CN103575535B - Wind-powered electricity generation double-fed generator rolling bearing fault method of discrimination and device - Google Patents

Wind-powered electricity generation double-fed generator rolling bearing fault method of discrimination and device Download PDF

Info

Publication number
CN103575535B
CN103575535B CN201310603092.8A CN201310603092A CN103575535B CN 103575535 B CN103575535 B CN 103575535B CN 201310603092 A CN201310603092 A CN 201310603092A CN 103575535 B CN103575535 B CN 103575535B
Authority
CN
China
Prior art keywords
drive end
double
rolling bearing
fed generator
represent
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.)
Expired - Fee Related
Application number
CN201310603092.8A
Other languages
Chinese (zh)
Other versions
CN103575535A (en
Inventor
唐建平
曹国荣
宋建秀
王宝归
陈世超
袁莹
赵燕峰
王莹
唐益文
袁乐
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
CRRC Zhuzhou Institute Co Ltd
Original Assignee
CSR Zhuzou Institute Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by CSR Zhuzou Institute Co Ltd filed Critical CSR Zhuzou Institute Co Ltd
Priority to CN201310603092.8A priority Critical patent/CN103575535B/en
Publication of CN103575535A publication Critical patent/CN103575535A/en
Application granted granted Critical
Publication of CN103575535B publication Critical patent/CN103575535B/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Landscapes

  • Wind Motors (AREA)

Abstract

The invention discloses a kind of wind-powered electricity generation double-fed generator rolling bearing fault method of discrimination and device, method implementation step is: the acceleration signal detecting double-fed generator drive end, anti-drive end respectively; Extract the time series that acceleration extreme point signal obtains acceleration extreme point respectively; Calculating elastic anchorage force obtains the time series of elastic anchorage force respectively; Carry out DFFT conversion respectively, obtain bearing fault characteristics frequency signal, according to bearing fault characteristics frequency signal carry out respectively double-fed generator drive end, anti-drive end breakdown judge and judged result is exported; Device comprises first, second acceleration transducer, acceleration extreme point signal extraction module, elastic anchorage force computing module, fault characteristic frequency computing module and breakdown judge module.The present invention has that fault detect is accurate, accuracy is high, quick, easy to use, advantage that bearing management maintenance cost is low easy to detect.

