direction loading frequency adjusting device comprises a second additional mass block, and the mass of the second additional mass block is determined by a natural frequency adjusting target of the wind power blade in the flap direction; the clamp is clamped on the outer side of the wind power blade; the shimmy direction loading frequency adjusting device is arranged on the supporting structure and is connected with one side of the clamp parallel to the foundation from the direction vertical to the foundation; and/or the waving direction loading frequency adjusting device is arranged on the supporting structure, and the waving direction loading frequency adjusting device is connected with one side, which is perpendicular to the clamp from the direction parallel to the foundation and is close to the foundation; according to the invention, the control device controls the additional mass block on the shimmy frequency adjusting device in the loading frequency adjusting device, so that the mass compensation is carried out on the blade in the shimmy direction, and the loading frequency of the blade in the shimmy direction is further adjusted; the additional mass block is arranged on the device outside the blade, so that the independence of the adjusting device in the shimmy direction and the flap direction is realized, and the natural frequencies of the adjusting device cannot influence each other when the frequency adjustment in the two directions is carried out.
Drawings
FIG. 1 is a schematic view of a biaxial fatigue loading experiment of a wind turbine blade provided by the invention;
FIG. 2 is a schematic view of a wind turbine blade fatigue loading frequency adjusting device provided by the invention;
FIG. 3 is a schematic diagram of a frequency adjustment apparatus provided in the present invention;
FIG. 4 is a schematic diagram of a shimmy frequency adjusting device provided by the present invention;
FIG. 5 is a schematic view of a swing frequency adjustment apparatus provided in the present invention;
FIG. 6 is a schematic view of an alternative arrangement of a shimmy and flap dual axis frequency adjustment arrangement provided by the present invention;
FIG. 7 is a schematic flow chart of a method for adjusting the double-shaft fatigue loading frequency of a wind turbine blade according to the present invention;
FIG. 8 is a schematic structural diagram of a double-shaft fatigue loading frequency adjusting system for a wind turbine blade according to the present invention;
FIG. 9 is a schematic diagram of a frequency adjustment scheme according to the present invention
The motion trail of the centroid of the blade;
FIG. 10 is a schematic view of the present invention
The moving track of the center of mass of the blade is determined;
FIG. 11 is a schematic view of the present invention
The moving track of the center of mass of the blade is determined;
FIG. 12 is a schematic view of the present invention
The moving track of the center of mass of the blade is determined;
FIG. 13 is a schematic view of the present invention
When the blade moves, the center of mass of the blade moves along the track;
FIG. 14 is a schematic view of the present invention
The moving track of the center of mass of the blade is determined;
description of reference numerals:
1-frequency adjusting module, 201-first loading connecting rod, 202-first balance rod, 203-first additional mass, 204-first balance fixing device, 301-second loading connecting rod, 302-second balance rod, 303-second additional mass, 304-second balance fixing device, 401-first sliding block, 402-second sliding block, 5-supporting plate, 6-wind power blade, 7-clamp, 8-foundation, 9-balance rod hinge point and 10-base.
Detailed Description
The following describes embodiments of the present invention in further detail with reference to the accompanying drawings.
Example 1:
the invention provides a wind power blade double-shaft fatigue loading frequency adjusting device, which can be used for adjusting the double-shaft natural frequency of a wind power blade, focuses on a frequency adjusting method in a blade fatigue test, but does not adopt a loading mode, and can independently compensate the mass of the wind power blade 6 in the swinging and waving directions by performing the wind power blade fatigue loading test shown in figure 1, and the wind power blade fatigue loading frequency adjusting device can independently adjust the natural frequency in the swinging and waving directions of the wind power blade 6 shown in figure 2. The schematic diagram of the frequency adjusting device is shown in fig. 3, and the frequency adjusting device comprises: the swinging direction loading frequency adjusting device, the shimmy direction loading frequency adjusting device, a supporting structure arranged on a foundation 8 and a clamp 7;
the shimmy direction loading frequency adjusting device comprises a first additional mass 203, and the mass of the first additional mass 203 is determined by a natural frequency adjusting target of the wind power blade 6 in the shimmy direction; the flap direction loading frequency adjusting device comprises a second additional mass block 303, and the mass of the second additional mass block 303 is determined by the natural frequency adjusting target of the wind power blade 6 in the flap direction;
the clamp 7 is clamped on the outer side of the wind power blade 6;
the shimmy direction loading frequency adjusting device is arranged on the supporting structure and is connected with one side of the clamp 7 parallel to the foundation 8 from the direction vertical to the foundation 8; and/or the waving direction loading frequency adjusting device is arranged on the supporting structure, and the waving direction loading frequency adjusting device is connected with one side, which is perpendicular to the clamp 7 and is close to the foundation 8, from the direction parallel to the foundation 8.
