CN102619875B - Self-aligning roller bearing for main shaft of wind turbine generator and design method thereof - Google Patents

Self-aligning roller bearing for main shaft of wind turbine generator and design method thereof Download PDF

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Publication number
CN102619875B
CN102619875B CN201210102961.4A CN201210102961A CN102619875B CN 102619875 B CN102619875 B CN 102619875B CN 201210102961 A CN201210102961 A CN 201210102961A CN 102619875 B CN102619875 B CN 102619875B
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bearing
roller
calculate
roller bearing
value
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CN102619875A (en
Inventor
于良峰
周传海
吕超
葛春丽
李刚强
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CRRC Wind Power Shandong Co Ltd
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Jinan Railway Vehicles Equipment Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
    • F16C23/086—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for rolling elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/10—Application independent of particular apparatuses related to size
    • F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/31—Wind motors

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  • Rolling Contact Bearings (AREA)
  • Wind Motors (AREA)

Abstract

The invention relates to a self-aligning roller bearing for a main shaft of a wind turbine generator and a design method thereof. The self-aligning roller bearing comprises a bearing outer ring, a bearing inner ring and two rows of rollers; and the self-aligning roller bearing is characterized in that the length of one row of rollers close to a wind wheel side on the self-aligning roller bearing is smaller than that of the other row. The design method of the bearing comprises the steps of: a, establishing a coordinate system; b. calculating stress of the main shaft by utilizing a formula F1=1/2C<F>RhoV<2>; c, calculating stress of the self-aligning roller bearing; d-1, calculating contact stress; d-2, fetching a lower limit value; d-3, fetching an upper limit value; d-4, implementing the calculation by utilizing a difference method, and d-5, calculating a proportionality factor satisfying an absolute value of (U<i> - V<i>) is smaller than 3U<i>/100 or an absolute value of (U<i> - V<i>) is smaller than 3V<i>/100, and designing a bearing meeting the requirement. According to the bearing and a bearing calculation method, the contact stress between each roller and a raceway can be effectively reduced; and a finite element method and the difference method are adopted, so that the difference value between the contact stresses of the two rows of rollers can be controlled within 3 percent, thereby solving the unbalance stress problem of the roller, reducing the failure rate and improving the service life of the bearing.

Description

A kind of wind driven generator principal shaft selfaligning roller bearing and design method thereof
Technical field
The present invention relates to a kind of wind driven generator principal shaft selfaligning roller bearing and design method thereof, in particular, relate in particular to a kind of unequal wind driven generator principal shaft selfaligning roller bearing of two rollers and design method thereof being applied on megawatt-level wind unit.
Background technique
Wind energy resources, as a kind of clean renewable energy sources, extensively exists in the whole world, and aboundresources is inexhaustible, the environmental protection of using.Therefore wind energy power has safe, clean feature, can be the mankind energy supply steady in a long-term is provided.At present, Main Developed Countries, developing country, the important means of all having challenged with the reply new century energy development wind energy power technology as state basic policy.
Transmitted chains is the core of wind power generating set, and main shaft bearing is to support the critical component that Transmitted chains runs well, and main shaft bearing performance directly determines the reliability of running of wind generating set, and the design of main shaft bearing is the important component part of Transmitted chains design.It is strong that selfaligning roller bearing has bearing capacity, manufacture simple, the feature that assembly process process is good, at present, commercial off-the-shelf megawatt-level wind unit adopts biserial spheric roller bearing form more, and two row roller specifications are identical, but, because wind-powered electricity generation unit is horizontal axis unit, in unit running process, the thrust that wind wheel is subject to is very big, and this thrust load is all born by main shaft bearing.Design feature due to double-row self-aligning roller bearing itself, be in the wind when receiving thrust, the roller stand under load of lower wind direction side is much larger than upwind side, according to on-the-spot test, the stressed difference of two row rollers is at least more than 3 times, front and back two row roller discontinuity equalizations, the wearing and tearing of rear row roller and raceway thereof are comparatively serious, had a strong impact on the working life of unit.
Summary of the invention
The present invention, in order to overcome the shortcoming of above-mentioned technical problem, provides a kind of unequal wind driven generator principal shaft selfaligning roller bearing of two rollers and design method thereof being applied on megawatt-level wind unit.
