CN107563041A - A kind of big part static strength fast evaluation method of Wind turbines - Google Patents
A kind of big part static strength fast evaluation method of Wind turbines Download PDFInfo
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Abstract
The invention discloses a kind of big part static strength fast evaluation method of Wind turbines, the intensive analysis database of the corresponding relation of each components of stress and the sharing part of the load of the foundation comprising big part key node；Based on intensive analysis database, the method synthesized using components of stress interpolation and equivalent stress carries out big part static strength rapid evaluation；By being contrasted to the result of fast evaluation method and FInite Element, the error amount of assessment result is calculated, components of stress difference and equivalent stress are synthesized, error amount is modified, obtains static strength appraisal procedure.The present invention is on the basis of big part static strength results accuracy is ensured, it is possible to prevente effectively from replicate analysis work, greatly shortens the time of the big part Static Strength Analysis of Wind turbines.
Description
Technical field
The present invention relates to a kind of big part static strength fast evaluation method of Wind turbines.
Background technology
In recent years, under the promotion of countries in the world wind-powered electricity generation policy and relevant laws and regulations, Wind Power Generation Industry has obtained quick hair
Exhibition.Wind turbines strength analysis calculation is researched and developed as Wind turbines, the core link in manufacturing process, all the time by wind turbine
Group manufacturer, colleges and universities and research institution are paid attention to.
For Wind turbines manufacturer, as the constantly improve of product seriation, newly-built wind field quantity are continuously increased, and institute
The wind field wind-resources situation run into is different, and seat in the plane load variationsization are significantly, it is necessary to carry out substantial amounts of strength assessment work.
Carry out that the workload of Static Strength Analysis is very huge to the big part of Wind turbines, if every time to unknown wind field
The big part of Wind turbines carries out static strength check needs and taken a significant amount of time.If the big strength of parts analysis of blower fan based on the type
Database carries out components of stress interpolation and equivalent stress synthesis, and the big part static strength quickly obtained under specific wind field, seat in the plane should
Power result, it is possible to prevente effectively from the big part of replicate analysis Wind turbines, greatly shortens the big part Static Strength Analysis of Wind turbines
Time.
The content of the invention
The present invention is in order to solve the above problems, it is proposed that a kind of big part static strength fast evaluation method of Wind turbines, this
Invention, it is possible to prevente effectively from replicate analysis work, is greatly shortened on the basis of big part static strength results accuracy is ensured
The time of the big part Static Strength Analysis of Wind turbines.
Further to better illustrate, big part of the invention is wheel hub, main shaft, mainframe and bearing block.
To achieve these goals, the present invention adopts the following technical scheme that：
A kind of big part static strength fast evaluation method of Wind turbines, following steps：
(1) intensive analysis of the corresponding relation of each components of stress and the sharing part of the load comprising big part key node is established
Database；
(2) intensive analysis database is based on, the method synthesized using components of stress interpolation and equivalent stress carries out big part
Static strength rapid evaluation；
(3) by being contrasted to the result of fast evaluation method and FInite Element, the error of assessment result is calculated
Value, components of stress difference and equivalent stress are synthesized, error amount is modified, obtains static strength appraisal procedure.
In the step (1), typical wind turbine model is chosen, obtains the limiting condition of the load of Wind turbines design
Loadmeter.
In the step (1), according to limiting condition loadmeter, the minimum value and maximum of each sharing part of the load are set, most
Small value needs, by including the value envelope in ultimate load table, to build loading condition table, load is divided into multiple grades with maximum
Load successively.
In the step (1), according to the static strength result of finite element under ultimate load, destination node, node are chosen
Main shaft surface stress value is uniformly distributed in more than in the region of setting value.
In the step (1), destination node under each loading condition is calculated using the static strength FEM model of structure
Each components of stress, the corresponding relation between each node stress component and each sharing part of the load is obtained, form intensive analysis data
Storehouse.