When a double-shaft fatigue test of the wind power blade is carried out, external periodic excitation loads are applied to the flapping and the shimmy directions of the blade at the same time, and the frequency of the excitation loads is respectively equal to the natural frequency of the blade in the flapping and the shimmy directions; the aim is to generate resonance in the flapping and shimmy directions and carry out double-shaft dynamic loading on the blade by utilizing the resonance of the structure.
In particular, the first additional mass 203 and the second additional mass 303 each comprise a plurality of sheet-like structures, which are stacked one on top of the other.
The mass block is a laminated structure, can increase or reduce the number of the laminated plates, changes the additional mass in the shimmy and/or swing direction, and is fixed at the two ends of the balancing pole.
Specifically, as shown in fig. 4, the shimmy direction loading frequency adjusting device further includes: a first balance bar 202, a first balance fixture 204, and a first load link 201 having a rod-like structure; the first balance bar 202 is a plate-shaped structure, and one end of the plate-shaped structure is slidably connected to one side, perpendicular to the clamp 7 and close to the foundation 8, through a first loading connecting rod 201;
one side of the middle part of the plate-shaped structure, which is far away from the clamp 7, is arranged on a supporting structure;
the first additional masses 203 are two groups, and the masses of the two groups are the same; the two groups are respectively fixed at two ends of the plate-shaped structure and are far away from one side of the clamp 7.
The first balance bar 202 is provided with a balance bar hinge point 9 at the middle position, and the balance bar hinge point 9 adopts a spherical bearing.
The two ends of the first balance rod 202 are provided with first additional masses 203 with equal mass, and the upper end of the balance rod hinge point 9 on the first balance rod 202 is connected with the first connecting rod 201 by adopting a spherical hinge for adjusting the additional mass of the blade in the swing direction motion.
Specifically, a first sliding block 401 is arranged at one end of the first loading connecting rod 201 facing the clamp 7; the first slider 401 slides in the horizontal direction of the jig 7.
First connecting rod 201 is used for transmitting the motion of wind-powered electricity generation blade 6 shimmy direction for anchor clamps 7 cross-section and first balancing pole 202 upper end synchronous motion, first connecting rod 201 and first balancing pole 202 adopt spherical hinged joint, and first slider 401 is fixed to the other end, and first slider 401 is installed on anchor clamps 7, only can follow anchor clamps 7 edge side-to-side movement.
In particular, the support structure comprises a base 10;
the base 10 is disposed on the foundation 8, and the first balancing fixing device 204 is fixed on a side of the base 10 away from the foundation 8.
Specifically, the first balance fixing device 204 is hinged to the first balance bar 202.
Wherein the base 10 is a base 10 of the entire mass compensation device for supporting the first balance bar 202;
the base 10 is fixed on the foundation 8, and the position of the base can be adjusted along the length direction of the blade according to actual requirements;
the fixture 7 is fixed on the cross section of the wind power blade 6, a spherical hinge is arranged between the fixture 7 and the first loading connecting rod 201, and the motion of the cross section of the wind power blade 6 is transmitted to the first loading connecting rod 201.
Specifically, as shown in fig. 5, the flap-direction loading frequency adjusting apparatus further includes: a second balance bar 302, a second balance fixing means 304, and a second load link 301 having a rod-shaped structure; the second balance bar 302 is a plate-shaped structure, and one end of the plate-shaped structure is slidably connected to one side of the clamp 7 parallel to the foundation 8 through a second loading connecting rod 301;
the middle part of the plate-shaped structure is arranged on the supporting structure towards one side of the clamp 7;
the second additional masses 303 are at least two groups, and the masses of the two groups are the same; the two groups are respectively fixed at two ends of the plate-shaped structure and are far away from one side of the clamp 7.
The second balance bar 302 is provided with a balance bar hinge point 9 at the middle position, and the balance bar hinge point 9 adopts a spherical bearing.