Wind driven generator principal shaft selfaligning roller bearing of the present invention, wind-driven generator comprise accept wind energy wind wheel, for the main shaft of transferring power and the bearing support that is arranged on main shaft, form, bearing support forms the selfaligning roller bearing that has comprised carrying effect, and selfaligning roller bearing comprises bearing outer ring, bearing inner race and two row rollers; It is characterized in that: on selfaligning roller bearing, the length of a row roller of close wind wheel side is less than the length of another row roller.Main shaft is for being delivered to the rotation of wind wheel the input end of gear-box, and selfaligning roller bearing is arranged on bearing support and forms above, guarantees that main shaft can freely rotate.Due to the selfaligning roller bearing effect that is not only stressed, be also subject to the powerful thrust that produced by wind wheel, cause the row roller away from wind wheel end very easily to wear and tear; Therefore the roller length away from wind wheel side is designed to be greater than the length of another row roller, can effectively increases the wear-resisting property of whole selfaligning roller bearing, increase the service life.
Wind driven generator principal shaft selfaligning roller bearing of the present invention, what on described bearing inner race, arrange does not match raceway width not etc. with two row rollers, and the raceway width matching with large size roller is greater than the raceway width matching with small size roller.The size of two row rollers is unequal, is easy to process the raceway adapting with roller length.
Wind driven generator principal shaft selfaligning roller bearing of the present invention, is provided with oil groove on described bearing outer ring, a side of oil groove deflection small size roller.Oil groove is arranged on the bearing outer ring between two row rollers.
Wind driven generator principal shaft selfaligning roller bearing of the present invention, described bearing support forms and also comprises bearing (ball) cover, bearing support, seal ring and sealing bracing ring; Bearing seat is in the periphery of selfaligning roller bearing, and bearing (ball) cover, seal ring and sealing bracing ring are positioned at the both sides of selfaligning roller bearing.
The design method of wind driven generator principal shaft selfaligning roller bearing of the present invention, wind-driven generator comprises wind wheel, play the gear-box of accelerating function and for connecting the main shaft of wind wheel and gear-box, selfaligning roller bearing is arranged on main shaft, and the roller length near wind wheel side on selfaligning roller bearing is less than the roller length near gear box side; It is characterized in that, design bearing method comprises the following steps: a. sets up system of coordinates, take the intersection point of wind wheel and the main shaft two-dimensional coordinate system in initial point is set up vertical plane, and this system of coordinates is the rest frame of not rotating with wind wheel; B. calculate stressed at true origin place of main shaft, establish
Figure 2012101029614100002DEST_PATH_IMAGE001
for the active force being produced by the suffered thrust of wind wheel,
Figure 2012101029614100002DEST_PATH_IMAGE002
active force for the gravity by wind wheel and spindle unit produces, calculates according to formula size;
（1）
Wherein,
Figure 2012101029614100002DEST_PATH_IMAGE004
For thrust coefficient, For atmospheric density,
Figure 2012101029614100002DEST_PATH_IMAGE006
For wind speed; Thrust coefficient
Figure 774894DEST_PATH_IMAGE004
Be averaged wind speed respective value, wind speed according to thrust coefficient curve Desirable annual mean wind speed is simplified calculating; C. calculate self-aligning roller bearing stressed,If thrust and pressure that self-aligning roller bearing center is suffered are respectively
Figure 2012101029614100002DEST_PATH_IMAGE007