Description

Wind-powered electricity generation double-fed generator rolling bearing fault method of discrimination and device
Technical field
The present invention relates to technical field of wind power generation, be specifically related to a kind of wind-powered electricity generation double-fed generator rolling bearing fault method of discrimination and device.
Background technology
Because dual feed wind generator group is in complicated operating condition usually, and be unfavorable for regular maintenance, cause the unit failure failure conditions such as such as doubly-fed generation machine bearing to occur.Install for the situation of same model rolling bearing for dual feed wind generator group rear and front end, because the fault characteristic frequency of its outer ring, inner ring, rolling body, retainer is consistent, the fault characteristic frequency that the rolling bearing of same model is installed in wind-powered electricity generation double-fed generator rear and front end is the same, when causing collector to collect bearing fault characteristics signal, thus cause determining which bearing is the bearing fault information that sensor records come from, and also cannot differentiate the fault degree of each bearing.Therefore, in order to faulty bearings can be changed when bearing failure in time, ensures that Wind turbines normal reliable is run, extend the serviceable life of Wind turbines and parts thereof, erroneous judgement can not be produced to the bearing of non-fault (or fault is slight) again simultaneously, the new bearing replacing that can normally run gets off, cause meaningless economic loss, prevent from causing the reliability of blower fan reduce or produce unnecessary renewal cost owing to crossing diagnosis or owing diagnosis, become a key technical problem urgently to be resolved hurrily.
Summary of the invention
The technical problem to be solved in the present invention is to provide that a kind of fault detect is accurate, accuracy is high, quick, easy to use, wind-powered electricity generation double-fed generator rolling bearing fault method of discrimination that bearing management maintenance cost is low easy to detect and device.
In order to solve the problems of the technologies described above, the technical solution used in the present invention is:
A kind of wind-powered electricity generation double-fed generator rolling bearing fault method of discrimination, implementation step is as follows:
1) acceleration signal of double-fed generator drive end, the acceleration signal of anti-drive end is detected when double-fed generator runs;
2) extract the acceleration extreme point signal of described acceleration signal respectively, obtain the time series of double-fed generator drive end, anti-drive end acceleration extreme point;
3) respectively according to the time series of described acceleration extreme point calculate double-fed generator drive end, anti-drive end base angle resiliency supported elastic anchorage force, obtain the elastic anchorage force time series of base angle resiliency supported of double-fed generator drive end, anti-drive end;
4) respectively the time series of described elastic anchorage force is carried out DFFT conversion, obtain the bearing fault characteristics frequency signal of double-fed generator drive end, anti-drive end rolling bearing, the bearing fault characteristics frequency signal according to double-fed generator drive end, anti-drive end carries out breakdown judge respectively and judged result is exported.
Further, the elastic anchorage force calculating base angle resiliency supported respectively according to the time series of described acceleration extreme point respectively in described step 3) specifically refers to and calculates the elastic anchorage force of the base angle resiliency supported of double-fed generator drive end according to formula (1), calculate the elastic anchorage force of the base angle resiliency supported of double-fed generator anti-drive end according to formula (2);
F 1N=（a 1 2·（L+ L 2）·а 1N/ b 1+ a 2 2·L 2·а 2N/ b 2）/(L 2+ L·L 1+ L·L 2) （1）
F 2N=-（a 1 2·L 1·а 1N/ b 1+ a 2 2·（L+ L 1）·а 2N/ b 2）/(L 2+ L·L 1+ L·L 2) （2）
In formula (1) and formula (2), F 1Nrepresent the elastic anchorage force of the base angle resiliency supported of double-fed generator drive end, F 2Nrepresent the elastic anchorage force of the base angle resiliency supported of double-fed generator anti-drive end, N is time series; a 1calculation expression be a 1=J 2/ L(1+(k 1j 1)/(k 2j 2)), a 2calculation expression be a 2=J 1/ L(1+(k 2j 2)/(k 1j 1)), b 1and k 1all represent the rigidity of the base angle resiliency supported of double-fed generator drive end, b 2and k 2all represent the rigidity of the base angle resiliency supported of double-fed generator anti-drive end, а 1Nrepresent the time series of double-fed generator drive end acceleration extreme point, а 2Nrepresent the time series of double-fed generator anti-drive end acceleration extreme point, J 1represent the moment of inertia of the base angle resiliency supported of double-fed generator drive end, J 2represent the moment of inertia of the base angle resiliency supported of double-fed generator anti-drive end, L represents the centre distance between the base angle resiliency supported of generator drive end and the base angle resiliency supported of anti-drive end, L 1represent the distance between the center line of the base angle resiliency supported of generator drive end and generator drive end end cap outermost end, L 2represent the distance between the center line of the base angle resiliency supported of generator anti-drive end and generator non-drive end shield outermost end.
Further, the detailed step of breakdown judge is carried out respectively according to the bearing fault characteristics frequency signal of double-fed generator drive end, anti-drive end rolling bearing in described step 4) as follows:
4.1) the outer ring fault characteristic frequency of double-fed generator drive end, anti-drive end rolling bearing is calculated according to formula (3);
f 0=Z/2·(1-d/D·cosа)·f （3）
In formula (3), f 0represent the outer ring fault characteristic frequency of rolling bearing, Z represents the rolling body quantity of rolling bearing, and d represents the rolling body diameter of rolling bearing, and D represents the rolling body pitch diameter of rolling bearing, and а represents the contact angle of rolling bearing, and f represents turn frequency of double-fed generator;
4.2) the inner ring fault characteristic frequency of double-fed generator drive end, anti-drive end rolling bearing is calculated according to formula (4);
f i=Z/2·(1+d/D·cosа)·f （4）
In formula (4), f irepresent the inner ring fault characteristic frequency of rolling bearing, Z represents the rolling body quantity of rolling bearing, and d represents the rolling body diameter of rolling bearing, and D represents the rolling body pitch diameter of rolling bearing, and а represents the contact angle of rolling bearing, and f represents turn frequency of double-fed generator;
4.3) the rolling body fault characteristic frequency of double-fed generator drive end, anti-drive end rolling bearing is calculated according to formula (5);
f b=1/2·R pmi/60·D/d·(1-(d/D·cosа) 2) （5）
In formula (5), f brepresent the rolling body fault characteristic frequency of rolling bearing, R pmirepresent the inner ring frequency of rolling bearing, d represents the rolling body diameter of rolling bearing, and D represents the rolling body pitch diameter of rolling bearing, and а represents the contact angle of rolling bearing;
4.4) the retainer fault characteristic frequency of double-fed generator drive end, anti-drive end rolling bearing is calculated according to formula (6);
f c=1/2·R pmi/60·(1-d/D·cosа)±R pm0/60·(1+d/D·cosа) （6）
In formula (6), f crepresent the retainer fault characteristic frequency of rolling bearing, R pmirepresent the inner ring frequency of rolling bearing, R pm0represent the outer ring frequency of rolling bearing, d represents the rolling body diameter of rolling bearing, and D represents the rolling body pitch diameter of rolling bearing, and а represents the contact angle of rolling bearing;
4.5) the bearing fault characteristics frequency signal of described double-fed generator drive end, anti-drive end rolling bearing is compared with the outer ring fault characteristic frequency of described rolling bearing, inner ring fault characteristic frequency, rolling body fault characteristic frequency, retainer fault characteristic frequency respectively, thus judge the fault type of the rolling bearing of double-fed generator drive end, anti-drive end and fault degree according to the matching degree between two frequencies compared and export judged result.
The present invention also provides a kind of wind-powered electricity generation double-fed generator rolling bearing fault discriminating gear, comprising:
First acceleration transducer, for detecting the acceleration signal of double-fed generator drive end when double-fed generator runs;
Second acceleration transducer, for detecting the acceleration signal of double-fed generator anti-drive end when double-fed generator runs;
Acceleration extreme point signal extraction module, for extracting the acceleration extreme point signal of described acceleration signal respectively, obtains the time series of double-fed generator drive end, anti-drive end acceleration extreme point;
Elastic anchorage force computing module, for calculating the elastic anchorage force of base angle resiliency supported of double-fed generator drive end, anti-drive end respectively respectively according to the time series of described acceleration extreme point, obtain the elastic anchorage force time series of base angle resiliency supported of double-fed generator drive end, anti-drive end;