And second additional masses 303 with equal mass are mounted at two ends of the second balance bar 302, and the upper end of a balance bar hinge point 9 on the second balance bar 302 is connected with the second connecting rod 301 by adopting a spherical hinge for adjusting the additional mass when the blade swings in the direction, so that the gravity of the additional mass does not act on the blade.
Specifically, one end of the second loading link 301 away from the second balance bar 302 includes a second slider 402; the second slider 402 slides in the vertical direction of the jig 7.
The second connecting rod 301 is used for transmitting the motion of the wind power blade 6 in the waving direction, so that the section of the clamp 7 and the upper end of the second balance bar 302 synchronously move, the second connecting rod 301 and the second balance bar 302 are connected by adopting a spherical hinge, the other end of the second connecting rod is fixed with a second sliding block 402, and the second sliding block 402 is installed on the clamp 7 and can only move up and down along the edge of the clamp 7.
Specifically, the support structure includes: the device comprises a base 10 and a supporting plate 5 which is positioned at one end of the base 10 and is vertical to the base 10;
the base 10 is disposed on a foundation 8, and the second balancing fixture 304 is fixed to a side of the supporting plate 5 away from the base 10.
Specifically, the second balance fixing device 304 is hinged to the second balance bar 302.
Wherein the base 10 is used for supporting the supporting plate 5 and the second balance bar 302 arranged on the supporting plate 5;
the base 10 is fixed on the foundation 8, and the position of the base can be adjusted along the length direction of the blade according to actual requirements;
the clamp 7 is fixed on the section of the wind power blade 6, and a spherical hinge is arranged between the clamp 7 and the second loading connecting rod 301, so that the motion of the section of the wind power blade 6 is transmitted to the second loading connecting rod 201.
Base 11: is a base of the whole mass compensation device and is used for supporting the shimmy balancing pole and the supporting plate;
foundation 12: the base is fixed on the foundation, and the position of the base can be adjusted along the length direction of the blade according to actual requirements;
a clamp 13: the spherical hinge is fixed on the section of the blade and between the spherical hinge and the connecting rod, and the spherical hinge transmits the motion of the section of the blade to the connecting rod.
Example 2:
the present invention also provides an alternative to the shimmy and flap dual axis frequency tuning device, as shown in fig. 6; additional mass
The second additional mass 303 mentioned for the above embodiment; additional mass
The first additional mass 203 mentioned for the above embodiments.
The mass of the second additional mass 303 when the blade vibrates
Mass 203 of the first additional mass acting only in the flapping direction
The blade can only act in the shimmy direction, and the mode of the sliding mass block can be adopted to simultaneously realize the independent adjustment of the natural frequency of the blade in the shimmy and flap directions.
The compensating mass block in the waving direction can only move along the waving direction, namely along the Y axis and cannot move along the Z axis, so that the additional mass is ensured to act only in the waving direction, and the mass in the waving direction is increased
The quality in the shimmy direction is not affected.
The compensating mass block in the shimmy direction can only move in the shimmy direction, namely along the Z axis and can not move in the Y axis direction, thereby ensuring that the additional mass only acts in the flapping direction, and equivalently, the mass in the shimmy direction is increased
The quality of the waving direction is not affected.
However, the additional mass may be subject to additional gravitational forces in the Z direction due to gravitational forces.
Example 3:
based on the same invention concept, the invention also provides a wind power blade double-shaft fatigue loading frequency adjusting method.
The flow of the method is shown in fig. 7, and includes: calculating the mass of a first additional mass block 203 in the wind power blade biaxial fatigue loading frequency adjusting device based on the flap natural frequency to be achieved; the natural frequency of the wind power blade 6 in the flapping direction is adjusted by taking the mass of the first additional mass 203 as the additional mass in the flapping direction;
and/or the presence of a gas in the gas,
calculating the mass of a second additional mass block 303 in the wind turbine blade biaxial fatigue loading frequency adjusting device based on the shimmy natural frequency to be achieved; the natural frequency of the wind power blade 6 in the shimmy direction is adjusted by taking the mass of the second additional mass block 303 as the additional mass in the shimmy direction;
wherein the shimmy natural frequency or the flap natural frequency is obtained by calculation according to basic parameters of the wind power blade 6; the wind power blade double-shaft fatigue loading frequency adjusting device is the wind power blade double-shaft fatigue loading frequency adjusting device.