With , the active force that gear-box produces main shaft at vertical direction is
Figure 2012101029614100002DEST_PATH_IMAGE009
; By
Figure 759960DEST_PATH_IMAGE007
=
Figure 512016DEST_PATH_IMAGE001
,
Figure 334478DEST_PATH_IMAGE008
= +
Figure 987362DEST_PATH_IMAGE009
Calculate the suffered thrust of self-aligning roller bearing and pressure; D. self-aligning roller bearing design, what establish close wind wheel one side is front row roller, length is
Figure 2012101029614100002DEST_PATH_IMAGE010
; Near gear-box one side be rear row roller, length is
Figure 2012101029614100002DEST_PATH_IMAGE011
; The contact stress of front row roller and rear row roller and raceway is respectively
Figure 2012101029614100002DEST_PATH_IMAGE012
With
Figure DEST_PATH_IMAGE013
;If proportionality coefficient
Figure 2012101029614100002DEST_PATH_IMAGE014
=
Figure 220023DEST_PATH_IMAGE010
/
Figure 213387DEST_PATH_IMAGE011
; Calculate according to following steps ,
Figure 891679DEST_PATH_IMAGE011
Size: d-1. calculates the contact stress of roller and raceway, when
Figure 352747DEST_PATH_IMAGE010
,
Figure 782591DEST_PATH_IMAGE011
Get in the situation of concrete numerical value, according to bearing inner race diameter, bearing outer diameter, bearing width, the thrust of self-aligning roller bearing
Figure 709703DEST_PATH_IMAGE007
And pressure
Figure 984826DEST_PATH_IMAGE008
, calculate contact stress
Figure 628297DEST_PATH_IMAGE012
With ; D-2. take off limit value, get one group of forward and backward row roller length value
Figure 2012101029614100002DEST_PATH_IMAGE016
With
Figure DEST_PATH_IMAGE017
, calculate the contact stress of forward and backward row roller and raceway according to the computational methods in steps d-1
Figure 2012101029614100002DEST_PATH_IMAGE018
,
Figure DEST_PATH_IMAGE019
, adjust With
Figure 443117DEST_PATH_IMAGE017
Size, make >
Figure 957592DEST_PATH_IMAGE019
, record
Figure 2012101029614100002DEST_PATH_IMAGE020
=
Figure 916190DEST_PATH_IMAGE016
/
Figure 489997DEST_PATH_IMAGE017
In Value; D-3. capping value, gets one group of forward and backward row roller length value
Figure DEST_PATH_IMAGE021
With , calculate the contact stress of forward and backward row roller and raceway according to the computational methods in steps d-1
Figure DEST_PATH_IMAGE023
, , adjust
Figure 849621DEST_PATH_IMAGE021
With
Figure 729852DEST_PATH_IMAGE022
Size, make
Figure 167786DEST_PATH_IMAGE023
>
Figure 276819DEST_PATH_IMAGE024
, record
Figure DEST_PATH_IMAGE025
=
Figure 687072DEST_PATH_IMAGE021
/
Figure 800521DEST_PATH_IMAGE022
In
Figure 725752DEST_PATH_IMAGE025
Value; D-4. get
Figure 2012101029614100002DEST_PATH_IMAGE026
=(
Figure 137011DEST_PATH_IMAGE020
+ )/2, according to
Figure 420541DEST_PATH_IMAGE026
=
Figure DEST_PATH_IMAGE027
/
Figure 2012101029614100002DEST_PATH_IMAGE028
, calculate
Figure 518554DEST_PATH_IMAGE027
With
Figure 484236DEST_PATH_IMAGE028
Value, calculate the contact stress of forward and backward row roller and raceway according to the computational methods in steps d-1 ,
Figure 2012101029614100002DEST_PATH_IMAGE030
; If
Figure 852769DEST_PATH_IMAGE029
<
Figure 42442DEST_PATH_IMAGE030
, get
Figure DEST_PATH_IMAGE031
=(
Figure 879948DEST_PATH_IMAGE020
+
Figure 134474DEST_PATH_IMAGE026
)/2; If
Figure 436143DEST_PATH_IMAGE029
>
Figure 921351DEST_PATH_IMAGE030
, get
Figure 308470DEST_PATH_IMAGE031
=(
Figure 615954DEST_PATH_IMAGE025
+
Figure 506550DEST_PATH_IMAGE026
), the like; D-5. in steps d-4, proportionality coefficient
Figure 2012101029614100002DEST_PATH_IMAGE032
=
Figure DEST_PATH_IMAGE033
/
Figure 2012101029614100002DEST_PATH_IMAGE034
Time, calculate corresponding contact stress and whether meet |
Figure DEST_PATH_IMAGE035
-
Figure 2012101029614100002DEST_PATH_IMAGE036
| <3
Figure 113724DEST_PATH_IMAGE035
/ 100 and |
Figure 722560DEST_PATH_IMAGE035
- | <3
Figure 844417DEST_PATH_IMAGE036
/ 100, record satisfies condition
Figure 812373DEST_PATH_IMAGE032
Value, according to
Figure 596920DEST_PATH_IMAGE033
With
Figure 308524DEST_PATH_IMAGE034
Value is determined bearing roller size, designs satisfactory bearing.
