Wind power gear box uniform load design control method

Abstract

The invention discloses a wind power gear box uniform load design control method, which specifically comprises the following steps: S1, according to design requirements, preliminarily taking a maximum uniform load coefficient K [gamma] max; s2, the gear machining precision grade is determined according to the theoretical maximum value K gamma max of the uniform load coefficient and the distribution number of the planetary gear pair; s3, according to the machining precision grade of each gear piece, the square and the floating amount of floating of the sun gear are calculated; s4, whether the value of the square and the floating amount of floating of the sun gear meets the first design requirement or not is judged, and if not, the step S5 is executed; if yes, entering S6; s5, adjusting the square sum and the floating amount of the sun gear; s6, calculating a load non-uniform coefficient K epsilon of the planetary gear pair; s7, judging whether the load non-uniform coefficient K epsilon of the planetary gear pair meets a second design requirement or not; if yes, entering S10; if not, entering S8 or S9; s8, the gear machining precision grade is adjusted; and S9, the square and the floating amount of the sun gear are adjusted again.

Description

Technical Field

[0001] The present invention relates to the technical field of gear boxes, and in particular to a load-sharing design control method for a wind power gear box. Background Art

[0002] With the vigorous development of wind power industry, wind turbines are widely operated in various types of wind farms. As the core component of wind turbines, wind turbine gearboxes are subjected to complex loads, resulting in a high failure rate.

[0003] At present, wind power gearboxes generally use multi-stage planetary gear transmission or multi-stage planetary plus parallel gear transmission. The errors caused during the manufacturing and assembly process will lead to uneven load on the planetary gears, which has a great impact on the life of the gearbox. Therefore, good load balancing can significantly improve the operating performance of the wind power gearbox, and different working conditions have a significant impact on the load balancing performance of the planetary level of the gearbox.

[0004] As wind turbine gearboxes gradually enter the era of large megawatts, the design process of wind turbine gearboxes basically adopts the "multi-stage planetary gear transmission" or "planetary gear + parallel gear transmission" method, and the planetary gear transmission system basically adopts the floating sun gear method to control its load-sharing performance. However, there is a lack of design ideas for load-sharing control of multi-divided planetary gears in planetary transmission gear pairs, resulting in a high failure rate of wind turbine gearboxes. Summary of the invention

[0005] In view of the technical problem that the failure rate of wind power gearboxes in the prior art is relatively high, the present invention provides a load balancing design control method for wind power gearboxes.

[0006] In order to achieve the above object, the present invention provides the following technical solutions:

[0007] A wind turbine gearbox load balancing design control method specifically comprises the following steps:

[0008] S1: According to the design requirements, a maximum load factor K that meets the design requirements of a certain level of planetary gear transmission of a wind turbine gearbox is preliminarily determined. γmax ;

[0009] S2: Based on the theoretical maximum value K of the load-balancing factor determined initially γmax And the number of splitters of the planetary gear pair, preliminarily determine the gear processing accuracy level;

[0010] S3: Calculate the square and floating amount of the sun gear according to the machining accuracy level of each gear component determined in S2;

[0011] S4: Determine whether the square sum of the floating amount of the sun gear meets the first design requirement. If not, proceed to S5; if satisfied, proceed to S6.

[0012] S5: Adjust the size of the square and floating amount of the sun gear until the design requirements are met;

[0013] S6: Calculate the uneven load coefficient K of the planetary gear pair ε ;

[0014] S7: Determine the uneven load coefficient K of the planetary gear pair ε Whether the second design requirement is met; if the second design requirement is met, proceed to S10; if the second design requirement is not met, proceed to S8 or S9;

[0015] S8: Adjust the gear processing accuracy level;

[0016] S9: Adjust the size of the square and floating amount of the sun gear again;

[0017] S10: Based on the machining accuracy and eccentricity error of each gear component obtained from the above design process, a three-dimensional model of the planetary gear pair of the wind turbine gearbox of this model is established, and a finite element analysis is performed;

[0018] S11: judging whether the finite element analysis result meets the third design requirement. If so, entering S12 to complete the wind power gearbox planetary gear pair load sharing control design process; if not, returning to S8 or S9 to readjust the machining accuracy of the gear part or the floating amount of the sun gear;

[0019] S12: Output the determined machining accuracy level of each gear component, the floating square and floating amount of the sun gear, and complete the load-sharing control design process of the planetary gear pair.