In the step (2), according to intensive analysis database, obtain corresponding to the sharing part of the load pair in operating mode by linear interpolation
Certain the destination node components of stress answered, addition obtain the destination node components of stress in the operating mode and made a concerted effort, and utilize Von mises stress
Formula synthesizes to obtain the equivalent stress of the destination node.
In the step (3), using combined stress with calculating the worst error of stress as error amount.
In the step (3), by the comparative analysis of Finite element analysis results and rapid evaluation result, rapid evaluation is obtained
The error amount of method, then to big part carry out static strength rapid evaluation when, error amount is taken into account.
The components of stress include 6 altogether.
Compared with prior art, beneficial effects of the present invention are：
1) the methods of present invention is by combining finite element analysis and linear interpolation, forms suitable static strength rapid evaluation side
Method, this method can solve the problem that the problem of big part static strength calculating speed of Wind turbines is slower, by this method to Wind turbines
Big part static strength carries out rapid evaluation, the quick response of wind power plant Unit Selection and microcosmic structure is realized, so as to quick response
Market bid works, and improves whole efficiency；
2) quickly realized by this method and analyzed by seat in the plane, quickly realize unit differentiation, optimized design, compensate for existing
There is the slow deficiency of conventional method of analysis；
3) procedure of big part Static Strength Analysis process, digitization, systematization are realized, and with sustainability optimization
May, the competitiveness that enhancing wind power plant prior art is supported；
4) the big part static strength fast evaluation method of Wind turbines established of the present invention can quickly obtain big part and specify
The stress situation of node, realize " the becoming more meticulous " of intensive analysis.
5) the big part static strength fast evaluation method of Wind turbines that the present invention establishes introduces the control condition of error, increases
The strong trustworthiness of this method.
Brief description of the drawings
The Figure of description for forming the part of the present invention is used for providing a further understanding of the present invention, and of the invention shows
Meaning property embodiment and its illustrate be used for explain the present invention, do not form inappropriate limitation of the present invention.
Fig. 1 is the schematic diagram of the big part static strength fast evaluation method of Wind turbines of the present invention；
Fig. 2 is the schematic diagram of dynamic hubload coordinates computed system used in Wind turbines Static Strength Analysis of the present invention；
Embodiment：
The invention will be further described with embodiment below in conjunction with the accompanying drawings.
It is noted that described further below is all exemplary, it is intended to provides further instruction to the present invention.It is unless another
Indicate, all technologies used herein and scientific terminology are with usual with general technical staff of the technical field of the invention
The identical meanings of understanding.
It should be noted that term used herein above is merely to describe embodiment, and be not intended to restricted root
According to the illustrative embodiments of the present invention.As used herein, unless the context clearly indicates otherwise, otherwise singulative
It is also intended to include plural form, additionally, it should be understood that, when in this manual using term "comprising" and/or " bag
Include " when, it indicates existing characteristics, step, operation, device, component and/or combinations thereof.
As background technology is introduced, the work that the big part of Wind turbines carries out Static Strength Analysis in the prior art be present
Amount is very huge, if being taken a significant amount of time every time to the big part progress static strength check needs of Wind turbines of a unknown wind field
Deficiency, in order to solve technical problem as above, the present invention proposes a kind of big part static strength rapid evaluation side of Wind turbines
Method, on the basis of big part static strength results accuracy is ensured, it is possible to prevente effectively from replicate analysis work, greatly shorten wind
The time of the big part Static Strength Analysis of group of motors
The present invention relies on the Finite element analysis results of a large amount of big parts of Wind turbines, and combines finite element analysis and linearly insert
Value method, form suitable static strength fast evaluation method.
Big part static strength fast evaluation method is described by taking main shaft as an example, according to the limit work of unit design load
Working condition loading table (as shown in table 1), sets the minimum value and maximum of 6 sharing parts of the load, and minimum value is needed the limit with maximum
Including value envelope in loadmeter, Mxmin, Mxmax, Mymin are designated as respectively ....