Computational methods of the present invention, can utilize finite element algorithm to calculate the contact stress of roller and raceway, utilize interpolation to determine the scaling factor of two row rollers, design the roller of two row's different sizes, before and after making, the suffered contact stress of two row rollers is equal as far as possible, the difference of contact stress less contact stress 3% with interior think meet design requirement.Steps d adopts interpolation to calculate, and gets larger roller scaling factor
Figure 111395DEST_PATH_IMAGE025
less roller scaling factor
Figure 250253DEST_PATH_IMAGE020
, before and after making there is the state that size is contrary in two row roller contact stress, gets
Figure 833681DEST_PATH_IMAGE020
with
Figure 270347DEST_PATH_IMAGE025
average
Figure 193304DEST_PATH_IMAGE026
; Again relatively at scaling factor
Figure 503062DEST_PATH_IMAGE026
two row roller contact stress states before and after lower bearing; If
Figure 259272DEST_PATH_IMAGE020
lower with
Figure 312679DEST_PATH_IMAGE026
the contact stress state of lower two row rollers is identical, gets with
Figure 757753DEST_PATH_IMAGE026
average be scaling factor
Figure 987877DEST_PATH_IMAGE031
otherwise, get
Figure 844975DEST_PATH_IMAGE020
with
Figure 227677DEST_PATH_IMAGE026
average be scaling factor , by that analogy, until the difference of bearing front and back two row roller contact stress is in less contact stress 3%.
The invention has the beneficial effects as follows: wind driven generator principal shaft selfaligning roller bearing of the present invention, according to the stressed unequal feature of the forward and backward row roller of bearing, selfaligning roller bearing is designed to little, the rear row roller of front row roller large, can effectively reduce the contact stress of roller and raceway, avoid in the past due to the stressed large and phenomenon of serious wear of rear row roller; Reduce rate of fault, improved bearing working life.The little side of oil groove deflection roller dimension, and the width of raceway and the size of roller are directly proportional.The design method of wind driven generator principal shaft selfaligning roller bearing of the present invention, by the qualitative and quantitative analysis to selfaligning roller bearing stressing conditions, adopt finite element and difference arithmetic to calculate rational front and rear row roller length, and by the difference of two row roller contact stress be controlled at less contact stress 3% in, make the working life of two row rollers basically identical, effectively improved bearing working life.
Accompanying drawing explanation
Fig. 1 is the structural representation of selfaligning roller bearing for existing wind driven generator principal shaft;
Fig. 2 is the structural representation of selfaligning roller bearing of the present invention;
Fig. 3 is structural representation and the force analysis figure of wind turbine transmission chain of the present invention;
Fig. 4 is the force analysis figure of selfaligning roller bearing in the present invention;
Fig. 5 is the structural representation that bottom bracket of the present invention forms.
In figure: 1 bearing outer ring, 2 front row rollers, 3 rear row rollers, 4 bearing inner races, 5 bearing outer rings, 6 front row rollers, 7 rear row rollers, 8 bearing inner races, 9 wind wheels, 10 main shafts, 11 bearing supports form, 12 gear-boxes, 13 bearing (ball) covers, 14 bearing supports, 15 selfaligning roller bearings, 16 seal rings, 17 sealing bracing rings, 18 locknuts.
Embodiment
Below in conjunction with accompanying drawing and embodiment, the invention will be further described.
As shown in Figure 1, provided the structural representation of selfaligning roller bearing for existing wind driven generator principal shaft, it comprises bearing outer ring 1, bearing inner race 4, front row roller 2, rear row roller 3; The diameter dimension of front row roller 2 and rear row roller 3 equates.In the process of using, because the thrust that wind wheel is subject to is very big, this thrust load is all born by the selfaligning roller bearing on main shaft, makes the roller stand under load of lower wind direction side much larger than upwind side.The stressed difference of general two row rollers (2,3) is at least more than 3 times, front and back two row roller discontinuity equalizations, and the wearing and tearing of rear row roller 3 and raceway thereof are comparatively serious, had a strong impact on the working life of unit.