Fault characteristic frequency computing module, for respectively the time series of described elastic anchorage force being carried out DFFT conversion, obtains the bearing fault characteristics frequency signal of double-fed generator drive end, anti-drive end;
Breakdown judge module, for carry out respectively according to the bearing fault characteristics frequency signal of double-fed generator drive end, anti-drive end double-fed generator drive end, anti-drive end breakdown judge and judged result is exported.
Further, described elastic anchorage force computing module comprises:
Drive end elastic anchorage force computing module, for calculating the elastic anchorage force of the base angle resiliency supported of double-fed generator drive end according to formula (1);
Anti-drive end elastic anchorage force computing module, for calculating the elastic anchorage force of the base angle resiliency supported of double-fed generator anti-drive end according to formula (2);
F 1N=（a 1 2·（L+ L 2）·а 1N/ b 1+ a 2 2·L 2·а 2N/ b 2）/(L 2+ L·L 1+ L·L 2) （1）
F 2N=-（a 1 2·L 1·а 1N/ b 1+ a 2 2·（L+ L 1）·а 2N/ b 2）/(L 2+ L·L 1+ L·L 2) （2）
In formula (1) and formula (2), F 1Nrepresent the elastic anchorage force of the base angle resiliency supported of double-fed generator drive end, F 2Nrepresent the elastic anchorage force of the base angle resiliency supported of double-fed generator anti-drive end, N is time series; a 1calculation expression be a 1=J 2/ L(1+(k 1j 1)/(k 2j 2)), a 2calculation expression be a 2=J 1/ L(1+(k 2j 2)/(k 1j 1)), b 1and k 1all represent the rigidity of the base angle resiliency supported of double-fed generator drive end, b 2and k 2all represent the rigidity of the base angle resiliency supported of double-fed generator anti-drive end, а 1Nrepresent the time series of double-fed generator drive end acceleration extreme point, а 2Nrepresent the time series of double-fed generator anti-drive end acceleration extreme point, J 1represent the moment of inertia of the base angle resiliency supported of double-fed generator drive end, J 2represent the moment of inertia of the base angle resiliency supported of double-fed generator anti-drive end, L represents the centre distance between the base angle resiliency supported of generator drive end and the base angle resiliency supported of anti-drive end, L 1represent the distance between the center line of the base angle resiliency supported of generator drive end and generator drive end end cap outermost end, L 2represent the distance between the center line of the base angle resiliency supported of generator anti-drive end and generator non-drive end shield outermost end.
Further, described breakdown judge module comprises:
Outer ring fault characteristic frequency computing module, for calculating the outer ring fault characteristic frequency of double-fed generator drive end, anti-drive end rolling bearing according to formula (3);
f 0=Z/2·(1-d/D·cosа)·f （3）
In formula (3), f 0represent the outer ring fault characteristic frequency of rolling bearing, Z represents the rolling body quantity of rolling bearing, and d represents the rolling body diameter of rolling bearing, and D represents the rolling body pitch diameter of rolling bearing, and а represents the contact angle of rolling bearing, and f represents turn frequency of double-fed generator;
Inner ring fault characteristic frequency computing module, for calculating the inner ring fault characteristic frequency of double-fed generator drive end, anti-drive end rolling bearing according to formula (4);
f i=Z/2·(1+d/D·cosа)·f （4）
In formula (4), f irepresent the inner ring fault characteristic frequency of rolling bearing, Z represents the rolling body quantity of rolling bearing, and d represents the rolling body diameter of rolling bearing, and D represents the rolling body pitch diameter of rolling bearing, and а represents the contact angle of rolling bearing, and f represents turn frequency of double-fed generator;
Rolling body fault characteristic frequency computing module, for calculating the rolling body fault characteristic frequency of double-fed generator drive end, anti-drive end rolling bearing according to formula (5);
f b=1/2·R pmi/60·D/d·(1-(d/D·cosа) 2) （5）
In formula (5), f brepresent the rolling body fault characteristic frequency of rolling bearing, R pmirepresent the inner ring frequency of rolling bearing, d represents the rolling body diameter of rolling bearing, and D represents the rolling body pitch diameter of rolling bearing, and а represents the contact angle of rolling bearing;
Retainer fault characteristic frequency computing module, for calculating the retainer fault characteristic frequency of double-fed generator drive end, anti-drive end rolling bearing according to formula (6);
f c=1/2·R pmi/60·(1-d/D·cosа)±R pm0/60·(1+d/D·cosа) （6）
In formula (6), f crepresent rolling bearing retainer fault characteristic frequency, R pmirepresent the inner ring frequency of rolling bearing, R pm0represent the outer ring frequency of rolling bearing, d represents the rolling body diameter of rolling bearing, and D represents the rolling body pitch diameter of rolling bearing, and а represents the contact angle of rolling bearing;
Fault characteristic frequency compares to determine module, for respectively the bearing fault characteristics frequency signal of described double-fed generator drive end, anti-drive end rolling bearing being compared with the outer ring fault characteristic frequency of described rolling bearing, inner ring fault characteristic frequency, rolling body fault characteristic frequency, retainer fault characteristic frequency respectively, thus judge the fault type of rolling bearing and fault degree according to the matching degree between two frequencies compared and export judged result.
Wind-powered electricity generation double-fed generator rolling bearing fault method of discrimination of the present invention has following advantage: the present invention is directed to dual feed wind generator group and be usually in complicated operating condition, and be unfavorable for regular maintenance, cause the problem that the unit failure failure conditions such as such as doubly-fed generation machine bearing occur, the acceleration signal of the present invention by obtaining from double-fed generator drive end and anti-drive end vibration transducer, the accekeration of each extreme point is equivalent to the initial acceleration that double-fed generator two ends produce the high frequency square wave power of resiliency supported, corresponding double-fed generator two ends are obtained to the time series signal of resiliency supported acting force according to mechanical equation, according to mounting means and the corresponding equation of motion of blower fan double-fed generator, obtain the double-fed generator two ends of time series signal to the acting force of resiliency supported, converted by DFFT, extract the acting force under same model Rolling Bearing Fault Character frequency signal respectively, thus indirect discrimination double-fed generator bearing fault, can for the outer ring of the consistent drive end of the fault characteristic frequency of double-fed wind generator and anti-drive end rolling bearing, inner ring, rolling body, retainer carries out fault analysis and diagnosis, thus can determine which bearing is the bearing fault information that sensor records come from, also fault degree and the type of each bearing can be differentiated, can guarantee to change faulty bearings in time when bearing failure, ensure that Wind turbines normal reliable is run, extend the serviceable life of Wind turbines and parts thereof, erroneous judgement can not be produced to the bearing of non-fault (or fault is slight) again simultaneously, the reliability of blower fan will be caused to reduce or produce unnecessary renewal cost owing to crossing diagnosis or owing diagnosis, there is fault detect accurate, accuracy is high, fast easy to detect, easy to use, the advantage that bearing management maintenance cost is low.
Wind-powered electricity generation double-fed generator rolling bearing fault discriminating gear of the present invention is the corresponding device of wind-powered electricity generation double-fed generator rolling bearing fault method of discrimination of the present invention, therefore also there is the technique effect identical with wind-powered electricity generation double-fed generator rolling bearing fault method of discrimination of the present invention, do not repeat them here.
Accompanying drawing explanation
Fig. 1 is the schematic flow sheet of embodiment of the present invention method.
Fig. 2 is the sensor fixing structure schematic diagram in the embodiment of the present invention.
Fig. 3 is the force analysis schematic diagram of the embodiment of the present invention when bearing fault.
Fig. 4 is that in the embodiment of the present invention, double-fed generator bearing fault produces impulsive force schematic diagram.
Fig. 5 is the framed structure schematic diagram of embodiment of the present invention device.
Embodiment
As shown in Figure 1, the implementation step of the wind-powered electricity generation double-fed generator rolling bearing fault method of discrimination of the present embodiment is as follows:
1) acceleration signal of double-fed generator drive end, the acceleration signal of anti-drive end is detected when double-fed generator runs.