The hub centre rotating coordinate system ultimate load of table 1
Loading condition table is set, as shown in table 2, the extreme values such as Mxmin, Mxmax, Mymin ... is divided into 8 steps and added successively
Carry, 1 to operating mode 8 load is respectively Mxmin, Mxmin*7/8 ... Mxmin*1/8, and 9 to operating mode 16 load is respectively
Mxmax*1/8, Mxmax*2/8 ... Mxmax, until operating mode 96.
The loading condition table of table 2
| Operating mode | 1 | 2 | 3 | 4 | 5 | 6 | 7 | 8 |
| Load | Mxmin | Mxmin*7/8 | Mxmin*6/8 | Mxmin*5/8 | Mxmin*4/8 | Mxmin*3/8 | Mxmin*2/8 | Mxmin*1/8 |
| Operating mode | 9 | 10 | 11 | 12 | 13 | 14 | 15 | 16 |
| Load | Mxmax*1/8 | Mxmax*2/8 | Mxmax*3/8 | Mxmax*4/8 | Mxmax*5/8 | Mxmax*6/8 | Mxmax*7/8 | Mxmax |
| Operating mode | 17 | 18 | 19 | 20 | 21 | 22 | 23 | 24 |
| Load | Mymin | Mymin*7/8 | Mymin*6/8 | Mymin*5/8 | Mymin*4/8 | Mymin*3/8 | Mymin*2/8 | Mymin*1/8 |
| Operating mode | 25 | 26 | 27 | 28 | 29 | 30 | 31 | 32 |
| Load | Mymax*1/8 | Mymax*2/8 | Mymax*3/8 | Mymax*4/8 | Mymax*5/8 | Mymax*6/8 | Mymax*7/8 | Mymax |
| Operating mode | 33 | 34 | 35 | 36 | 37 | 38 | 39 | 40 |
| Load | Mzmin | Mzmin*7/8 | Mzmin*6/8 | Mzmin*5/8 | Mzmin*4/8 | Mzmin*3/8 | Mzmin*2/8 | Mzmin*1/8 |
| Operating mode | 41 | 42 | 43 | 44 | 45 | 46 | 47 | 48 |
| Load | Mzmax*1/8 | Mzmax*2/8 | Mzmax*3/8 | Mzmax*4/8 | Mzmax*5/8 | Mzmax*6/8 | Mzmax*7/8 | Mzmax |
| Operating mode | 49 | 50 | 51 | 52 | 53 | 54 | 55 | 56 |
| Load | Fxmin | Fxmin*7/8 | Fxmin*6/8 | Fxmin*5/8 | Fxmin*4/8 | Fxmin*3/8 | Fxmin*2/8 | Fxmin*1/8 |
| Operating mode | 57 | 58 | 59 | 60 | 61 | 62 | 63 | 64 |
| Load | Fxmax*1/8 | Fxmax*2/8 | Fxmax*3/8 | Fxmax*4/8 | Fxmax*5/8 | Fxmax*6/8 | Fxmax*7/8 | Fxmax |
| Operating mode | 65 | 66 | 67 | 68 | 69 | 70 | 71 | 72 |
| Load | Fymin | Fymin*7/8 | Fymin*6/8 | Fymin*5/8 | Fymin*4/8 | Fymin*3/8 | Fymin*2/8 | Fymin*1/8 |
| Operating mode | 73 | 74 | 75 | 76 | 77 | 78 | 79 | 80 |
| Load | Fymax*1/8 | Fymax*2/8 | Fymax*3/8 | Fymax*4/8 | Fymax*5/8 | Fymax*6/8 | Fymax*7/8 | Fymax |
| Operating mode | 81 | 82 | 83 | 84 | 85 | 86 | 87 | 88 |
| Load | Fzmin | Fzmin*7/8 | Fzmin*6/8 | Fzmin*5/8 | Fzmin*4/8 | Fzmin*3/8 | Fzmin*2/8 | Fzmin*1/8 |
| Operating mode | 89 | 90 | 91 | 92 | 93 | 94 | 95 | 96 |
| Load | Fzmax*1/8 | Fzmax*2/8 | Fzmax*3/8 | Fzmax*4/8 | Fzmax*5/8 | Fzmax*6/8 | Fzmax*7/8 | Fzmax |
According to the static strength result of finite element under ultimate load, destination node is chosen, node is uniformly distributed in main shaft
Surface stress value large area.