[0020] Preferably, S2 includes:

[0021] S2-1: In the wind turbine gearbox, the sun gear is floated to achieve the load balancing of the planetary gear pair. The calculation formula of the load balancing coefficient of the planetary gear is as follows:

[0022]

[0023] In formula (1), K γ represents the load-sharing factor of the planetary gear; F1 represents the tooth surface load between the planetary gear and the sun gear; T a Indicates the torque on the sun gear; n p Indicates the number of planetary gears; r bs Indicates the base circle radius of the sun gear;

[0024] S2-2: According to the theoretical maximum value of the load-balancing factor K γmax And the split number of the planetary gear pair, calculate the maximum tooth surface load F between the planetary gear and the sun gear 1max :

[0025]

[0026] In formula (2), F 1max It represents the maximum tooth surface load between the planetary gear and the sun gear; y1 represents the split number of the three-stage planetary gear pair of the gearbox;

[0027] S2-3: Based on the maximum load factor K γmax and maximum tooth surface load F 1max , the comprehensive meshing error between the sun gear and the planetary gear, and between the planetary gear and the inner gear ring can be obtained:

[0028]

[0029] In formula (3), K sp Represents the equivalent gear meshing stiffness between the sun gear and the planetary gear; r bs Indicates the base circle radius of the sun gear; θ s represents the rotation angle of the sun gear caused by elastic deformation; r bpi Indicates the radius of the planetary gear base circle; θ pi represents the rotation angle of the i-th planetary gear caused by elastic deformation; Δ spi Indicates the comprehensive meshing error between the floating sun gear and a single planet gear; F piI represents the tooth surface load between the i-th planetary gear and the inner ring gear; K pl Represents the equivalent gear meshing stiffness between the inner ring gear and the planetary gear; Δ piI Indicates the comprehensive meshing error between the inner gear ring and a single planetary gear;

[0030] S2-4: Based on the comprehensive meshing error, combined with the actual production cost and the actual machinable accuracy, within the maximum comprehensive meshing error range, preliminarily allocate the machining accuracy of the sun gear, planetary gear, and inner ring gear in the planetary gear system to determine the machining accuracy level of each gear component.

[0031] Preferably, the method for determining the machining accuracy level is:

[0032] The comprehensive meshing error between the floating sun gear and a single planet gear Δ spi =e spi +Δ si , the comprehensive meshing error between the inner ring gear and a single planetary gear Δ piI =e piI :

[0033]

[0034] In formula (4), the equivalent meshing error eE caused by the sun gear machining error on the internal meshing action line is si, the equivalent meshing error eE caused by the i-th planetary gear machining error pIi , the equivalent meshing error eE caused by the planet carrier processing error cIi , the equivalent meshing error eE caused by the machining error of the inner gear ring on the external meshing action line Ii , the equivalent meshing error eE caused by the i-th planetary gear machining error pIi , the equivalent meshing error eE caused by the planet carrier processing error c2i , the inner and outer meshing tooth thickness errors are expressed as ε1 and ε2 respectively;

[0035] According to formula (4), we first determine that the machining accuracy of the sun gear, planetary gear and inner ring gear is level 6. If the calculated comprehensive meshing error exceeds the allowable range, the accuracy of the sun gear and planetary gear is increased to level 5.

[0036] Preferably, S3 includes:

[0037] S3-1: The actual eccentricity error of the part size can be determined by calculating according to the machining accuracy level of each gear part determined in S2 and the established formula in the mechanical design manual;

[0038] S3-2: Considering the influence of installation errors such as bearing clearance, calculate the tangential displacement e of the planetary gear shaft hole on the planetary carrier according to the mechanical design manual. T , planetary gear eccentricity error e c , sun gear eccentricity error e a , eccentricity error of inner gear ring e b , planet carrier eccentricity error e H ;

[0039] S3-3: Then calculate the floating amount required by the part size limit deviation:

[0040]

[0041] In formula (5), α' represents the meshing angle of the planetary gear transmission, E zT Indicates the required floating value of the tangential displacement of the center of the planetary gear shaft hole on the planet carrier; E za 、E zc 、E zb 、E zH Respectively represent the required values ​​of floating amount for the eccentricity errors of the sun gear, planetary gear, inner ring gear and planet carrier;

[0042] S3-4: Finally, calculate the square and floating amount of the sun gear:

[0043]

[0044] In formula (6), E zIndicates the square and amount of sun gear floating.