Specifically, the basic parameters of the wind power blade 6 include: the blade mass, the rigidity of the wind power blade in the shimmy direction and the blade rigidity of the wind power blade in the flapping direction.
Specifically, the mass of the first additional mass 203 is calculated as follows:
in the formula (I), the compound is shown in the specification,
in order to control the natural frequency of the shimmy,
for the blade stiffness in the shimmy direction,
as to the mass of the blade, the blade is,
is the mass of the first additional mass 203.
When the shimmy mass compensation mode is adopted, the support plate and the hinge point fixing device, the shimmy balancing bar, the waving balancing bar, the mass block and the connecting rod which are connected with the support plate are all detached, and only relevant shimmy compensation structures are reserved; the distances between the hinge point in the middle of the balancing rod and the mass blocks at the two ends are the same, namely
The masses of the mass blocks at both ends are
。
In the working mode, the equivalent is to increase the section position of the blade
And the accessory mass is only active when the blade is shimmy. This mode only changes the natural frequency of blade edgewise, not the natural frequency of flapping.
In the direction of the shimmy, the vibration,
as to the mass of the blade, the blade is,
in order to damp the shimmy motion,
in order to provide rigidity in the direction of shimmy,
the excitation is simple harmonic excitation in the external shimmy direction.
Virgin biomassWhen the amount is compensated, the equivalent motion equation of the blade shimmy direction is
First order natural frequency of shimmy
Frequency of excitation
When this happens, the system resonates.
The number of sheet structures is determined according to the mass and then stacked to form a mass.
When mass compensation is carried out, the mass compensation is increased in the shimmy direction
After addition of mass, first order natural frequency of shimmy
First order natural frequency of blade shimmy
Reducing, at the moment, the external shimmy excitation frequency
And may be reduced appropriately.
Specifically, the mass calculation formula of the second additional mass 303 is as follows:
in the formula (I), the compound is shown in the specification,
in order to swing the natural frequency of the wave,
in order to impart directional blade stiffness,
as to the mass of the blade, the blade is,
is the mass of the second additional mass 303.
When the waving frequency adjusting mode is adopted for working, the shimmy balancing pole and all the parts connected with the shimmy balancing pole are detached. The distances between the hinge point in the middle of the balancing rod and the mass blocks at the two ends are the same, namely
The masses of the mass blocks at both ends are
。
In the working mode, the equivalent is to increase the section position of the blade
And the attachment mass only works when the blade is flap. This mode only changes the natural frequency of blade flapping and does not change the natural frequency of edgewise vibration.
When the frequency is not adjusted, in the flapping direction,
as to the mass of the blade, the blade is,
in order to damp the flapping motion,
in order to impart directional rigidity to the blade,
the excitation is simple harmonic to the external flap direction. First order natural frequency of waving
Frequency of excitation
When this happens, the system resonates.
The number of sheet structures is determined according to the mass and then stacked to form a mass.
When frequency is adjusted, the waving direction is increased
After additional mass, first-order flap natural frequency
First order flap natural frequency of blade
Reducing, at the same time, the external flap excitation frequency
Should also be reduced.
When working in a dual-axis frequency regulation mode, waving additional mass
And pendulum vibration additional mass
Can be flexibly adjusted without influencing each other. Equivalent to increase the flapping direction at the blade section position
Added mass of in the direction of shimmy
Additional mass of (2). Waving simple harmonic excitation
Excitation frequency and natural flapping frequency of
Same, simple harmonic excitation of shimmy
Excitation frequency and natural frequency of shimmy
The same is true.
By imparting additional mass
And pendulum vibration additional mass
To adjust the size of
And
the magnitude relation of (1) when
The motion rule of the blade is simplest, and the control of dynamic load is easier.
Example 4:
based on the same inventive concept, the invention also provides a wind power blade double-shaft fatigue loading frequency adjusting system shown in fig. 8, which is characterized by comprising the following components:
the flapping natural frequency calculating module is used for calculating the mass of a first additional mass block 203 in the wind power blade double-shaft fatigue loading frequency adjusting device based on the to-be-achieved flapping natural frequency;
the shimmy natural frequency calculating module is used for calculating the mass of a second additional mass block 303 in the wind power blade double-shaft fatigue loading frequency adjusting device based on the shimmy natural frequency to be achieved;
wherein the shimmy natural frequency or the flap natural frequency is obtained by calculation according to basic parameters of the wind power blade 6; the wind power blade double-shaft fatigue loading frequency adjusting device is the wind power blade double-shaft fatigue loading frequency adjusting device.