Using same FEM model, 96 operating modes in computational chart 2.
Six components of stress Sx, Sy, Sz, Sxy, Syz, Sxz of destination node under 96 loading conditions are extracted, obtain 6
Corresponding relation between node stress component and each sharing part of the load, form intensive analysis database.As shown in Table 3 and Table 4, wherein
" Mx ", " My " are the title of the sharing part of the load, and " 1 " is the sequence number in destination node, and " 331072 " are node number, the 3rd in secondary series
Row and the following load value for corresponding to.
36 components of stress of table and Mx corresponding form (unit kNm, Mpa)
| Mx | 1 | ||||||
| 331072 | Sx | Sy | Sz | Sxy | Syz | Sxz | |
| -2200 | -0.262 | -0.107 | -0.14 | 0.098 | 4.822 | -101.749 | |
| -1925 | -0.201 | -0.082 | -0.107 | 0.075 | 4.22 | -89.03 | |
| -1650 | -0.147 | -0.06 | -0.079 | 0.055 | 3.617 | -76.312 | |
| -1375 | -0.102 | -0.042 | -0.055 | 0.038 | 3.014 | -63.593 | |
| -1100 | -0.066 | -0.027 | -0.035 | 0.024 | 2.411 | -50.874 | |
| -825 | -0.037 | -0.015 | -0.02 | 0.014 | 1.808 | -38.156 | |
| -550 | -0.016 | -0.007 | -0.009 | 0.006 | 1.206 | -25.437 | |
| -275 | -0.004 | -0.002 | -0.002 | 0.002 | 0.603 | -12.719 | |
| 400 | -0.009 | -0.004 | -0.005 | 0.003 | -0.877 | 18.5 | |
| 800 | -0.035 | -0.014 | -0.018 | 0.013 | -1.754 | 37 | |
| 1200 | -0.078 | -0.032 | -0.042 | 0.029 | -2.63 | 55.499 | |
| 1600 | -0.139 | -0.057 | -0.074 | 0.052 | -3.507 | 73.999 | |
| 2000 | -0.217 | -0.089 | -0.115 | 0.081 | -4.384 | 92.499 | |
| 2400 | -0.312 | -0.128 | -0.166 | 0.116 | -5.261 | 110.999 | |
| 2800 | -0.424 | -0.174 | -0.226 | 0.158 | -6.138 | 129.498 | |
| 3200 | -0.554 | -0.227 | -0.295 | 0.206 | -7.015 | 147.998 |
46 components of stress of table and My corresponding form (unit kNm, Mpa)
For 6 load Mx, My, Mz, Fx, Fy, Fz of some limiting condition, according to intensive analysis database, pass through line
Property interpolation obtain in operating mode certain destination node components of stress Sx corresponding to Mx-Mx、Sy-Mx、Sz-Mx、Sxy-Mx、Syz-Mx、Sxz-Mx, together
Reason obtains the destination node components of stress corresponding to other 5 load, and addition obtains the destination node components of stress in the operating mode and closed
Power, i.e.,：
Sx=Sx-Mx +Sx-My +Sx-Mz +Sx-Fx +Sx-Fx +Sx-Fx
Sy=Sy-Mx +Sy-My +Sy-Mz +Sy-Fx +Sy-Fx +Sy-Fx
Sz=Sz-Mx +Sz-My +Sz-Mz +Sz-Fx +Sz-Fx +Sz-Fx
Sxy=Sxy-Mx +Sxy-My +Sxy-Mz +Sxy-Fx +Sxy-Fx +Sxy-Fx
Syz=Syz-Mx +Syz-My +Syz-Mz +Syz-Fx +Syz-Fx +Syz-Fx
Sxz=Sxz-Mx +Sxz-My +Sxz-Mz +Sxz-Fx +Sxz-Fx +Sxz-Fx
Synthesize to obtain the equivalent stress of the destination node by Von mises stress formulas again.