As shown in Figure 2, provided the structural representation of selfaligning roller bearing of the present invention, it comprises bearing outer ring 5, front row roller 6, rear row roller 7 and bearing inner race 8; Fig. 3 and Fig. 5 have provided respectively wind turbine transmission chain and bearing support forms 11 structural representation, and the Transmitted chains of wind-powered electricity generation unit comprises wind wheel 9, main shaft 10, bearing support composition 11 and gear-box 12; Bearing support forms 11 and comprises bearing (ball) cover 13, bearing support 14, selfaligning roller bearing 15, seal ring 16, sealing bracing ring 17, locknut 18.In the Transmitted chains of wind-powered electricity generation unit, wind wheel 9 is for receiving wind energy and driving main shaft 10 to rotate, and main shaft 10 is input to the rotation of wind wheel 9 input end of gear-box 12, and gear-box 12 is step-up gear.Bearing support forms 11 on the main shaft 10 between wind wheel 9 and gear-box 12, and bearing support forms the location that the selfaligning roller bearing 15 on 11 is realized main shaft, guarantees that main shaft 10 freely rotates.Front row roller 6 is the row roller near wind wheel 9 one sides, and rear row roller 7 is the roller away from wind wheel 9 one sides, and the length of rear row roller 7 is greater than the length of front row roller 6.Like this, even if the active force that rear row roller 7 bears is larger, also can guarantee that front and rear row roller (6,7) equates with the contact stress of raceway or it is equal to approach, the transition of row roller 7 after while having avoided two row roller sizes to equate, cross quick-wearing, effectively extended the working life of selfaligning roller bearing 15.
Bearing support 14 is positioned at the periphery of selfaligning roller bearing 15, realizes the fixation to selfaligning roller bearing 15; Bearing (ball) cover 13, seal ring 16 and sealing bracing ring 17 are arranged at the both sides of selfaligning roller bearing 15, realize the effective location to selfaligning roller bearing 15.The phase place effect that locknut 18 is realized sealing bracing ring 17.
Because rear row roller 7 and raceway area of contact are large, can reduce the contact stress between roller and raceway, reduced rate of fault, improve bearing working life.Oil groove on bearing outer ring 5 is not in centre, but row roller 6 one sides before deflection.Bearing inner race 8 left-right asymmetries, the raceway of front row roller 6 correspondences is narrow.Meanwhile, the bearing of design should have assembly process process, guarantees that bearing and bearing support are easy to assembling.
By the Design of length of rear row roller 7, be to be only greater than the length of front-seat 6 rollers or far from being enough, because without quantitative analysis, how must do not go out the contact stress of front row roller 6, rear row roller 7 and track, equate, approach or differ greatly.Provide the design method of this wind driven generator principal shaft selfaligning roller bearing below, so that the contact stress that obtains front row roller 6, rear row roller 7 and raceway on long terms selfaligning roller bearing about equally.It comprises the following steps:
A. set up system of coordinates, take the intersection point of wind wheel and the main shaft two-dimensional coordinate system in initial point is set up vertical plane, this system of coordinates is the rest frame of not rotating with wind wheel; The initial point of system of coordinates is power in Fig. 3
Figure 924554DEST_PATH_IMAGE001
with power
Figure 257447DEST_PATH_IMAGE002