Example 5:
in order to prove the method for adjusting the double-shaft fatigue loading frequency of the wind power blade provided by the invention; the loading frequency adjustment method proposed by the present invention is explained below by a specific example
When the frequency adjustment is not performed, because
After the blade is synthesized in the shimmy and flap directions, the motion trail is complex, the distribution of load values on the blade is difficult to control, and great difficulty is brought to the fatigue characteristic analysis of the blade, as shown in fig. 9.
When the frequency of the two shafts is adjusted, the two shafts are driven to rotate
The blade vibrates in the same frequency in the shimmy and flap directions through control
And with
Phase difference between
The motion track of the center of mass of the blade in the loading plane is more regular; when the phase difference is different, the moving tracks of the centers of mass of the blades are also different.
When in use
，
The moving track of the center of mass of the blade is shown in FIG. 10;
when in use
，
The moving track of the center of mass of the blade is shown in FIG. 11;
when in use
，
The moving track of the center of mass of the blade is shown in FIG. 12;
when in use
，
When the moving track of the center of mass of the blade is shown in FIG. 13;
when in use
，
The locus of travel of the centroid of the blade is shown in figure 14.
Example 6:
based on the same inventive concept, the present invention also provides a computer device comprising a processor and a memory, the memory being configured to store a computer program comprising program instructions, the processor being configured to execute the program instructions stored by the computer storage medium. The Processor may be a Central Processing Unit (CPU), or may be other general purpose Processor, a Digital Signal Processor (DSP), an Application Specific Integrated Circuit (ASIC), an off-the-shelf Programmable gate array (FPGA) or other Programmable logic device, a discrete gate or transistor logic device, a discrete hardware component, etc., which is a computing core and a control core of the terminal, and is specifically adapted to implement one or more instructions, and specifically adapted to load and execute one or more instructions in a computer storage medium so as to implement a corresponding method flow or a corresponding function, so as to implement the steps of the wind turbine blade two-axis fatigue loading frequency adjusting method in the foregoing embodiments.
Example 7:
based on the same inventive concept, the present invention further provides a storage medium, in particular a computer readable storage medium (Memory), which is a Memory device in a computer device and is used for storing programs and data. It is understood that the computer readable storage medium herein can include both built-in storage media in the computer device and, of course, extended storage media supported by the computer device. The computer-readable storage medium provides a storage space storing an operating system of the terminal. Also, one or more instructions, which may be one or more computer programs (including program code), are stored in the memory space and are adapted to be loaded and executed by the processor. It should be noted that the computer-readable storage medium may be a high-speed RAM memory, or may be a non-volatile memory (non-volatile memory), such as at least one disk memory. One or more instructions stored in a computer-readable storage medium can be loaded and executed by a processor to implement the steps of the wind turbine blade dual-axis fatigue loading frequency adjusting method in the above embodiments.
As will be appreciated by one skilled in the art, embodiments of the present invention may be provided as a method, system, or computer program product. Accordingly, the present invention may take the form of an entirely hardware embodiment, an entirely software embodiment or an embodiment combining software and hardware aspects. Furthermore, the present invention may take the form of a computer program product embodied on one or more computer-usable storage media (including, but not limited to, disk storage, CD-ROM, optical storage, and the like) having computer-usable program code embodied therein.
The present invention is described with reference to flowchart illustrations and/or block diagrams of methods, apparatus (systems), and computer program products according to embodiments of the invention. It will be understood that each flow and/or block of the flowchart illustrations and/or block diagrams, and combinations of flows and/or blocks in the flowchart illustrations and/or block diagrams, can be implemented by computer program instructions. These computer program instructions may be provided to a processor of a general purpose computer, special purpose computer, embedded processor, or other programmable data processing apparatus to produce a machine, such that the instructions, which execute via the processor of the computer or other programmable data processing apparatus, create means for implementing the functions specified in the flowchart flow or flows and/or block diagram block or blocks.
These computer program instructions may also be stored in a computer-readable memory that can direct a computer or other programmable data processing apparatus to function in a particular manner, such that the instructions stored in the computer-readable memory produce an article of manufacture including instruction means which implement the function specified in the flowchart flow or flows and/or block diagram block or blocks.