Table 5 contrasts form for the combined stress of main shaft with calculating stress, only have chosen 8 destination nodes, four limit carry
The result of lotus operating mode is analyzed, wherein, combined stress refers to the equivalent stress obtained by big part fast evaluation method.
As seen from the table, the maximum stress point of 4 operating modes occurs at No. 2 destination nodes of Mymin ultimate load operating modes, combined stress
Worst error with calculating stress is 0.343%.Can be larger compared with dot, error for stress, worst error reaches
11.666%.But during due to whether meeting to require in the static strength for judging big part, use maximum stress value to be judged,
The small point of stress can be ignored, therefore the combined stress of main shaft should be taken as 0.343% with calculating the error of stress, error amount
Very little.
The main shaft combined stress of table 5 and finite element result contrast form (unit of stress MPa)
Static strength rapid evaluation is carried out to mainframe, bearing block with identical method, obtains the synthesis of mainframe, bearing block
Stress and finite element result contrast form.
Table 6 is that mainframe combined stress and finite element result contrast form, only have chosen 8 to No. 17 destination nodes, four
The result of ultimate load operating mode is analyzed.As seen from the table, the maximum stress point of 4 operating modes, occur in the Mzmax limit
At No. 15 destination nodes of load working condition, combined stress is -0.87% with the worst error for calculating stress.In addition, stress is smaller
The error of point is then bigger.
The mainframe combined stress of table 6 and finite element result contrast form (unit of stress MPa)
Table 7 contrasts form for combined stress and the finite element result of bearing block, only have chosen 1 to No. 7 destination node, four
The result of ultimate load operating mode is analyzed.As seen from the table, the maximum stress point of 4 operating modes, occur in the Mymin limit
At No. 5 destination nodes of load working condition, combined stress is 5.61% with the worst error for calculating stress.In addition, stress is compared with dot
Application condition it is big.
The bearing block combined stress of table 7 and finite element result contrast form (unit of stress MPa)
To sum up, in the examples described above, table 3, table 4 illustrate pair of the components of stress and the sharing part of the load in intensive analysis database
It should be related to, table 5, table 6, table 7 illustrate the error amount and reliability of this fast evaluation method.Obviously, the result of above-mentioned example
Successfully illustrate that method therefor of the embodiment of the present invention is reliable, precision is higher, and the big part of Wind turbines established with this is quiet strong
Spend the rapid evaluation that fast evaluation method then can be used for Wind turbines wind field adaptability.
The static strength fast evaluation method that the present invention establishes has advantages below：
1. quick response, big part static strength rapid evaluation (i.e. " input-output " pattern) is realized by this method, so as to
Fast responding market Public Bidding Work, improve whole efficiency；
Analyzed 2. quickly being realized by this method by seat in the plane, quickly realize unit differentiation, optimized design, compensate for existing
There is the slow deficiency of conventional method of analysis；
3. the procedure of big part Static Strength Analysis process, digitization, systematization are realized, and with sustainability optimization
May, the competitiveness that enhancing wind power plant prior art is supported.
The preferred embodiments of the present invention are the foregoing is only, are not intended to limit the invention, for the skill of this area
For art personnel, the present invention can have various modifications and variations.Within the spirit and principles of the invention, that is made any repaiies
Change, equivalent substitution, improvement etc., should be included in the scope of the protection.