[0045] Preferably, in S5, the method for adjusting the size of the square sum of the floating amount of the sun gear is:

[0046] If the design stipulates that the maximum value of the square and floating amount of the sun gear is 2, if the calculated result is 2.1, then adjust the calculated value to 1.9, and then reversely calculate the eccentricity error and equivalent meshing error of each component, adjust the processing accuracy level of each component, and then calculate the value of the square and floating amount of the sun gear based on the adjusted processing accuracy, and compare it with the specified value; repeat the iterative operation.

[0047] Preferably, in S6, the calculation formula of the load unevenness coefficient of the planetary gear pair is:

[0048]

[0049] In formula (7), K ε Indicates the uneven load coefficient of the planetary gear pair; P max represents the maximum power transmitted by the planetary gear transmission; P represents the power transmitted by the planetary gear transmission; P' represents the average power transmitted by the planetary gear transmission; n w Indicates the number of planetary gears; T max It represents the maximum torque transmitted by the star gear transmission; T represents the torque transmitted by the planetary gear transmission; T' represents the average torque transmitted by the planetary gear.

[0050] Preferably, in S8, the method for adjusting the gear machining accuracy level is:

[0051] If the sum of the square of the floating amount of the sun gear is less than the first design requirement, the machining accuracy of the gear part is reduced; if the sum of the square of the floating amount of the sun gear is greater than the first design requirement, the machining accuracy of the gear part is improved.

[0052] Preferably, in S10, the finite element analysis method is:

[0053] According to the processing accuracy and eccentricity error of each gear part, a three-dimensional model of the planetary gear pair of this type of wind turbine gearbox was established using three-dimensional modeling software, and the assembly was imported into ANSYS software to set the boundary conditions for static and dynamic simulation analysis and calculation. The modeling was carried out using MASTA software, and the boundary conditions, assembly relationships, and processing accuracy of each gear part were added for finite element analysis.

[0054] Preferably, in S11, the third design requirement includes whether the contact surface cloud diagram of each gear part is uniformly stressed, whether the stress on each component exceeds the allowable stress of the material, and whether the fatigue damage of the workpiece during its service life exceeds the design specification.

[0055] In summary, due to the adoption of the above technical solution, compared with the prior art, the present invention has at least the following beneficial effects:

[0056] 1. Traditional wind turbine gearbox load-sharing control is mainly based on the "design-production-test" method. First, based on experience and relevant technical specifications, the processing accuracy of each gear part of the planetary gear system and the floating amount of the sun gear are designed, and then the product is produced. Finally, the load-sharing performance of the planetary gear system is tested to determine whether it meets the design requirements.

[0057] The load-sharing control design method proposed in the present invention first gives a theoretical maximum value of the load-sharing coefficient under the condition of meeting the design requirements. Within this value range, the machining accuracy of the gear parts is allocated, and the floating amount of the sun gear and the value of the load unevenness coefficient are calculated, which are used as the evaluation criteria to adjust the machining accuracy of the gear parts. In the present invention, the machining accuracy of each gear part of the planetary gear system is repeatedly iteratively adjusted, calculated and verified during the design process, so that the obtained results are more reliable.

[0058] 2. In the design process, the present invention omits the "production-testing" link, greatly saves design costs, and effectively shortens the design cycle. BRIEF DESCRIPTION OF THE DRAWINGS

[0059] Figure 1 Schematic diagram of a wind turbine gearbox load balancing design control method according to an exemplary embodiment of the present invention. DETAILED DESCRIPTION

[0060] The present invention is further described in detail below in conjunction with the examples and specific implementation methods. However, this should not be understood as the scope of the above subject matter of the present invention being limited to the following examples, and all technologies realized based on the content of the present invention belong to the scope of the present invention.

[0061] In the description of the present invention, it is necessary to understand that the terms "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating the orientation or position relationship, are based on the orientation or position relationship shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0062] like Figure 1 As shown, the present invention provides a wind power gearbox load balancing design control method, comprising the following steps:

[0063] S1: According to the design requirements, a theoretical maximum value K of the load-sharing coefficient that meets the design requirements of a certain stage of planetary gear transmission of a wind turbine gearbox is preliminarily determined.γmax , to measure the load-sharing performance requirements of the planetary gear transmission.