These computer program instructions may also be loaded onto a computer or other programmable data processing apparatus to cause a series of operational steps to be performed on the computer or other programmable apparatus to produce a computer implemented process such that the instructions which execute on the computer or other programmable apparatus provide steps for implementing the functions specified in the flowchart flow or flows and/or block diagram block or blocks.
It should be noted that the above-mentioned embodiments are only for illustrating the technical solutions of the present invention and not for limiting the protection scope thereof, and although the present invention is described in detail with reference to the above-mentioned embodiments, those skilled in the art should understand that after reading the present invention, they can make various changes, modifications or equivalents to the specific embodiments of the application, but these changes, modifications or equivalents are all within the protection scope of the claims of the application.
Claims (17)
1. The utility model provides a wind-powered electricity generation blade biax fatigue loading frequency adjusting device which characterized in that includes: a waving direction loading frequency adjusting device, a shimmy direction loading frequency adjusting device, a supporting structure arranged on a foundation (8) and a clamp (7);
the shimmy direction loading frequency adjusting device comprises a first additional mass block (203), and the mass of the first additional mass block (203) is determined by a natural frequency adjusting target of the wind power blade (6) in the shimmy direction; the flap direction loading frequency adjusting device comprises a second additional mass block (303), and the mass of the second additional mass block (303) is determined by a natural frequency adjusting target of the wind power blade (6) in the flap direction;
the clamp (7) is clamped on the outer side of the wind power blade (6);
the shimmy direction loading frequency adjusting device is arranged on the supporting structure and is connected with one side of the clamp (7) parallel to the foundation (8) from the direction vertical to the foundation (8); and/or the waving direction loading frequency adjusting device is arranged on the supporting structure, and the waving direction loading frequency adjusting device is connected with one side, perpendicular to the clamp (7) and close to the foundation (8), from the direction parallel to the foundation (8).
2. The device according to claim 1, wherein the first additional mass (203) and the second additional mass (303) each comprise a plurality of sheet-like structures, stacked one on top of the other.
3. The apparatus of claim 1, wherein the shimmy direction loading frequency adjustment means further comprises: a first balance bar (202), a first balance fixing device (204) and a first loading connecting rod (201) with a rod-shaped structure; the first balancing rod (202) is of a plate-shaped structure, and one end of the plate-shaped structure is connected to one side, perpendicular to the clamp (7) and close to the foundation (8), in a sliding mode through a first loading connecting rod (201);
one side of the middle part of the plate-shaped structure, which is far away from the clamp (7), is arranged on a supporting structure;
the first additional masses (203) are divided into two groups, and the masses of the two groups are the same; the two groups of the clamping devices are respectively fixed at two ends of the plate-shaped structure and are far away from one side of the clamp (7).
4. A device according to claim 3, characterized in that the end of the first loading link (201) facing the clamp (7) is provided with a first slider (401); the first slider (401) slides in the horizontal direction of the jig (7).
5. A device according to claim 3, wherein the support structure comprises a base (10);
the base (10) is arranged on a foundation (8), and the first balance fixing device (204) is fixed on one side, far away from the foundation (8), of the base (10).
6. A device according to claim 3, wherein the first counter-fixing means (204) is hinged to the first counter-rod (202).
7. The apparatus of claim 1, wherein the flapwise loading frequency adjustment apparatus further comprises: a second balance bar (302), a second balance fixing device (304) and a second loading connecting rod (301) with a rod-shaped structure; the second balance rod (302) is of a plate-shaped structure, and one end of the plate-shaped structure is connected to one side, parallel to the foundation (8), of the clamp (7) in a sliding mode through a second loading connecting rod (301);
the middle part of the plate-shaped structure is arranged on the supporting structure towards one side of the clamp (7);
the second additional masses (303) are at least two groups, and the masses of the two groups are the same; the two groups of the clamping devices are respectively fixed at two ends of the plate-shaped structure and are far away from one side of the clamp (7).
8. The apparatus as in claim 7, wherein an end of the second load link (301) distal from the second balance bar (302) includes a second slider block (402); the second sliding block (402) slides along the vertical direction of the clamp (7).
9. The apparatus of claim 7, wherein the support structure comprises: the device comprises a base (10) and a supporting plate (5) which is positioned at one end of the base (10) and is vertical to the base (10);
the base (10) is arranged on a foundation (8), and the second balance fixing device (304) is fixed on one side, far away from the base (10), of the supporting plate (5).