Although above-mentioned the embodiment of the present invention is described with reference to accompanying drawing, model not is protected to the present invention
The limitation enclosed, one of ordinary skill in the art should be understood that on the basis of technical scheme those skilled in the art are not
Need to pay various modifications or deformation that creative work can make still within protection scope of the present invention.
Claims (9)
1. a kind of big part static strength fast evaluation method of Wind turbines, it is characterized in that：Following steps：
(1) the intensive analysis data of the corresponding relation of each components of stress and the sharing part of the load comprising big part key node are established
Storehouse；
(2) intensive analysis database is based on, it is quiet strong that the method synthesized using components of stress interpolation and equivalent stress carries out big part
Spend rapid evaluation；
(3) by being contrasted to the result of fast evaluation method and FInite Element, the error amount of assessment result is calculated, incites somebody to action
Components of stress difference and equivalent stress synthesis, are modified to error amount, obtain static strength appraisal procedure.
2. a kind of big part static strength fast evaluation method of Wind turbines as claimed in claim 1, it is characterized in that：The step
(1) in, typical wind turbine model is chosen, obtains the limiting condition loadmeter of the load of Wind turbines design.
3. a kind of big part static strength fast evaluation method of Wind turbines as claimed in claim 1, it is characterized in that：The step
(1) in, the minimum value and maximum of 6 sharing parts of the load are set according to limiting condition loadmeter, minimum value and maximum need by
Including value envelope in ultimate load table, loading condition table is built, load is divided into multiple grades and loaded successively.
4. a kind of big part static strength fast evaluation method of Wind turbines as claimed in claim 1, it is characterized in that：The step
(1) in, according to the static strength result of finite element under ultimate load, destination node is chosen, node is uniformly distributed in main spindle table
Face stress value is more than in the region of setting value.
5. a kind of big part static strength fast evaluation method of Wind turbines as claimed in claim 1, it is characterized in that：The step
(1) in, six components of stress of destination node under each loading condition is calculated using the static strength FEM model of structure, are obtained
Corresponding relation between 6 node stress components and each sharing part of the load, form intensive analysis database.
6. a kind of big part static strength fast evaluation method of Wind turbines as claimed in claim 1, it is characterized in that：The step
(2) in, according to intensive analysis database, obtaining corresponding to certain destination node corresponding to the sharing part of the load in operating mode by linear interpolation should
Force component, addition obtain the destination node components of stress in the operating mode and made a concerted effort, synthesize to obtain the mesh using Von mises stress formulas
Mark the equivalent stress of node.
7. a kind of big part static strength fast evaluation method of Wind turbines as claimed in claim 1, it is characterized in that：The step
(3) in, using combined stress with calculating the worst error of stress as error amount.
8. a kind of big part static strength fast evaluation method of Wind turbines as claimed in claim 1, it is characterized in that：The step
(3) by the comparative analysis of Finite element analysis results and rapid evaluation result in, the error amount of fast evaluation method is obtained, then it is right
When big part carries out static strength rapid evaluation, error amount is taken into account.
9. a kind of big part static strength fast evaluation method of Wind turbines as claimed in claim 1, it is characterized in that：The components of stress
Include 6 altogether.
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| 何玉林，杨豆思，金鑫，彭小云: "大型直驱型风力发电机组轮毂强度分析", 《机械科学与技术》 * |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN111985084A (en) * | 2020-07-24 | 2020-11-24 | 华设设计集团股份有限公司 | Bridge mechanics real-time analysis method based on finite variables |
| CN111985084B (en) * | 2020-07-24 | 2023-10-27 | 华设设计集团股份有限公司 | Bridge mechanics real-time analysis method based on finite variable |
| CN112182939A (en) * | 2020-10-16 | 2021-01-05 | 中国航发四川燃气涡轮研究院 | Dynamic strength evaluation method for engine bearing frame |
| CN112182939B (en) * | 2020-10-16 | 2022-11-18 | 中国航发四川燃气涡轮研究院 | Dynamic strength evaluation method for engine bearing frame |
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