[0064] S2: Based on the theoretical maximum value K of the load-balancing factor determined initially γmax As well as the number of splitters of the planetary gear pair, reasonably allocate the gear processing accuracy, and preliminarily determine the gear processing accuracy level. The details are as follows:

[0065] S2-1: In wind turbine gearboxes, the floating sun gear is generally used to achieve load balancing of the planetary gear pair. At this time, the calculation formula for the load balancing coefficient of any planetary gear is as follows:

[0066]

[0067] In formula (1), K γ represents the load-sharing factor of the planetary gear; F1 represents the tooth surface load between the planetary gear and the sun gear; T a Indicates the torque on the sun gear; n p Indicates the number of planetary gears; r bs Indicates the sun gear base circle radius.

[0068] S2-2: According to the theoretical maximum value of the load-balancing factor K γmax And the split number of the planetary gear pair, calculate the maximum tooth surface load F between any planetary gear and the sun gear 1max :

[0069]

[0070] In formula (2), F 1max It represents the maximum tooth surface load between the planetary gear and the sun gear; y1 represents the flow distribution number of the three-stage planetary gear pair of the gearbox.

[0071] S2-3: Based on the maximum load factor K γmax and maximum tooth surface load F 1max , the comprehensive meshing error between the sun gear and the planetary gear, and between the planetary gear and the inner gear ring can be obtained:

[0072]

[0073] In formula (3), K sp Represents the equivalent gear meshing stiffness between the sun gear and the planetary gear; r bs Indicates the base circle radius of the sun gear; θ s represents the rotation angle of the sun gear caused by elastic deformation; r bpi Indicates the radius of the planetary gear base circle; θ pi represents the rotation angle of the i-th planetary gear caused by elastic deformation; Δ spi Indicates the comprehensive meshing error between the floating sun gear and a single planet gear; F piIrepresents the tooth surface load between the i-th planetary gear and the inner ring gear; K pl Represents the equivalent gear meshing stiffness between the inner ring gear and the planetary gear; Δ piI Represents the comprehensive meshing error between the inner ring gear and a single planetary gear.

[0074] S2-4: Based on the comprehensive meshing error, and taking into account the actual production cost and the actual machinable accuracy, within the maximum comprehensive meshing error range, preliminarily allocate the machining accuracy of the sun gear, planetary gear, and inner ring gear in the planetary gear system, and determine the machining accuracy level of each gear component.

[0075] In this embodiment, the comprehensive meshing error Δ between the floating sun gear and a single planet gear is spi =e spi +Δ si , the comprehensive meshing error between the inner ring gear and a single planetary gear Δ piI =e piI .

[0076] According to the following formula:

[0077]

[0078] In formula (4), the equivalent meshing error eE caused by the sun gear machining error on the internal meshing action line is si , the equivalent meshing error eE caused by the i-th planetary gear machining error pIi , the equivalent meshing error eE caused by the planet carrier processing error cIi , the equivalent meshing error eE caused by the machining error of the inner gear ring on the external meshing action line Ii , the equivalent meshing error eE caused by the i-th planetary gear machining error pIi , the equivalent meshing error eE caused by the planet carrier processing error c2i The internal and external meshing tooth thickness errors are expressed as ε1 and ε2 respectively.

[0079] According to the above relationship (4), combined with the processing cost and processing difficulty, the processing accuracy of each gear part is selected. For example, first randomly determine that the processing accuracy of the sun gear, planetary gear and inner ring gear is level 6. If the calculated comprehensive meshing error result exceeds the allowable range, the accuracy of the sun gear and planetary gear is improved to level 5. Since the processing difficulty and cost of the inner ring gear are high, the processing accuracy of the other two gear parts is improved first.