The present embodiment is particular by the acceleration signal being arranged on double-fed generator drive end respectively, the acceleration transducer of anti-drive end realizes not detecting at double-fed generator motion time double-fed generator drive end, anti-drive end.As shown in Figure 2, support 1 supporting and fixing of double-fed generator common is at present on base 7, rotating shaft 6 is inserted with in support 1, the left side (anti-drive end) of rotating shaft 6 and right side (drive end) to be connected with the end cap 4 of support 1 respectively by the bearing outer ring of a roller bearing 5 and to coordinate, rotating shaft 6 is provided with rotor core 3, be provided with stator core 2 in support 1, stator core 2 is set in the outside of rotor core 3.In the present embodiment, the first acceleration transducer 9 being used for the acceleration signal detecting double-fed generator drive end is arranged on the end cap 4 of double-fed generator drive end, the second acceleration transducer 10 being used for the acceleration signal detecting double-fed generator anti-drive end is arranged on the end cap 4 of double-fed generator anti-drive end, base 7 is equipped with base angle resiliency supported 8 in the bottom of double-fed generator drive end, anti-drive end.When installing acceleration transducer, first the paint on end cap 4 surface is needed to polish off, and the surface finish of end cap 4 is become plane, then at the surperficial coated with metal bonding agent of the first acceleration transducer 9, second acceleration transducer 10, then firmly the surface of the first acceleration transducer 9, second acceleration transducer 10 and end cap 4 are close together respectively.
See the force analysis to base angle resiliency supported 8 during double-fed generator bearing fault as shown in Figure 3, F 1for vibratory impulse power, F that the roller bearing 5 of double-fed generator drive end produces when fault 2for vibratory impulse power, F that the roller bearing 5 of double-fed generator anti-drive end produces when fault k1for resiliency supported acting force, the F of the base angle resiliency supported 8 of double-fed generator drive end k2for the resiliency supported acting force of the base angle resiliency supported 8 of double-fed generator anti-drive end, G are the gravity of double-fed generator, K 1for the base angle resiliency supported rigidity of the base angle resiliency supported 8 of double-fed generator drive end, K 2for the base angle resiliency supported rigidity of the base angle resiliency supported 8 of double-fed generator anti-drive end.Suppose in the dynamic process of doubly-fed generation machine vibration, the displacement of the base angle resiliency supported 8 of double-fed generator drive end is y 1, initial displacement amount is y 10, the displacement of the base angle resiliency supported 8 of double-fed generator anti-drive end is y 2, initial displacement amount is y 20(displacement all with direction upwards for positive displacement amount), double-fed generator with the base angle resiliency supported 8 of the drive end anglec of rotation that is initial point for θ 1, double-fed generator with the base angle resiliency supported 8 of the anti-drive end anglec of rotation that is initial point for θ 2(rotating just is all in a clockwise direction), the moment of inertia of the base angle resiliency supported 8 of double-fed generator drive end is J 1, the moment of inertia of the base angle resiliency supported 8 of double-fed generator anti-drive end is J 2; In addition, double-fed generator is when vibrating, and owing to there being the effect of base angle resiliency supported 8, its perpendicular displacement amount is not too large, and for this reason approximate have formula (1.1) and formula (1.2).
θ 1=（y 2-y 1）/L （1.1）
θ 2=（y 2-y 1）/L （1.2）
In formula (1.1) and formula (1.2), θ 1represent the anglec of rotation that double-fed generator is initial point with the base angle resiliency supported 8 of drive end, θ 2represent the anglec of rotation that double-fed generator is initial point with the base angle resiliency supported 8 of anti-drive end, y 1represent the displacement of the base angle resiliency supported 8 of double-fed generator drive end, y 2represent the displacement of the base angle resiliency supported 8 of double-fed generator anti-drive end, L represents the centre distance between the base angle resiliency supported 8 of generator drive end and the base angle resiliency supported 8 of anti-drive end.
Therefore the reacting force of double-fed generator resiliency supported is such as formula shown in (1.3) and formula (1.4).
F k1=-k 1(y 1+y 10) （1.3）
F k2=-k 2(y 2+y 20) （1.4）
In formula (1.3) and formula (1.4), K 1for the rigidity of the base angle resiliency supported 8 of double-fed generator drive end, K 2for the rigidity of the base angle resiliency supported 8 of double-fed generator anti-drive end, F k1for the resiliency supported acting force of the base angle resiliency supported 8 of double-fed generator drive end, F k2for the resiliency supported acting force of the base angle resiliency supported 8 of double-fed generator anti-drive end, y 1represent the displacement of the base angle resiliency supported 8 of double-fed generator drive end, y 2represent the displacement of the base angle resiliency supported 8 of double-fed generator anti-drive end, y 10represent the initial displacement amount of the base angle resiliency supported 8 of double-fed generator drive end, y 20represent the initial displacement amount of the base angle resiliency supported 8 of double-fed generator anti-drive end.
Formula (1.5) and formula (1.6) can be obtained according to the equation of motion.
J 1·dθ 1/dt=J 1/L·（dy 2/dt–dy 1/dt）=F k2·L+F 1·L 1-1/2·G·L-F 2·（L 2+L）（1.5）
J 2·dθ 2/dt=J 2/L·（dy 2/dt–dy 1/dt）=F 1·（L+L 1）+1/2·G·L-F k1·L-F 2·L 2 （1.6）
Formula (1.5) and formula (1.6) are subtracted each other, has formula (1.7).
-k 2(y 2+y 20)·L/ J 1+（L 1/ J 1-（L+L 1）/ J 2）F 1-（1/2·J 1+1/2·J 2）G·L- k 1(y 1+y 10)·L/ J 2+（L 2/ J 2-（L+L 2）/ J 1）F 2=0 （1.7）
In formula (1.5), formula (1.6) and formula (1.7), J 1represent the moment of inertia of the base angle resiliency supported 8 of double-fed generator drive end, J 2represent the moment of inertia of the base angle resiliency supported 8 of double-fed generator anti-drive end, θ 1represent the anglec of rotation that double-fed generator is initial point with the base angle resiliency supported 8 of drive end, θ 2represent the anglec of rotation that double-fed generator is initial point with the base angle resiliency supported 8 of anti-drive end, y 1represent the displacement of the base angle resiliency supported 8 of double-fed generator drive end, y 2represent the displacement of the base angle resiliency supported 8 of double-fed generator anti-drive end, K 1represent the rigidity of the base angle resiliency supported 8 of double-fed generator drive end, K 2represent the rigidity of the base angle resiliency supported 8 of double-fed generator anti-drive end, F k1represent the resiliency supported acting force of the base angle resiliency supported 8 of double-fed generator drive end, F k2represent the resiliency supported acting force of the base angle resiliency supported 8 of double-fed generator anti-drive end, L represents the centre distance between the base angle resiliency supported 8 of generator drive end and the base angle resiliency supported 8 of anti-drive end, L 1represent the distance between the center line of the base angle resiliency supported 8 of generator drive end and generator drive end end cap 4 outermost end, L 2represent the distance between the center line of the base angle resiliency supported 8 of generator anti-drive end and generator non-drive end shield 4 outermost end, G represents the gravity of double-fed generator, F 1represent vibratory impulse power, F that the roller bearing 5 of double-fed generator drive end produces when fault 2represent and the vibratory impulse power that the roller bearing 5 of double-fed generator anti-drive end produces when fault produce impulsive force schematic diagram see double-fed generator bearing fault as shown in Figure 4, in the present embodiment when rolling bearing 6 fault, vibratory impulse power F 1, F 2be high frequency square wave power.
Make in formula (1.7):
A=（L 1/ J 1-（L+L 1）/ J 2）,
B=（L 2/ J 2-（L+L 2）/ J 1）,
C=- k 2·y 20·L/ J 1- k 1·y 10·L/ J 2-（1/2·J 1+1/2·J 2）G·L。
Then formula (1.7) can be expressed as formula (1.8).
-k 2·y 2·L/ J 1- k 1·y 1·L/ J 2+A·F 1+B·F 2+C=0 （1.8）
Under normal circumstances, C=0, then formula (1.8) can be exchanged into formula (1.9) ~ formula (1.11).
-k 2·y 2·L/ J 1- k 1·y 1·L/ J 2+A·F 1+B·F 2=0 （1.9）
y 1=-（k 2·J 2）/（k 1·J 1）·y 2-（A·F 1+B·F 2）·J 2/ k 1·L （1.10）
y 2=-（k 1·J 1）/（k 2·J 2）·y 1-（A·F 1+B·F 2）·J 1/ k 2·L （1.11）
Formula (1.10) is substituted into formula (1.5) and then has formula (1.12).
J 1/L·（1+（k 2·J 2）/（k 1·J 1））·y 2 ′= -k 2(y 2+y 20) ·L+ F 1·L 1-1/2·G·L- F 2·（L 2+L）= k 2y 2+ F 1·L 1- F 2·（L 2+L） （1.12）
Formula (1.12) can be exchanged into formula (1.13).
J 1/L·（1+（k 2·J 2）/（k 1·J 1））·y 2 ′=- k 2y 2+ F 1·L 1- F 2·（L 2+L） （1.13）
In formula (1.12) and formula (1.13), y 2 'represent the speed of deformation amount of the base angle resiliency supported 8 of generator anti-drive end.
Make in formula (1.13):
a 2= J 1/L·（1+（k 2·J 2）/（k 1·J 1））
b 2= k 2
c 2= F 1·L 1- F 2·（L 2+L）。
Then formula (1.13) can be expressed as formula (1.14) and formula (1.15).
a 2y 2 ′+ b 2y 2= c 2（1.14）
y 2=( c 2/ b 2) ·e -(b2/a2)t+k 2（1.15）
Formula (1.11) is substituted into formula (1.6) and then can obtain formula (1.16).
-J 2/L·（1+（k 1·J 1）/（k 2·J 2））·y 1 ′=k 1(y 1+y 10)·L+ F 1·（L+L 1）+1/2·G·L - F 2·L 2= -k 1y 1+ F 1·（L+L 1）- F 2·L 2 （1.16）
Formula (1.16) can be exchanged into formula (1.17).
J 2/L·（1+（k 1·J 1）/（k 2·J 2））·y 1 ′=-k 1y 1-F 1·（L+L 1）+F 2·L 2 （1.17）
(1.16) and in formula (1.17), y 1 'represent the speed of deformation amount of the base angle resiliency supported 8 of generator drive end.
Make in formula (1.17):
a 1= J 2/L·（1+（k 1·J 1）/（k 2·J 2））
b 1= k 1
c 1= -F 1·（L+L 1）+F 2·L 2。
Then formula (1.17) can be expressed as formula (1.18) and formula (1.19).