intersection point;
B. calculate stressed at true origin place of main shaft, establish
Figure 993190DEST_PATH_IMAGE001
for the active force being produced by the suffered thrust of wind wheel,
Figure 81232DEST_PATH_IMAGE002
active force for the gravity by wind wheel and spindle unit produces, calculates according to formula (1)
Figure 348265DEST_PATH_IMAGE001
size;
Figure 484848DEST_PATH_IMAGE003
（1）
Wherein,
Figure 888148DEST_PATH_IMAGE004
for thrust coefficient,
Figure 832577DEST_PATH_IMAGE005
for air density, for wind speed; Thrust coefficient
Figure 261601DEST_PATH_IMAGE004
according to thrust coefficient curve, be averaged wind speed respective value, wind speed desirable annual mean wind speed is simplified calculating;
C. calculate selfaligning roller bearing stressed, establish the suffered thrust in selfaligning roller bearing center and pressure and be respectively
Figure 401781DEST_PATH_IMAGE007
with , as shown in Figure 4, the active force that gear-box produces main shaft at vertical direction is
Figure 918530DEST_PATH_IMAGE009
; By
Figure 499685DEST_PATH_IMAGE007
= ,
Figure 252188DEST_PATH_IMAGE008
=
Figure 331002DEST_PATH_IMAGE002
+
Figure 828980DEST_PATH_IMAGE009
calculate the suffered thrust of selfaligning roller bearing and pressure;
D. selfaligning roller bearing design, what establish close wind wheel one side is front row roller, length is
Figure 272731DEST_PATH_IMAGE010
; Near gear-box one side be rear row roller, length is ; The contact stress of front row roller and rear row roller and raceway is respectively
Figure 558404DEST_PATH_IMAGE012
with
Figure 910888DEST_PATH_IMAGE013
; If scaling factor
Figure 791120DEST_PATH_IMAGE014
=
Figure 229054DEST_PATH_IMAGE010
/
Figure 649671DEST_PATH_IMAGE011
; According to following steps, calculate
Figure 831164DEST_PATH_IMAGE010
,
Figure 679035DEST_PATH_IMAGE011
size:
D-1. calculate the contact stress of roller and raceway, when
Figure 541948DEST_PATH_IMAGE010
,
Figure 766256DEST_PATH_IMAGE011
get in the situation of concrete numerical value, according to bearing inner race diameter, bearing outer diameter, bearing width, the thrust of selfaligning roller bearing
Figure 280283DEST_PATH_IMAGE007
and pressure
Figure 564634DEST_PATH_IMAGE008
, calculate contact stress
Figure 977161DEST_PATH_IMAGE012
with ; In the process of calculating, can adopt finite element algorithm;
D-2. take off limit value, get one group of forward and backward row roller length value
Figure 858846DEST_PATH_IMAGE016
with
Figure 2514DEST_PATH_IMAGE017
, according to the computational methods in steps d-1, calculate the contact stress of forward and backward row roller and raceway
Figure 902337DEST_PATH_IMAGE018
,
Figure 468447DEST_PATH_IMAGE019
, adjust
Figure 442219DEST_PATH_IMAGE016
with
Figure 68373DEST_PATH_IMAGE017
size, make >
Figure 746665DEST_PATH_IMAGE019
, record
Figure 840523DEST_PATH_IMAGE020
= /
Figure 246413DEST_PATH_IMAGE017
in
Figure 105392DEST_PATH_IMAGE020
value;
D-3. capping value, gets one group of forward and backward row roller length value with
Figure 21712DEST_PATH_IMAGE022
, according to the computational methods in steps d-1, calculate the contact stress of forward and backward row roller and raceway
Figure 117844DEST_PATH_IMAGE023
,
Figure 750819DEST_PATH_IMAGE024
, adjust
Figure 881586DEST_PATH_IMAGE021
with
Figure 20444DEST_PATH_IMAGE022
size, make
Figure 541555DEST_PATH_IMAGE023
<
Figure 791271DEST_PATH_IMAGE024
, record
Figure 464960DEST_PATH_IMAGE025
=
Figure 774718DEST_PATH_IMAGE021
/
Figure 845443DEST_PATH_IMAGE022
in
Figure 836532DEST_PATH_IMAGE025
value;
D-4. get
Figure 676312DEST_PATH_IMAGE026
=(
Figure 343923DEST_PATH_IMAGE020
+ )/2, according to =