[0080] S3: According to the machining accuracy level of each gear part determined in S2, consult the mechanical design manual and calculate it through the established formula in the mechanical design manual to determine the actual eccentricity error of the part size; then comprehensively consider the influence of installation errors such as bearing clearance, and calculate the tangential displacement e of the planetary gear shaft hole on the planet carrier according to the mechanical design manual. T , planetary gear eccentricity error ec , sun gear eccentricity error e a , eccentricity error of inner gear ring e b , planet carrier eccentricity error e H , and then calculate the floating amount required by the part size limit deviation:

[0081]

[0082] In formula (5), e T Indicates the tangential displacement of the planetary gear shaft hole on the planet carrier; e a Indicates the eccentricity error of the sun gear; e c Indicates the eccentricity error of the planetary gear; e b Indicates the eccentricity error of the inner gear ring; e H represents the eccentricity error of the planet carrier; α' represents the meshing angle of the planetary gear transmission, E zT Indicates the required floating value of the tangential displacement of the center of the planetary gear shaft hole on the planet carrier; E za 、E zc 、E zb 、E zH Respectively represent the required values ​​of floating amount for the eccentricity errors of the sun gear, planetary gear, inner ring gear and planet carrier;

[0083] Finally, calculate the square and floating amount of the sun gear:

[0084]

[0085] In formula (6), E z Indicates the square and amount of sun gear floating.

[0086] S4: Determine whether the square and floating values ​​of the sun gear meet the design requirements, in order to verify whether the design and structure of the load-balancing mechanism are reasonable; if not, enter S5; if satisfied, enter S6.

[0087] S5: Adjust the size of the sun gear square and floating amount within a certain range until the design requirements are met.

[0088] For example: the design stipulates that the maximum value of the square and floating amount of the sun gear is 2. If the calculated result is 2.1, the calculated value is adjusted to 1.9, and then the eccentricity error and equivalent meshing error of each component are calculated, and the processing accuracy level of each component is adjusted. Then, based on the adjusted processing accuracy, the square and floating value of the sun gear are calculated and compared with the specified value; the iterative operation is repeated back and forth.

[0089] S6: According to the mechanical design manual, calculate the actual value K of the load unevenness coefficient of the planetary gear pair at this level ε , the calculation formula is as follows:

[0090]

[0091] In formula (7), K ε Indicates the uneven load coefficient of the planetary gear pair; P max represents the maximum power transmitted by the planetary gear transmission; P represents the power transmitted by the planetary gear transmission; P' represents the average power transmitted by the planetary gear transmission; n w Indicates the number of planetary gears; T max It represents the maximum torque transmitted by the star gear transmission; T represents the torque transmitted by the planetary gear transmission; T' represents the average torque transmitted by the planetary gear.

[0092] S7: Determine the obtained planetary gear pair load unevenness coefficient K ε Is it within the range of the sun gear floating load unevenness coefficient specified in the mechanical design manual? If it meets the design requirements, go to S10; if it does not meet the design requirements, go to S8 or S9.

[0093] S8: Considering the actual gear processing accuracy that can be achieved, adjust the gear processing accuracy level. If the square and floating amount of the sun gear float are less than the first design requirement, in order to reduce the processing cost and shorten the processing cycle, the gear processing accuracy can be appropriately reduced; if the square and floating amount of the sun gear float are greater than the first design requirement, then improve the gear processing accuracy and then go to S3.

[0094] S9: Reduce the size of the square sum of the sun gear and the floating amount again, for example, reduce the value of the square sum of the sun gear and the floating amount adjusted in S5 from 1.9 to 1.8 again, and then go to S4.

[0095] S10: Based on the design parameters such as machining accuracy and eccentricity error of each gear part obtained from the above design process, the three-dimensional model of the planetary gear pair of the wind power gearbox of this model is established by using modeling software such as UG NX and solid works, and the assembly is imported into ANSYS software to set boundary conditions and other settings for static and dynamic simulation analysis and calculation. The modeling is carried out by MASTA software, and the boundary conditions, assembly relations and machining accuracy of each gear part are added for solution calculation. That is, finite element analysis is carried out to verify whether the design results meet the requirements.

[0096] S11: Determine whether the finite element analysis results meet the design requirements, that is, check whether the contact surface cloud diagrams of each gear part in the calculation results are uniformly stressed, whether the stress of each component exceeds the allowable stress of the material, whether the fatigue damage of the workpiece during the service life exceeds the design specifications, etc. If it meets the design requirements, enter S12 to complete the wind power gearbox planetary gear pair load control design process; if it does not meet the design requirements, return to S8 or S9 to re-adjust the parameters such as the machining accuracy of the gear parts or the floating amount of the sun gear.

[0097] S12: Output the calculation results of the determined machining accuracy level of each gear component, the floating square and floating amount of the sun gear, and complete the load-sharing control design process of the planetary gear pair.