a 1y 1 ′+ b 1y 1= c 1 （1.18）
y 1=( c 1/ b 1) ·e -(b1/a1)t+k 1 （1.19）
For this reason, double-fed generator drive end and anti-drive end vibration acceleration can be expressed as formula (1.20) and formula (1.21).
а 1= y 1 〞= b 1/ a 1 2·e -(b1/a1)t·c 1 （1.20）
а 2= y 2 〞= b 2/ a 2 2·e -(b2/a2)t·c 2 （1.21）
In formula (1.20) and formula (1.21), y 1 〞represent the deformation amount of acceleration of the base angle resiliency supported 8 of double-fed generator drive end, y 2 〞represent the deformation amount of acceleration of the base angle resiliency supported 8 of double-fed generator anti-drive end.
2) extract the acceleration extreme point signal of acceleration signal respectively, obtain the time series а of double-fed generator drive end, anti-drive end acceleration extreme point 1N, а 2N.
From the acceleration signal that double-fed generator drive end and anti-drive end vibration transducer are tested, extract each extreme point signal, make it be а 1N, а 2N(wherein N is time series), for the accekeration of each extreme point, can be similar to and think this moment high frequency square wave power F 1N, F 2Nproduce at initial time, then, shown in the time series formula (1.22) having an acceleration extreme point of double-fed generator drive end, the time series of double-fed generator anti-drive end acceleration extreme point is such as formula shown in (1.23).
а 1N= y 1N 〞= b 1/ a 1 2·e -(b1/a1)0·c 1= b 1/ a 1 2·（-F 1N·（L+L 1）+F 2N·L 2） （1.22）；
а 2N= y 2N 〞= b 2/ a 2 2·e -(b2/a2)0·c 2= b 2/ a 2 2·c 2= F 1N·L 1- F 2N·（L 2+L） （1.23）；
In formula (1.22) and formula (1.23), y 1N 〞represent the deformation acceleration time series of the base angle resiliency supported 8 of double-fed generator drive end, y 2N 〞represent the deformation acceleration time series of the base angle resiliency supported 8 of double-fed generator anti-drive end.
3) respectively according to the time series а of acceleration extreme point 1N, а 2Ncalculate the elastic anchorage force of base angle resiliency supported 8 of double-fed generator drive end, anti-drive end, obtain the elastic anchorage force time series F of base angle resiliency supported 8 of double-fed generator drive end, anti-drive end 1N, F 2N.
In the present embodiment, in step 3) respectively according to the time series of acceleration extreme point respectively calculating elastic anchorage force specifically refer to and calculate the elastic anchorage force of the base angle resiliency supported 8 of double-fed generator drive end according to formula (1), calculate the elastic anchorage force of the base angle resiliency supported 8 of double-fed generator anti-drive end according to formula (2);
F 1N=（a 1 2·（L+ L 2）·а 1N/ b 1+ a 2 2·L 2·а 2N/ b 2）/(L 2+ L·L 1+ L·L 2) （1）
F 2N=-（a 1 2·L 1·а 1N/ b 1+ a 2 2·（L+ L 1）·а 2N/ b 2）/(L 2+ L·L 1+ L·L 2) （2）
In formula (1) and formula (2), F 1Nrepresent the elastic anchorage force of the base angle resiliency supported 8 of double-fed generator drive end, F 2Nrepresent the elastic anchorage force of the base angle resiliency supported 8 of double-fed generator anti-drive end, N is time series; a 1calculation expression be a 1=J 2/ L(1+(k 1j 1)/(k 2j 2)), a 2calculation expression be a 2=J 1/ L(1+(k 2j 2)/(k 1j 1)), b 1and k 1all represent the rigidity of the base angle resiliency supported 8 of double-fed generator drive end, b 2and k 2all represent the rigidity of the base angle resiliency supported 8 of double-fed generator anti-drive end, а 1Nrepresent the time series of double-fed generator drive end acceleration extreme point, а 2Nrepresent the time series of double-fed generator anti-drive end acceleration extreme point, J 1represent the moment of inertia of the base angle resiliency supported 8 of double-fed generator drive end, J 2represent the moment of inertia of the base angle resiliency supported 8 of double-fed generator anti-drive end, L represents the base angle resiliency supported 8 of generator drive end and the distance of the base angle resiliency supported 8 of anti-drive end, L 1represent the distance between the base angle resiliency supported 8 of generator drive end and generator drive end end cap 4, L 2represent the distance between the base angle resiliency supported 8 of generator anti-drive end and generator non-drive end shield 4.F 1N, F 2Nthe time series а with double-fed generator drive end and anti-drive end acceleration extreme point 1N, а 2Nthe linear function of variable, therefore, once obtain а 1N, а 2Nvalue, can F be tried to achieve 1N, F 1Nvalue.
4) respectively by the time series F of elastic anchorage force 1N, F 2Ncarry out DFFT conversion (i.e. discrete fast fourier transform), obtain the bearing fault characteristics frequency signal F of roller bearing 5 of double-fed generator drive end, anti-drive end 1f, F 2f, according to the bearing fault characteristics frequency signal of the roller bearing 5 of double-fed generator drive end, anti-drive end carry out respectively double-fed generator drive end, anti-drive end breakdown judge and judged result is exported.
In the present embodiment, in step 4) according to the bearing fault characteristics frequency signal of double-fed generator drive end, anti-drive end carry out respectively double-fed generator drive end, anti-drive end the detailed step of breakdown judge as follows:
4.1) the housing washer fault characteristic frequency of double-fed generator roller bearing 5 is calculated according to formula (3);
f 0=Z/2·(1-d/D·cosа) ·f （3）
In formula (3), f 0represent housing washer fault characteristic frequency, Z represents the rolling body quantity of rolling bearing, and d represents the rolling body diameter of rolling bearing, and D represents the rolling body pitch diameter of rolling bearing, and а represents the contact angle of rolling bearing, and f represents turn frequency of double-fed generator;
4.2) the rolling bearing inner ring fault characteristic frequency of double-fed generator roller bearing 5 is calculated according to formula (4);
f i=Z/2·(1+d/D·cosа) ·f （4）
In formula (4), f irepresent rolling bearing inner ring fault characteristic frequency, Z represents the rolling body quantity of rolling bearing, and d represents the rolling body diameter of rolling bearing, and D represents the rolling body pitch diameter of rolling bearing, and а represents the contact angle of rolling bearing, and f represents turn frequency of double-fed generator;
4.3) the rolling bearing rolling body fault characteristic frequency of double-fed generator roller bearing 5 is calculated according to formula (5);
f b=1/2·R pmi/60·D/d·(1-( d/D·cosа) 2) （5）
In formula (5), f brepresent rolling bearing rolling body fault characteristic frequency, R pmirepresent the inner ring frequency of rolling bearing, d represents the rolling body diameter of rolling bearing, and D represents the rolling body pitch diameter of rolling bearing, and а represents the contact angle of rolling bearing;
4.4) the rolling bearing retainer fault characteristic frequency of double-fed generator roller bearing 5 is calculated according to formula (6);
f c=1/2·R pmi/60·(1-d/D·cosа)±R pm0/60·(1+d/D·cosа) （6）
In formula (6), f crepresent rolling bearing retainer fault characteristic frequency, R pmirepresent the inner ring frequency of rolling bearing, R pm0represent the outer ring frequency of rolling bearing, d represents the rolling body diameter of rolling bearing, and D represents the rolling body pitch diameter of rolling bearing, and а represents the contact angle of rolling bearing;
4.5) by the bearing fault characteristics frequency signal F of the roller bearing 5 of double-fed generator drive end, anti-drive end 1f, F 2fcompare with the housing washer fault characteristic frequency of double-fed generator roller bearing 5, rolling bearing inner ring fault characteristic frequency, rolling bearing rolling body fault characteristic frequency, rolling bearing retainer fault characteristic frequency respectively, thus judge the fault type of the rolling bearing of double-fed generator drive end, anti-drive end and fault degree according to the matching degree between two frequencies compared and export judged result.
In the present embodiment, if the bearing fault characteristics frequency signal (F of roller bearing 5 1f, F 2f) be less than appointment threshold value with the difference of another frequency (one of the housing washer fault characteristic frequency, rolling bearing inner ring fault characteristic frequency, rolling bearing rolling body fault characteristic frequency, rolling bearing retainer fault characteristic frequency of double-fed generator) compared, then be judged to be that the fault corresponding with another frequency compared occurs for the drive end that bearing fault characteristics frequency signal is corresponding or anti-drive end, and this difference is less, then the degree broken down is higher.For double-fed generator drive end, if the bearing fault characteristics frequency signal F of the roller bearing 5 of double-fed generator drive end 1fbe less than the threshold value of specifying with the difference of rolling bearing inner ring fault characteristic frequency, then judge F 1fcorresponding double-fed generator drive end generation rolling bearing inner ring fault, and this difference is less, then the degree that inner ring fault occurs is higher.It should be noted that, except above-mentioned employing difference with specify threshold value decision method except, the benchmark of other multiple judgement can also be adopted realize the matching degree between two frequencies comparing, such as ratio adopting difference between the ratio between two comparison others, two comparison others etc., it equally also can realize the fault type and the fault degree that judge the rolling bearing of double-fed generator drive end, anti-drive end according to the matching degree between two frequencies comparing, therefore does not repeat them here.