Figure 125431DEST_PATH_IMAGE027
/
Figure 776992DEST_PATH_IMAGE028
, calculate
Figure 507795DEST_PATH_IMAGE027
with
Figure 903004DEST_PATH_IMAGE028
value, according to the computational methods in steps d-1, calculate the contact stress of forward and backward row roller and raceway
Figure 389480DEST_PATH_IMAGE029
,
Figure 477522DEST_PATH_IMAGE030
; If
Figure 931506DEST_PATH_IMAGE029
< , get
Figure 533705DEST_PATH_IMAGE031
=(
Figure 730332DEST_PATH_IMAGE020
+
Figure 219082DEST_PATH_IMAGE026
)/2; If >
Figure 433474DEST_PATH_IMAGE030
, get
Figure 535422DEST_PATH_IMAGE031
=(
Figure 777047DEST_PATH_IMAGE025
+ ), the like;
D-5. in steps d-4, scaling factor
Figure 882592DEST_PATH_IMAGE032
=
Figure 483338DEST_PATH_IMAGE033
/
Figure 884363DEST_PATH_IMAGE034
time, calculate corresponding contact stress and whether meet |
Figure 228757DEST_PATH_IMAGE035
-
Figure 726735DEST_PATH_IMAGE036
| <3
Figure 918288DEST_PATH_IMAGE035
/ 100 and |
Figure 259140DEST_PATH_IMAGE035
- | <3
Figure 120228DEST_PATH_IMAGE036
/ 100, record satisfies condition
Figure 797197DEST_PATH_IMAGE032
value, according to
Figure 172814DEST_PATH_IMAGE033
with
Figure 859010DEST_PATH_IMAGE034
value is determined bearing roller size, designs satisfactory bearing.

Claims (2)

1. the design method of a wind driven generator principal shaft selfaligning roller bearing, wind-driven generator comprises wind wheel (9), play the gear-box (12) of accelerating function and for connecting the main shaft (10) of wind wheel and gear-box, selfaligning roller bearing (15) is arranged on main shaft, and the roller length near wind wheel (9) side on selfaligning roller bearing is less than the roller length near gear box side; It is characterized in that, design bearing method comprises the following steps:
A. set up system of coordinates, take the intersection point of wind wheel and the main shaft two-dimensional coordinate system in initial point is set up vertical plane, this system of coordinates is the rest frame of not rotating with wind wheel;
B. calculate stressed at true origin place of main shaft, be made as
Figure 2012101029614100001DEST_PATH_IMAGE002
the active force being produced by the suffered thrust of wind wheel, active force for the gravity by wind wheel and spindle unit produces, calculates according to formula (1)
Figure 238033DEST_PATH_IMAGE002
size;
（1）
Wherein,
Figure 2012101029614100001DEST_PATH_IMAGE008
for thrust coefficient,
Figure 2012101029614100001DEST_PATH_IMAGE010
for air density,
Figure 2012101029614100001DEST_PATH_IMAGE012
for wind speed; Thrust coefficient
Figure 908836DEST_PATH_IMAGE008
according to thrust coefficient curve, be averaged wind speed respective value, wind speed
Figure 688573DEST_PATH_IMAGE012
desirable annual mean wind speed is simplified calculating;
C. calculate selfaligning roller bearing stressed, establish the suffered thrust in selfaligning roller bearing center and pressure and be respectively
Figure 2012101029614100001DEST_PATH_IMAGE014
with , the active force that gear-box produces main shaft at vertical direction is
Figure 2012101029614100001DEST_PATH_IMAGE018
; By
Figure 582318DEST_PATH_IMAGE014
=
Figure 396690DEST_PATH_IMAGE002
,
Figure 32202DEST_PATH_IMAGE016
=
Figure 299235DEST_PATH_IMAGE004
+
Figure 560452DEST_PATH_IMAGE018
calculate the suffered thrust of selfaligning roller bearing and pressure;
D. selfaligning roller bearing design, what establish close wind wheel one side is front row roller, length is
Figure 2012101029614100001DEST_PATH_IMAGE020
; Near gear-box one side be rear row roller, length is ; The contact stress of front row roller and rear row roller and raceway is respectively
Figure DEST_PATH_IMAGE024