[0098] Those skilled in the art will appreciate that the above-mentioned embodiments are specific examples for implementing the present invention, and in actual applications, various changes may be made thereto in form and detail without departing from the spirit and scope of the present invention.

Claims

1. A wind turbine gearbox load-sharing design control method, It is characterized in that The specific steps include: S1: According to the design requirements, a maximum load factor K that meets the design requirements of a certain level of planetary gear transmission of a wind turbine gearbox is preliminarily determined. γmax ; S2: Based on the theoretical maximum value K of the load-balancing factor determined initially γmax And the number of splitters of the planetary gear pair, preliminarily determine the gear processing accuracy level; S3: Calculate the square and floating amount of the sun gear according to the machining accuracy level of each gear component determined in S2; S4: Determine whether the square sum of the floating amount of the sun gear meets the first design requirement. If not, proceed to S5; if satisfied, proceed to S6. S5: Adjust the size of the square and floating amount of the sun gear until the design requirements are met; S6: Calculate the uneven load coefficient K of the planetary gear pair ε ; S7: Determine the uneven load coefficient K of the planetary gear pair ε Whether the second design requirement is met; if the second design requirement is met, proceed to S10; if the second design requirement is not met, proceed to S8 or S9; S8: Adjust the gear processing accuracy level; S9: Adjust the size of the square and floating amount of the sun gear again; S10: Based on the machining accuracy and eccentricity error of each gear component obtained from the above design process, a three-dimensional model of the planetary gear pair of the wind turbine gearbox of this model is established, and a finite element analysis is performed; S11: judging whether the finite element analysis result meets the third design requirement. If so, entering S12 to complete the wind power gearbox planetary gear pair load sharing control design process; if not, returning to S8 or S9 to readjust the machining accuracy of the gear part or the floating amount of the sun gear; S12: Output the determined machining accuracy level of each gear component, the floating square and floating amount of the sun gear, and complete the load-sharing control design process of the planetary gear pair.

2. A wind turbine gearbox load balancing design control method as claimed in claim 1, It is characterized in that The S2 includes: S2-1: In the wind turbine gearbox, the sun gear is floated to achieve the load balancing of the planetary gear pair. The calculation formula of the load balancing coefficient of the planetary gear is as follows: In formula (1), K γ Indicates the planetary gear load factor; F 1 Indicates the tooth surface load between the planetary gear and the sun gear; T a Indicates the torque on the sun gear; n p Indicates the number of planetary gears; r bs Indicates the base circle radius of the sun gear; S2-2: According to the theoretical maximum value of the load-balancing factor K γmax And the split number of the planetary gear pair, calculate the maximum tooth surface load F between the planetary gear and the sun gear 1max : In formula (2), F 1max Indicates the maximum tooth surface load between the planetary gear and the sun gear; y 1 Indicates the split number of the three-stage planetary gear pair of the gearbox; S2-3: Based on the maximum load factor K γmax and maximum tooth surface load F 1max , the comprehensive meshing error between the sun gear and the planetary gear, and between the planetary gear and the inner gear ring can be obtained: In formula (3), K sp Represents the equivalent gear meshing stiffness between the sun gear and the planetary gear; r bs Indicates the base circle radius of the sun gear; θ s represents the rotation angle of the sun gear caused by elastic deformation; r bpi Indicates the radius of the planetary gear base circle; θ pi represents the rotation angle of the i-th planetary gear caused by elastic deformation; Δ spi Indicates the comprehensive meshing error between the floating sun gear and a single planet gear; F piI represents the tooth surface load between the i-th planetary gear and the inner ring gear; K pl Represents the equivalent gear meshing stiffness between the inner ring gear and the planetary gear; Δ piI Indicates the comprehensive meshing error between the inner gear ring and a single planetary gear; S2-4: Based on the comprehensive meshing error, combined with the actual production cost and the actual machinable accuracy, within the maximum comprehensive meshing error range, preliminarily allocate the machining accuracy of the sun gear, planetary gear, and inner ring gear in the planetary gear system to determine the machining accuracy level of each gear component.