In sum, the present embodiment wind-powered electricity generation double-fed generator rolling bearing fault method of discrimination is in complicated operating condition for dual feed wind generator group usually, and be unfavorable for regular maintenance, cause the problem that the unit failure failure conditions such as such as doubly-fed generation machine bearing occur, the acceleration signal of the present invention by obtaining from double-fed generator drive end and anti-drive end vibration transducer, the accekeration of each extreme point is equivalent to the initial acceleration that double-fed generator two ends produce the high frequency square wave power of base angle resiliency supported 8, the time series signal of corresponding double-fed generator two ends to the resiliency supported acting force of base angle resiliency supported 8 is obtained according to mechanical equation, according to mounting means and the corresponding equation of motion of blower fan double-fed generator, obtain the double-fed generator two ends of time series signal to the elastic anchorage force of base angle resiliency supported 8, converted by DFFT, extract the acting force under same model Rolling Bearing Fault Character frequency signal respectively, thus indirect discrimination double-fed generator bearing fault, can for the outer ring of the consistent drive end of the fault characteristic frequency of double-fed wind generator and anti-drive end rolling bearing, inner ring, rolling body, retainer carries out fault analysis and diagnosis, thus can determine which bearing is the bearing fault information that sensor records come from, also fault degree and the type of each bearing can be differentiated, can guarantee to change faulty bearings in time when bearing failure, ensure that Wind turbines normal reliable is run, extend the serviceable life of Wind turbines and parts thereof, erroneous judgement can not be produced to the bearing of non-fault (or fault is slight) again simultaneously, the reliability of blower fan will be caused to reduce or produce unnecessary renewal cost owing to crossing diagnosis or owing diagnosis, there is fault detect accurate, accuracy is high, fast easy to detect, easy to use, the advantage that bearing management maintenance cost is low.
As shown in Figure 5, corresponding with the wind-powered electricity generation double-fed generator rolling bearing fault method of discrimination of the present embodiment, the present embodiment also provides a kind of wind-powered electricity generation double-fed generator rolling bearing fault discriminating gear, comprising:
First acceleration transducer, for detecting the acceleration signal of double-fed generator drive end when double-fed generator runs;
Second acceleration transducer, for detecting the acceleration signal of double-fed generator anti-drive end when double-fed generator runs;
Acceleration extreme point signal extraction module, for extracting the acceleration extreme point signal of acceleration signal respectively, obtains the time series of double-fed generator drive end, anti-drive end acceleration extreme point;
Elastic anchorage force computing module, for respectively according to the time series of acceleration extreme point calculating elastic anchorage force respectively, obtains the time series of base angle elastic anchorage force of double-fed generator drive end, anti-drive end;
Fault characteristic frequency computing module, for respectively the time series of elastic anchorage force being carried out DFFT conversion, obtains the bearing fault characteristics frequency signal of double-fed generator drive end, anti-drive end;
Breakdown judge module, for carry out respectively according to the bearing fault characteristics frequency signal of double-fed generator drive end, anti-drive end double-fed generator drive end, anti-drive end breakdown judge and judged result is exported.
In the present embodiment, elastic anchorage force computing module comprises:
Drive end elastic anchorage force computing module, for calculating the elastic anchorage force of the base angle resiliency supported 8 of double-fed generator drive end according to formula (1);
Anti-drive end elastic anchorage force computing module is used for the elastic anchorage force of the base angle resiliency supported 8 calculating double-fed generator anti-drive end according to formula (2);
F 1N=（a 1 2·（L+ L 2）·а 1N/ b 1+ a 2 2·L 2·а 2N/ b 2）/(L 2+ L·L 1+ L·L 2) （1）
F 2N=-（a 1 2·L 1·а 1N/ b 1+ a 2 2·（L+ L 1）·а 2N/ b 2）/(L 2+ L·L 1+ L·L 2) （2）
In formula (1) and formula (2), F 1Nrepresent the elastic anchorage force of the base angle resiliency supported 8 of double-fed generator drive end, F 2Nrepresent the elastic anchorage force of the base angle resiliency supported 8 of double-fed generator anti-drive end, N is time series; a 1calculation expression be a 1=J 2/ L(1+(k 1j 1)/(k 2j 2)), a 2calculation expression be a 2=J 1/ L(1+(k 2j 2)/(k 1j 1)), b 1and k 1all represent the rigidity of the base angle resiliency supported 8 of double-fed generator drive end, b 2and k 2all represent the rigidity of the base angle resiliency supported 8 of double-fed generator anti-drive end, а 1Nrepresent the time series of double-fed generator drive end acceleration extreme point, а 2Nrepresent the time series of double-fed generator anti-drive end acceleration extreme point, J 1represent the moment of inertia of the base angle resiliency supported 8 of double-fed generator drive end, J 2represent the moment of inertia of the base angle resiliency supported 8 of double-fed generator anti-drive end, L represents the base angle resiliency supported 8 of generator drive end and the distance of the base angle resiliency supported 8 of anti-drive end, L 1represent the distance between the base angle resiliency supported 8 of generator drive end and generator drive end end cap 4, L 2represent the distance between the base angle resiliency supported 8 of generator anti-drive end and generator non-drive end shield 4.
In the present embodiment, breakdown judge module comprises:
Outer ring fault characteristic frequency computing module, for calculating the outer ring fault characteristic frequency of the rolling bearing 5 of double-fed generator according to formula (3);
f 0=Z/2·(1-d/D·cosа) ·f （3）
In formula (3), f 0represent the outer ring fault characteristic frequency of rolling bearing 5, Z represents the rolling body quantity of rolling bearing 5, and d represents the rolling body diameter of rolling bearing 5, and D represents the rolling body pitch diameter of rolling bearing 5, а represents the contact angle of rolling bearing 5, and f represents turn frequency of double-fed generator;
Inner ring fault characteristic frequency computing module, for calculating the inner ring fault characteristic frequency of the rolling bearing 5 of double-fed generator according to formula (4);
f i=Z/2·(1+d/D·cosа) ·f （4）
In formula (4), f irepresent the inner ring fault characteristic frequency of rolling bearing 5, Z represents the rolling body quantity of rolling bearing 5, and d represents the rolling body diameter of rolling bearing 5, and D represents the rolling body pitch diameter of rolling bearing 5, а represents the contact angle of rolling bearing 5, and f represents turn frequency of double-fed generator;
Rolling body fault characteristic frequency computing module, for calculating the rolling body fault characteristic frequency of the rolling bearing 5 of double-fed generator according to formula (5);
f b=1/2·R pmi/60·D/d·(1-( d/D·cosа) 2) （5）
In formula (5), f brepresent the rolling body fault characteristic frequency of rolling bearing 5, R pmirepresent the inner ring frequency of rolling bearing 5, d represents the rolling body diameter of rolling bearing 5, and D represents the rolling body pitch diameter of rolling bearing 5, and а represents the contact angle of rolling bearing 5;
Retainer fault characteristic frequency computing module, for calculating the retainer fault characteristic frequency of the rolling bearing 5 of double-fed generator according to formula (6);
f c=1/2·R pmi/60·(1-d/D·cosа)±R pm0/60·(1+d/D·cosа) （6）
In formula (6), f crepresent the retainer fault characteristic frequency of rolling bearing 5, R pmirepresent the inner ring frequency of rolling bearing 5, R pm0represent the outer ring frequency of rolling bearing 5, d represents the rolling body diameter of rolling bearing 5, and D represents the rolling body pitch diameter of rolling bearing 5, and а represents the contact angle of rolling bearing 5;
Fault characteristic frequency compares to determine module, for the bearing fault characteristics frequency signal of double-fed generator drive end, anti-drive end rolling bearing 5 is compared with the outer ring fault characteristic frequency of rolling bearing 5, the inner ring fault characteristic frequency of rolling bearing 5, the rolling body fault characteristic frequency of rolling bearing 5, the retainer fault characteristic frequency of rolling bearing 5 respectively, thus judge the fault type of the rolling bearing 5 of double-fed generator drive end, anti-drive end and fault degree and export judged result.
The above is only the preferred embodiment of the present invention, protection scope of the present invention be not only confined to above-described embodiment, and all technical schemes belonged under thinking of the present invention all belong to protection scope of the present invention.It should be pointed out that for those skilled in the art, some improvements and modifications without departing from the principles of the present invention, these improvements and modifications also should be considered as protection scope of the present invention.