with ; If scaling factor
Figure DEST_PATH_IMAGE028
=
Figure 744895DEST_PATH_IMAGE020
/
Figure 675942DEST_PATH_IMAGE022
; According to following steps, calculate
Figure 118686DEST_PATH_IMAGE020
,
Figure 855698DEST_PATH_IMAGE022
size:
D-1. calculate the contact stress of roller and raceway, when
Figure 379084DEST_PATH_IMAGE020
,
Figure 619048DEST_PATH_IMAGE022
get in the situation of concrete numerical value, according to bearing inner race diameter, bearing outer diameter, bearing width, the thrust of selfaligning roller bearing
Figure 673722DEST_PATH_IMAGE014
and pressure
Figure 948846DEST_PATH_IMAGE016
, calculate contact stress
Figure 592317DEST_PATH_IMAGE024
with
Figure DEST_PATH_IMAGE030
;
D-2. take off limit value, get one group of forward and backward row roller length value with , according to the computational methods in steps d-1, calculate the contact stress of forward and backward row roller and raceway
Figure DEST_PATH_IMAGE036
, , adjust
Figure 865166DEST_PATH_IMAGE032
with
Figure 472384DEST_PATH_IMAGE034
size, make
Figure 364248DEST_PATH_IMAGE036
>
Figure 924542DEST_PATH_IMAGE038
, record =
Figure 509238DEST_PATH_IMAGE032
/
Figure 459877DEST_PATH_IMAGE034
in
Figure 217748DEST_PATH_IMAGE040
value;
D-3. capping value, gets one group of forward and backward row roller length value
Figure DEST_PATH_IMAGE042
with
Figure DEST_PATH_IMAGE044
, according to the computational methods in steps d-1, calculate the contact stress of forward and backward row roller and raceway , , adjust
Figure 193401DEST_PATH_IMAGE042
with
Figure 135949DEST_PATH_IMAGE044
size, make
Figure 66560DEST_PATH_IMAGE046
< , record
Figure DEST_PATH_IMAGE050
=
Figure 87310DEST_PATH_IMAGE042
/
Figure 263076DEST_PATH_IMAGE044
in
Figure 939039DEST_PATH_IMAGE050
value;
D-4. get =(
Figure 973467DEST_PATH_IMAGE040
+
Figure 34964DEST_PATH_IMAGE052
)/2, according to
Figure 897745DEST_PATH_IMAGE052
= /
Figure DEST_PATH_IMAGE056
, calculate
Figure 123321DEST_PATH_IMAGE054
with
Figure 213637DEST_PATH_IMAGE056
value, according to the computational methods in steps d-1, calculate the contact stress of forward and backward row roller and raceway
Figure DEST_PATH_IMAGE058
,
Figure DEST_PATH_IMAGE060
; If
Figure 83635DEST_PATH_IMAGE058
< , get
Figure DEST_PATH_IMAGE062
=(
Figure 107884DEST_PATH_IMAGE040
+
Figure 673995DEST_PATH_IMAGE052
)/2; If
Figure 788712DEST_PATH_IMAGE058
>
Figure 149286DEST_PATH_IMAGE060
, get
Figure 598722DEST_PATH_IMAGE062
=(
Figure 968524DEST_PATH_IMAGE050
+
Figure 734486DEST_PATH_IMAGE052
), the like;
D-5. in steps d-4, scaling factor
Figure DEST_PATH_IMAGE064
=
Figure DEST_PATH_IMAGE066
/
Figure DEST_PATH_IMAGE068
time, calculate corresponding contact stress and whether meet |
Figure DEST_PATH_IMAGE070
- | < 3 / 100 and |
Figure 831721DEST_PATH_IMAGE070
- | < 3
Figure 78212DEST_PATH_IMAGE072
/ 100, record satisfies condition
Figure 859217DEST_PATH_IMAGE064
value, according to
Figure 955349DEST_PATH_IMAGE066
with
Figure 729270DEST_PATH_IMAGE068
value is determined bearing roller size, designs satisfactory bearing.
2. the design method of wind driven generator principal shaft selfaligning roller bearing according to claim 1, is characterized in that: in steps d-1, the calculating of contact stress employing is finite element algorithm.
CN201210102961.4A 2012-04-10 2012-04-10 Self-aligning roller bearing for main shaft of wind turbine generator and design method thereof Active CN102619875B (en)

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CN101331334A (en) * 2005-12-16 2008-12-24 Ntn株式会社 Roller bearing, main shaft support structure for wind-driven generator, pad and retainer segment
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