3. A wind turbine gearbox load balancing design control method as claimed in claim 2, It is characterized in that The method for determining the machining accuracy level is: The comprehensive meshing error between the floating sun gear and a single planet gear Δ spi =e spi +Δ si , the comprehensive meshing error between the inner ring gear and a single planetary gear Δ piI =e piI : In formula (4), the equivalent meshing error eE caused by the sun gear machining error on the internal meshing action line is si , the equivalent meshing error eE caused by the i-th planetary gear machining error pIi , the equivalent meshing error eE caused by the planet carrier processing error cIi , the equivalent meshing error eE caused by the machining error of the inner gear ring on the external meshing action line Ii , the equivalent meshing error eE caused by the i-th planetary gear machining error pIi , the equivalent meshing error eE caused by the planet carrier processing error c2i , the inner and outer meshing tooth thickness errors are expressed as ε 1 , ε 2 ; According to formula (4), we first determine that the machining accuracy of the sun gear, planetary gear and inner ring gear is level 6. If the calculated comprehensive meshing error exceeds the allowable range, the accuracy of the sun gear and planetary gear is increased to level 5.

4. A wind turbine gearbox load balancing design control method as claimed in claim 1, It is characterized in that The S3 includes: S3-1: The actual eccentricity error of the part size can be determined by calculating according to the machining accuracy level of each gear part determined in S2 and the established formula in the mechanical design manual; S3-2: Considering the influence of installation errors such as bearing clearance, calculate the tangential displacement e of the planetary gear shaft hole on the planetary carrier according to the mechanical design manual. T , planetary gear eccentricity error e c , sun gear eccentricity error e a , eccentricity error of inner gear ring e b , planet carrier eccentricity error e H ; S3-3: Then calculate the floating amount required by the part size limit deviation: In formula (5), α' represents the meshing angle of the planetary gear transmission, E zT Indicates the required floating value of the tangential displacement of the center of the planetary gear shaft hole on the planet carrier; E za 、E zc 、E zb 、E zH Respectively represent the required values ​​of floating amount for the eccentricity errors of the sun gear, planetary gear, inner ring gear and planet carrier; S3-4: Finally, calculate the square and floating amount of the sun gear: In formula (6), E z Indicates the square and amount of sun gear floating.

5. A wind turbine gearbox load balancing design control method as claimed in claim 1, It is characterized in that In S5, the method for adjusting the size of the square and floating amount of the sun gear is: If the design stipulates that the maximum value of the square and floating amount of the sun gear is 2, if the calculated result is 2.1, then adjust the calculated value to 1.9, and then reversely calculate the eccentricity error and equivalent meshing error of each component, adjust the processing accuracy level of each component, and then calculate the value of the square and floating amount of the sun gear based on the adjusted processing accuracy, and compare it with the specified value; repeat the iterative operation.

6. A wind turbine gearbox load balancing design control method as claimed in claim 1, It is characterized in that In S6, the calculation formula of the load unevenness coefficient of the planetary gear pair is: In formula (7), K ε Indicates the uneven load coefficient of the planetary gear pair; P max Indicates the maximum power transmitted by the planetary gear transmission; P indicates the power transmitted by the planetary gear transmission; P , Indicates the average power transmitted by the planetary gear transmission; n w Indicates the number of planetary gears; T max represents the maximum torque transmitted by the planetary gear transmission; T represents the torque transmitted by the planetary gear transmission; T , Represents the average torque transmitted by the planetary gear.

7. A wind turbine gearbox load balancing design control method as claimed in claim 1, It is characterized in that In S8, the method for adjusting the gear machining accuracy level is: If the sum of the square of the floating amount of the sun gear is less than the first design requirement, the machining accuracy of the gear part is reduced; if the sum of the square of the floating amount of the sun gear is greater than the first design requirement, the machining accuracy of the gear part is improved.

8. A wind turbine gearbox load balancing design control method as claimed in claim 1, It is characterized in that In S10, the finite element analysis method is: According to the processing accuracy and eccentricity error of each gear part, a three-dimensional model of the planetary gear pair of this type of wind turbine gearbox was established using three-dimensional modeling software, and the assembly was imported into ANSYS software to set the boundary conditions for static and dynamic simulation analysis and calculation. The modeling was carried out using MASTA software, and the boundary conditions, assembly relationships, and processing accuracy of each gear part were added for finite element analysis.

9. A wind turbine gearbox load balancing design control method as claimed in claim 1, It is characterized in that In S11, the third design requirement includes whether the contact surface cloud diagram of each gear part is uniformly stressed, whether the stress of each component exceeds the allowable stress of the material, and whether the fatigue damage of the workpiece during its service life exceeds the design specification.

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