Claims (6)

1. a wind-powered electricity generation double-fed generator rolling bearing fault method of discrimination, is characterized in that implementation step is as follows:
1) acceleration signal of double-fed generator drive end, the acceleration signal of anti-drive end is detected when double-fed generator runs;
2) extract the acceleration extreme point signal of described acceleration signal respectively, obtain the time series of double-fed generator drive end, anti-drive end acceleration extreme point;
3) calculate the elastic anchorage force of base angle resiliency supported of double-fed generator drive end, anti-drive end respectively according to the time series of described acceleration extreme point, obtain the elastic anchorage force time series of base angle resiliency supported of double-fed generator drive end, anti-drive end;
4) respectively the time series of described elastic anchorage force is carried out DFFT conversion, obtain the bearing fault characteristics frequency signal of rolling bearing of double-fed generator drive end, anti-drive end, the bearing fault characteristics frequency signal according to double-fed generator drive end, anti-drive end carries out breakdown judge respectively and judged result is exported.
2. wind-powered electricity generation double-fed generator rolling bearing fault method of discrimination according to claim 1, is characterized in that: the elastic anchorage force calculating base angle resiliency supported respectively according to the time series of described acceleration extreme point respectively in described step 3) specifically refers to and calculates the elastic anchorage force of the base angle resiliency supported of double-fed generator drive end according to formula (1), calculate the elastic anchorage force of the base angle resiliency supported of double-fed generator anti-drive end according to formula (2);
F 1N=（a 1 2·（L+ L 2）·а 1N/ b 1+ a 2 2·L 2·а 2N/ b 2）/(L 2+ L·L 1+ L·L 2) （1）
F 2N=-（a 1 2·L 1·а 1N/ b 1+ a 2 2·（L+ L 1）·а 2N/ b 2）/(L 2+ L·L 1+ L·L 2) （2）
In formula (1) and formula (2), F 1Nrepresent the elastic anchorage force of the base angle resiliency supported of double-fed generator drive end, F 2Nrepresent the elastic anchorage force of the base angle resiliency supported of double-fed generator anti-drive end, N is time series; a 1calculation expression be a 1=J 2/ L(1+(k 1j 1)/(k 2j 2)), a 2calculation expression be a 2=J 1/ L(1+(k 2j 2)/(k 1j 1)), b 1and k 1all represent the rigidity of the base angle resiliency supported of double-fed generator drive end, b 2and k 2all represent the rigidity of the base angle resiliency supported of double-fed generator anti-drive end, а 1Nrepresent the time series of double-fed generator drive end acceleration extreme point, а 2Nrepresent the time series of double-fed generator anti-drive end acceleration extreme point, J 1represent the moment of inertia of the base angle resiliency supported of double-fed generator drive end, J 2represent the moment of inertia of the base angle resiliency supported of double-fed generator anti-drive end, L represents the centre distance between the base angle resiliency supported of generator drive end and the base angle resiliency supported of anti-drive end, L 1represent the distance between the center line of the base angle resiliency supported of generator drive end and generator drive end end cap outermost end, L 2represent the distance between the center line of the base angle resiliency supported of generator anti-drive end and generator non-drive end shield outermost end.
3. wind-powered electricity generation double-fed generator rolling bearing fault method of discrimination according to claim 1 and 2, it is characterized in that, carry out the detailed step of breakdown judge respectively according to the bearing fault characteristics frequency signal of the rolling bearing of double-fed generator drive end, anti-drive end in described step 4) as follows:
4.1) according to the outer ring fault characteristic frequency of the rolling bearing of formula (3) calculating double-fed generator drive end, anti-drive end;
f 0=Z/2·(1-d/D·cosа)·f （3）
In formula (3), f 0represent the outer ring fault characteristic frequency of rolling bearing, Z represents the rolling body quantity of rolling bearing, and d represents the rolling body diameter of rolling bearing, and D represents the rolling body pitch diameter of rolling bearing, and а represents the contact angle of rolling bearing, and f represents turn frequency of double-fed generator;
4.2) according to the inner ring fault characteristic frequency of the rolling bearing of formula (4) calculating double-fed generator drive end, anti-drive end;
f i=Z/2·(1+d/D·cosа)·f （4）
In formula (4), f irepresent the inner ring fault characteristic frequency of rolling bearing, Z represents the rolling body quantity of rolling bearing, and d represents the rolling body diameter of rolling bearing, and D represents the rolling body pitch diameter of rolling bearing, and а represents the contact angle of rolling bearing, and f represents turn frequency of double-fed generator;
4.3) according to the rolling body fault characteristic frequency of the rolling bearing of formula (5) calculating double-fed generator drive end, anti-drive end;
f b=1/2·R pmi/60·D/d·(1-(d/D·cosа) 2) （5）
In formula (5), f brepresent the rolling body fault characteristic frequency of rolling bearing, R pmirepresent the inner ring frequency of rolling bearing, d represents the rolling body diameter of rolling bearing, and D represents the rolling body pitch diameter of rolling bearing, and а represents the contact angle of rolling bearing;
4.4) according to the retainer fault characteristic frequency of the rolling bearing of formula (6) calculating double-fed generator drive end, anti-drive end;
f c=1/2·R pmi/60·(1-d/D·cosа)±R pm0/60·(1+d/D·cosа) （6）
In formula (6), f crepresent the retainer fault characteristic frequency of rolling bearing, R pmirepresent the inner ring frequency of rolling bearing, R pm0represent the outer ring frequency of rolling bearing, d represents the rolling body diameter of rolling bearing, and D represents the rolling body pitch diameter of rolling bearing, and а represents the contact angle of rolling bearing;
4.5) the bearing fault characteristics frequency signal of the rolling bearing of described double-fed generator drive end, anti-drive end is compared with the outer ring fault characteristic frequency of described rolling bearing, inner ring fault characteristic frequency, rolling body fault characteristic frequency, retainer fault characteristic frequency respectively, thus judge the fault type of the rolling bearing of double-fed generator drive end, anti-drive end and fault degree according to the matching degree between two frequencies compared and export judged result.
4. a wind-powered electricity generation double-fed generator rolling bearing fault discriminating gear, is characterized in that comprising:
First acceleration transducer, for detecting the acceleration signal of double-fed generator drive end when double-fed generator runs;
Second acceleration transducer, for detecting the acceleration signal of double-fed generator anti-drive end when double-fed generator runs;
Acceleration extreme point signal extraction module, for extracting the acceleration extreme point signal of described acceleration signal respectively, obtains the time series of double-fed generator drive end, anti-drive end acceleration extreme point;
Elastic anchorage force computing module, for calculating the elastic anchorage force of base angle resiliency supported of double-fed generator drive end, anti-drive end respectively according to the time series of described acceleration extreme point, obtain the elastic anchorage force time series of base angle resiliency supported of double-fed generator drive end, anti-drive end;
Fault characteristic frequency computing module, for respectively the time series of described elastic anchorage force being carried out DFFT conversion, obtains the bearing fault characteristics frequency signal of double-fed generator drive end, anti-drive end;
Breakdown judge module, for carry out respectively according to the bearing fault characteristics frequency signal of double-fed generator drive end, anti-drive end double-fed generator drive end, anti-drive end breakdown judge and judged result is exported.
5. wind-powered electricity generation double-fed generator rolling bearing fault discriminating gear according to claim 4, is characterized in that: described elastic anchorage force computing module comprises:
Drive end elastic anchorage force computing module, for calculating the elastic anchorage force of the base angle resiliency supported of double-fed generator drive end according to formula (1);
Anti-drive end elastic anchorage force computing module, for calculating the elastic anchorage force of the base angle resiliency supported of double-fed generator anti-drive end according to formula (2);
F 1N=（a 1 2·（L+ L 2）·а 1N/ b 1+ a 2 2·L 2·а 2N/ b 2）/(L 2+ L·L 1+ L·L 2) （1）
F 2N=-（a 1 2·L 1·а 1N/ b 1+ a 2 2·（L+ L 1）·а 2N/ b 2）/(L 2+ L·L 1+ L·L 2) （2）
In formula (1) and formula (2), F 1Nrepresent the elastic anchorage force of the base angle resiliency supported of double-fed generator drive end, F 2Nrepresent the elastic anchorage force of the base angle resiliency supported of double-fed generator anti-drive end, N is time series; a 1calculation expression be a 1=J 2/ L(1+(k 1j 1)/(k 2j 2)), a 2calculation expression be a 2=J 1/ L(1+(k 2j 2)/(k 1j 1)), b 1and k 1all represent the rigidity of the base angle resiliency supported of double-fed generator drive end, b 2and k 2all represent the rigidity of the base angle resiliency supported of double-fed generator anti-drive end, а 1Nrepresent the time series of double-fed generator drive end acceleration extreme point, а 2Nrepresent the time series of double-fed generator anti-drive end acceleration extreme point, J 1represent the moment of inertia of the base angle resiliency supported of double-fed generator drive end, J 2represent the moment of inertia of the base angle resiliency supported of double-fed generator anti-drive end, L represents the centre distance between the base angle resiliency supported of generator drive end and the base angle resiliency supported of anti-drive end, L 1represent the distance between the center line of the base angle resiliency supported of generator drive end and generator drive end end cap outermost end, L 2represent the distance between the center line of the base angle resiliency supported of generator anti-drive end and generator non-drive end shield outermost end.
6. the double-fed generator rolling bearing fault discriminating gear of the wind-powered electricity generation according to claim 4 or 5, is characterized in that, described breakdown judge module comprises:
Outer ring fault characteristic frequency computing module, for the outer ring fault characteristic frequency of the rolling bearing according to formula (3) calculating double-fed generator drive end, anti-drive end;
f 0=Z/2·(1-d/D·cosа)·f （3）
In formula (3), f 0represent the outer ring fault characteristic frequency of rolling bearing, Z represents the rolling body quantity of rolling bearing, and d represents the rolling body diameter of rolling bearing, and D represents the rolling body pitch diameter of rolling bearing, and а represents the contact angle of rolling bearing, and f represents turn frequency of double-fed generator;
Inner ring fault characteristic frequency computing module, for the inner ring fault characteristic frequency of the rolling bearing according to formula (4) calculating double-fed generator drive end, anti-drive end;
f i=Z/2·(1+d/D·cosа)·f （4）
In formula (4), f irepresent the inner ring fault characteristic frequency of rolling bearing, Z represents the rolling body quantity of rolling bearing, and d represents the rolling body diameter of rolling bearing, and D represents the rolling body pitch diameter of rolling bearing, and а represents the contact angle of rolling bearing, and f represents turn frequency of double-fed generator;
Rolling body fault characteristic frequency computing module, for the rolling body fault characteristic frequency of the rolling bearing according to formula (5) calculating double-fed generator drive end, anti-drive end;
f b=1/2·R pmi/60·D/d·(1-(d/D·cosа) 2) （5）
In formula (5), f brepresent the rolling body fault characteristic frequency of rolling bearing, R pmirepresent the inner ring frequency of rolling bearing, d represents the rolling body diameter of rolling bearing, and D represents the rolling body pitch diameter of rolling bearing, and а represents the contact angle of rolling bearing;
Retainer fault characteristic frequency computing module, for the retainer fault characteristic frequency of the rolling bearing according to formula (6) calculating double-fed generator drive end, anti-drive end;
f c=1/2·R pmi/60·(1-d/D·cosа)±R pm0/60·(1+d/D·cosа) （6）
In formula (6), f crepresent rolling bearing retainer fault characteristic frequency, R pmirepresent the inner ring frequency of rolling bearing, R pm0represent the outer ring frequency of rolling bearing, d represents the rolling body diameter of rolling bearing, and D represents the rolling body pitch diameter of rolling bearing, and а represents the contact angle of rolling bearing;
Fault characteristic frequency compares to determine module, for respectively the bearing fault characteristics frequency signal of the rolling bearing of described double-fed generator drive end, anti-drive end being compared with the outer ring fault characteristic frequency of described rolling bearing, inner ring fault characteristic frequency, rolling body fault characteristic frequency, retainer fault characteristic frequency respectively, thus judge the fault type of rolling bearing and fault degree according to the matching degree between two frequencies compared and export judged result.
CN201310603092.8A 2013-11-26 2013-11-26 Wind-powered electricity generation double-fed generator rolling bearing fault method of discrimination and device Expired - Fee Related CN103575535B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201310603092.8A CN103575535B (en) 2013-11-26 2013-11-26 Wind-powered electricity generation double-fed generator rolling bearing fault method of discrimination and device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201310603092.8A CN103575535B (en) 2013-11-26 2013-11-26 Wind-powered electricity generation double-fed generator rolling bearing fault method of discrimination and device