10. The device according to claim 7, characterized in that said second balancing fixture (304) is hinged with said second balancing bar (302).
11. A wind power blade double-shaft fatigue loading frequency adjusting method is characterized by comprising the following steps:
calculating the mass of a first additional mass block (203) in the wind turbine blade biaxial fatigue loading frequency adjusting device based on the flap natural frequency to be achieved; the mass of the first additional mass block (203) is taken as the additional mass in the flapping direction to realize the adjustment of the natural frequency of the wind power blade (6) in the flapping direction;
and/or the presence of a gas in the gas,
calculating the mass of a second additional mass block (303) in the wind turbine blade biaxial fatigue loading frequency adjusting device based on the shimmy natural frequency to be achieved; the mass of the second additional mass block (303) is used as the additional mass in the shimmy direction to adjust the natural frequency of the wind power blade (6) in the shimmy direction;
the shimmy natural frequency or the flap natural frequency is obtained by calculation according to basic parameters of the wind power blade (6);
the wind power blade double-shaft fatigue loading frequency adjusting device is as claimed in any one of claims 1 to 10.
12. The method according to claim 11, characterized in that the fundamental parameters of the wind blades (6) comprise: the blade mass, the rigidity of the wind power blade in the shimmy direction and the blade rigidity of the wind power blade in the flapping direction.
13. The method of claim 12, wherein the mass of the first additional mass is calculated as follows:
in the formula (I), the compound is shown in the specification,
in order to control the natural frequency of the shimmy,
for the blade stiffness in the shimmy direction,
as to the mass of the blade, the blade is,
is the mass of the first additional mass (203).
14. The method of claim 12, wherein the mass of the second additional mass is calculated as follows:
in the formula (I), the compound is shown in the specification,
in order to wave the natural frequency,
in order to impart directional blade stiffness,
as to the mass of the blade, the blade is,
is the mass of the second additional mass (303).
15. A wind turbine blade double-shaft fatigue loading frequency adjusting system is characterized by comprising:
the flapping natural frequency calculating module is used for calculating the mass of a first additional mass block (203) in the wind power blade double-shaft fatigue loading frequency adjusting device based on the to-be-achieved flapping natural frequency;
the shimmy natural frequency calculating module is used for calculating the mass of a second additional mass block (303) in the wind power blade double-shaft fatigue loading frequency adjusting device based on the shimmy natural frequency to be achieved;
the shimmy natural frequency or the flap natural frequency is obtained by calculation according to basic parameters of the wind power blade (6); the wind power blade double-shaft fatigue loading frequency adjusting device is as claimed in any one of claims 1 to 10.
16. A wind turbine blade biaxial fatigue loading frequency adjustment computer device, comprising: one or more processors;
a memory for storing one or more programs;
the one or more programs, when executed by the one or more processors, implement the wind blade dual-axis fatigue loading frequency adjustment method of any of claims 11-14.
17. A computer-readable storage medium of a wind turbine blade dual-axis fatigue loading frequency adjustment, characterized in that it has a computer program stored thereon, which when executed, implements the wind turbine blade dual-axis fatigue loading frequency adjustment method according to any of claims 11 to 14.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211487611.4A CN115824606B (en) | 2022-11-25 | 2022-11-25 | Wind power blade double-shaft fatigue loading frequency adjusting device, method and system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211487611.4A CN115824606B (en) | 2022-11-25 | 2022-11-25 | Wind power blade double-shaft fatigue loading frequency adjusting device, method and system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN115824606A true CN115824606A (en) | 2023-03-21 |
| CN115824606B CN115824606B (en) | 2024-03-19 |
Family
ID=85531451
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202211487611.4A Active CN115824606B (en) | 2022-11-25 | 2022-11-25 | Wind power blade double-shaft fatigue loading frequency adjusting device, method and system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN115824606B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117405532A (en) * | 2023-12-12 | 2024-01-16 | 兰州理工大学 | Multifunctional fatigue testing device for blade |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20100263448A1 (en) * | 2007-12-14 | 2010-10-21 | Alliance For Sustainable Energy, Llc. | Dual- axis resonance testing of wind turbine blades |