Publications (2)

Publication Number Publication Date
CN103575535A CN103575535A (en) 2014-02-12
CN103575535B true CN103575535B (en) 2015-09-09

Family

ID=50047791

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201310603092.8A Expired - Fee Related CN103575535B (en) 2013-11-26 2013-11-26 Wind-powered electricity generation double-fed generator rolling bearing fault method of discrimination and device

Country Status (1)

Country Link
CN (1) CN103575535B (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104034369B (en) * 2014-06-23 2016-06-01 康吉诺（北京）科技有限公司 A kind of Analysis on Fault Diagnosis instrument
CN107643180A (en) * 2016-07-21 2018-01-30 北京航天动力研究所 High-speed low temperature turbine pump retainer method for diagnosing faults based on wavelet analysis
CN108204897B (en) * 2016-12-16 2020-05-22 唐智科技湖南发展有限公司 Method for judging correctness of bearing parameters and automatically diagnosing and matching multiple parameters
CN110470494A (en) * 2018-05-11 2019-11-19 浙江盾安人工环境股份有限公司 A kind of monitoring of air-conditioning vibration and diagnostic method
CN108680856A (en) * 2018-05-24 2018-10-19 龙逸电科（天津）技术有限公司 A kind of power distribution network generating set fault detection system
CN111654141A (en) * 2020-06-03 2020-09-11 宁波大学 Electromagnetic induction type bearing rotating speed measuring device and measuring method

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1825082A (en) * 2006-03-31 2006-08-30 洛阳轴研科技股份有限公司 Automatic diagnosing system for rolling bearing fault
CN102798529A (en) * 2012-08-30 2012-11-28 桂林电子科技大学 Method and system for diagnosing bearing faults of large-size wind turbine bearing

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5419472B2 (en) * 2009-01-09 2014-02-19 Ｎｔｎ株式会社 Wind turbine generator main shaft bearing monitoring device

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1825082A (en) * 2006-03-31 2006-08-30 洛阳轴研科技股份有限公司 Automatic diagnosing system for rolling bearing fault
CN102798529A (en) * 2012-08-30 2012-11-28 桂林电子科技大学 Method and system for diagnosing bearing faults of large-size wind turbine bearing

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
Sanna Pyhnen et al..Independent component analysis of vibrations for fault diagnosis of an induction motor.《Proceedings of the IASTED international Conference》.2003,Pages203-208. *
异步电动机轴承故障检测方法研究;陈凯;《中国优秀硕士学位论文全文数据库 工程科技II辑》;20070715(第1期);C042-39 *

Also Published As

Publication number Publication date
CN103575535A (en) 2014-02-12

Similar Documents

Publication Publication Date Title
CN103575535B (en) Wind-powered electricity generation double-fed generator rolling bearing fault method of discrimination and device
Chen et al. Bearing corrosion failure diagnosis of doubly fed induction generator in wind turbines based on stator current analysis
CN104075795B (en) Method and system for monitoring vibration state of impeller of wind generating set
CN101588112B (en) Electric brush slip ring fault diagnosis Device for fault mechanism diagnosis and maintenance and design method
CN101592590B (en) Fault indirect diagnosis technique of rotating blade
CN104865400B (en) A kind of detection recognition method and system of Wind turbines rotating speed
CN201714570U (en) Multifunctional wind turbine unit safety monitoring and fault diagnosis device
CN103925155B (en) The self-adapting detecting method that a kind of Wind turbines output is abnormal
CN102200186A (en) Remote on-line state monitoring and fault diagnosis system of gear box of wind generating set
CN206649082U (en) Wind power generating set slip ring dynamic electric resistor test device
CN103207081A (en) Engine rub-impact fault simulation experiment table applied to air channel static monitoring
CN202547923U (en) Vibration detecting device for pitch-variable bearing of wind turbine generator system
CN104393787A (en) Rotary piezoelectric cantilever energy harvester
CN110531259A (en) Induction machine electric fault diagnosis method based on magnetic leakage signal
CN103208880B (en) Magnetic suspension flywheel energy storage device and fault diagnosis method thereof
CN102352824A (en) Monitoring system based on electric information for health status of wind driven generator and monitoring method thereof
CN117077064B (en) Fault detection method, device and equipment for wind power equipment and storage medium
CN201448194U (en) Fan vibration monitoring device based on information fusion technology
Lee et al. Bearing fault detection of IPMSMs using zoom FFT
Wang et al. Early rolling bearing fault diagnosis in induction motors based on on-rotor sensing vibrations
CN102954888A (en) Real-time on-line diagnosis method for oil film oscillation fault of turboset
CN110486236B (en) Fault detection method and system for wind driven generator
KR20210033202A (en) A system for forecasting of break of industrial machinery/equipment
EP4239187A1 (en) Method and device for identifying a dominant mode during operation of a wind turbine
CN102900600A (en) Wind driven generator state monitoring method

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
C14 Grant of patent or utility model
GR01 Patent grant
CF01 Termination of patent right due to non-payment of annual fee
CF01 Termination of patent right due to non-payment of annual fee

Granted publication date: 20150909

Termination date: 20191126