| US20170241860A1 (en) * | 2014-09-26 | 2017-08-24 | Vestas Wind Systems A/S | Fatigue testing of a wind turbine blade |
| CN112414697A (en) * | 2021-01-25 | 2021-02-26 | 南昌工程学院 | Wind power blade degree of freedom fatigue loading control method, device and system |
| 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 |
| WO2022016907A1 (en) * | 2020-07-21 | 2022-01-27 | 上海电气风电集团股份有限公司 | Two-axis loading fatigue testing method for fan full-size blade and two-axis loading device |
| CN115165281A (en) * | 2022-06-22 | 2022-10-11 | 同济大学 | Decoupling control method for double-shaft fatigue loading of fan blade |
-
2022
- 2022-11-25 CN CN202211487611.4A patent/CN115824606B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20100263448A1 (en) * | 2007-12-14 | 2010-10-21 | Alliance For Sustainable Energy, Llc. | Dual- axis resonance testing of wind turbine blades |
| US20170241860A1 (en) * | 2014-09-26 | 2017-08-24 | Vestas Wind Systems A/S | Fatigue testing of a wind turbine blade |
| WO2022016907A1 (en) * | 2020-07-21 | 2022-01-27 | 上海电气风电集团股份有限公司 | Two-axis loading fatigue testing method for fan full-size blade and two-axis loading device |
| CN112414697A (en) * | 2021-01-25 | 2021-02-26 | 南昌工程学院 | Wind power blade degree of freedom fatigue loading control method, device and system |
| 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 |
| CN115165281A (en) * | 2022-06-22 | 2022-10-11 | 同济大学 | Decoupling control method for double-shaft fatigue loading of fan blade |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117405532A (en) * | 2023-12-12 | 2024-01-16 | 兰州理工大学 | Multifunctional fatigue testing device for blade |
| CN117405532B (en) * | 2023-12-12 | 2024-06-11 | 兰州理工大学 | Multifunctional fatigue testing device for blade |
Also Published As
| Publication number | Publication date |
|---|---|
| CN115824606B (en) | 2024-03-19 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US8601878B2 (en) | Base excitation testing system using spring elements to pivotally mount wind turbine blades | |
| Thomsen et al. | A method for determination of damping for edgewise blade vibrations | |
| US8677827B2 (en) | Wind turbine blade testing system using base excitation | |
| WO2022016907A1 (en) | Two-axis loading fatigue testing method for fan full-size blade and two-axis loading device | |
| Petrović et al. | Advanced control algorithms for reduction of wind turbine structural loads | |
| CN108035237A (en) | The wing plate system and its control method that a kind of suppression Bridge Flutter and whirlpool shake | |
| US8505387B2 (en) | Apparatus and method for applying a cyclical load to an elongate specimen | |
| KR20150119990A (en) | Flapwise fatigue testing method and Dual-axis resornace fatige testing method of a wind turbine blade using excitation in horizontal direction | |
| Li et al. | A piezoelectric–electromagnetic hybrid flutter-based wind energy harvester: Modeling and nonlinear analysis | |
| Krenk et al. | Resonant vibration control of three-bladed wind turbine rotors | |
| CN105416609A (en) | Multi-field coupling testing system and method | |
| CN104568351A (en) | Damping-structure-optimized blade testing experiment table and experimental method thereof | |
| CN201331416Y (en) | Device for measuring rotation inertia and mass center of car power assembly | |
| CN115824606A (en) | Wind power blade double-shaft fatigue loading frequency adjusting device, method and system | |
| He et al. | An investigation on interarea mode oscillations of interconnected power systems with integrated wind farms | |
| CN110231162A (en) | The method for testing fatigue of wind electricity blade | |
| CN103743556A (en) | Testing apparatus for steam turbine blade with shroud ring and boss lashing wire structures | |
| CN204807291U (en) | Rotor test platform of discernment oil film exciting force | |
| CN207987704U (en) | A kind of wing plate system for inhibiting Bridge Flutter and whirlpool to shake | |
| CN220185679U (en) | Vibration damper for generator stator, generator stator and generator | |
| CN103149022A (en) | Multi-axle fatigue tester for vibration type welding nail connecting component | |
| CN103148869B (en) | High overload and linear vibration composite test device | |
| CN115791044B (en) | Double-shaft dynamic loading device, method and system for wind power blade | |
| CN205209757U (en) | Aerogenerator's test fixture | |
| WO2015001405A1 (en) | Static and fatigue testing of wind turbine blades |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |