Doubly-fed wind power main gear box and five-stage transmission structure thereof

By adopting the five-stage transmission structure and planetary mechanism design in the wind power main gearbox, the problem of difficult to increase torque density and high manufacturing costs in the existing technology is solved, the torque density is improved and the cost is reduced, and the market competitiveness is improved .

CN222363359UActive Publication Date: 2025-01-17GUANGDONG MINGYANG WIND POWER IND GRP CO LTD
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Patent Information

Application Number
CN202421036276.0
Authority / Receiving Office
CN · China
Patent Type
Utility models(China)
Current Assignee / Owner
Filing Date
2024-05-14
Publication Date
2025-01-17
Estimated Expiration
2034-05-14

AI Technical Summary

Technical Problem

The structural layout of the existing double-feed wind power main gear box leads to difficult to improve torque density, high manufacturing cost, weak market competitiveness, and difficult processing technology, with few gear teeth, large modulus, large teeth width, large ring diameter, and high speed. It is difficult to reduce weight than the limit.

Method used

Adopt a five-stage transmission structure, including first-stage to fifth-stage planetary mechanisms and parallel shaft cylindrical gear transmission, connects planetary mechanisms at all levels through splines to enhance power transmission efficiency, reduce the diameter and tooth width of the ring gear, and increase the number of planetary wheels and Speed ​​ratio reduces processing difficulty.

Benefits of technology

The torque density has been increased to 240-250kNm/t, which reduces manufacturing costs, reduces gearbox weight, reduces processing technology difficulty, and improves market competitiveness.

✦ Generated by Eureka AI based on patent content.

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Abstract

The utility model discloses a doubly-fed wind power main gearbox and a five-stage transmission structure thereof. The five-stage transmission structure comprises a first-stage planetary mechanism, a second-stage planetary mechanism, a third-stage planetary mechanism, a fourth-stage planetary mechanism, a five-stage driving wheel and an output shaft which are sequentially connected. A first-stage sun gear of the first-stage planetary mechanism is connected with a second-stage planet carrier of the second-stage planetary mechanism through a spline, a second-stage sun gear of the second-stage planetary mechanism is connected with a third-stage planet carrier of the third-stage planetary mechanism through a spline, and a third-stage sun gear of the third-stage planetary mechanism is connected with a fourth-stage planet carrier of the fourth-stage planetary mechanism through a spline. A fourth-stage sun wheel of the fourth-stage planetary mechanism is connected with a fifth-stage driving wheel through a spline, and the fifth-stage driving wheel is meshed with an output shaft gear on an output shaft to form parallel shaft cylindrical gear transmission. According to the utility model, the torque density can be greatly improved, and the manufacturing cost is reduced.
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Description

Technical Field

[0001] The utility model relates to the technical field of wind power generation, in particular to a double-fed wind power main gear box and a five-stage transmission structure thereof. Background Art

[0002] In a wind turbine, the main gearbox is a very important component in the transmission system of the unit, which plays a role in transmitting power, increasing speed and reducing torque. Due to fierce market competition, the market price of wind turbines has been declining year by year, reaching a dilemma of no profit or even loss. As the main component of the unit, the main gearbox of the wind turbine occupies a high proportion of the cost. Reducing the weight of the main gearbox of the wind turbine, increasing the torque density and reducing the manufacturing cost are the primary conditions for winning the market opportunity. However, under the premise of ensuring product reliability, reducing the weight of the main gearbox of the wind turbine is a difficult point in design.

[0003] At present, in the industry, for the doubly fed wind turbine main gearbox, a two-stage planetary plus one-stage parallel shaft or a three-stage planetary plus one-stage parallel shaft structural layout is usually adopted. The disadvantages of this gearbox structural layout are:

[0004] 1. The speed ratio of each level is very large, and some have reached the maximum speed ratio.

[0005] 2. The primary gear ring has a large diameter and a very wide tooth width.

[0006] 3. The gear has few teeth, large module, large tooth width, and difficult processing technology.

[0007] 4. The torque density is usually around 220kNm / t, and it is difficult to further increase the torque density.

[0008] 5. The manufacturing cost is high and the market competitiveness of the units is weak. Utility Model Content

[0009] The first purpose of the utility model is to overcome the shortcomings and deficiencies of the prior art and provide a five-stage transmission structure of a doubly-fed wind turbine main gearbox, which can greatly improve the torque density and reduce the manufacturing cost.

[0010] The second objective of the utility model is to provide a doubly-fed wind turbine main gearbox.

[0011] The first object of the utility model is achieved through the following technical solutions: a five-stage transmission structure of a doubly-fed wind power main gearbox, the five-stage transmission structure comprising a first-stage planetary mechanism, a second-stage planetary mechanism, a third-stage planetary mechanism, a fourth-stage planetary mechanism, a fifth-stage driving wheel and an output shaft connected in sequence; wherein the first-stage planetary carrier of the first-stage planetary mechanism serves as an input shaft for receiving power input, and its first-stage sun gear is connected to the second-stage planetary carrier of the second-stage planetary mechanism through a spline, and the power after the first-stage planetary mechanism speeds up is transmitted to the second-stage planetary mechanism, and the second-stage sun gear of the second-stage planetary mechanism is connected to the second-stage planetary mechanism through a spline. The three-stage planetary frame of the three-stage planetary mechanism is connected to transmit the power after the speed increase of the two-stage planetary mechanism to the three-stage planetary mechanism; the three-stage sun gear of the three-stage planetary mechanism is connected to the four-stage planetary frame of the four-stage planetary mechanism through a spline to transmit the power after the speed increase of the three-stage planetary mechanism to the four-stage planetary mechanism; the four-stage sun gear of the four-stage planetary mechanism is connected to the five-stage driving wheel through a spline to transmit the power after the speed increase of the four-stage planetary mechanism to the five-stage driving wheel; the five-stage driving wheel serves as a parallel stage transmission and meshes with the output shaft gear on the output shaft to form a parallel shaft cylindrical gear transmission.

[0012] Specifically, the first-stage planetary mechanism includes a first-stage planet carrier, a first-stage sun gear, a first-stage planet gear and a first-stage ring gear, wherein the first-stage planet gear is mounted on the first-stage planet carrier through a pin shaft and is located in the first-stage ring gear, and is respectively meshed with the first-stage ring gear and the first-stage sun gear.

[0013] Specifically, the number of the first-stage planetary gears is 10-12.

[0014] Specifically, the diameter of the primary gear ring is 2900-3000 mm, and the tooth width is 500-600 mm.

[0015] Specifically, the secondary planetary mechanism includes a secondary planetary carrier, a secondary sun gear, a secondary planetary gear and a secondary ring gear, wherein the secondary planetary gear is mounted on the secondary planetary carrier through a pin shaft and is located in the secondary ring gear, respectively meshing with the secondary ring gear and the secondary sun gear.

[0016] Specifically, the number of the secondary planetary gears is 8-10.

[0017] Specifically, the diameter of the secondary gear ring is 2500-2600 mm, and the tooth width is 300-400 mm.

[0018] Specifically, the three-stage planetary mechanism includes a three-stage planetary carrier, a three-stage sun gear, a three-stage planetary gear and a three-stage ring gear, wherein the three-stage planetary gear is installed on the three-stage planetary carrier through a pin shaft and is located in the three-stage ring gear, and is respectively meshed with the three-stage ring gear and the three-stage sun gear.

[0019] Specifically, the number of the three-stage planetary gears is 8-10.

[0020] Specifically, the diameter of the three-stage gear ring is 2000-2150 mm, and the tooth width is 250-280 mm.

[0021] Specifically, the four-stage planetary mechanism includes a four-stage planetary carrier, a four-stage sun gear, a four-stage planetary gear and a four-stage ring gear, wherein the four-stage planetary gear is installed on the four-stage planetary carrier through a pin shaft and is located in the four-stage ring gear, and is respectively meshed with the four-stage ring gear and the four-stage sun gear.

[0022] Specifically, the number of the four-stage planetary gears is 5.

[0023] Specifically, the diameter of the four-stage gear ring is 1800-1900 mm, and the tooth width is 200-300 mm.

[0024] Specifically, the speed ratio of the first-stage planetary mechanism is 2.5-2.7, the speed ratio of the second-stage planetary mechanism is 2.7-2.9, the speed ratio of the third-stage planetary mechanism is 2.7-2.9, the speed ratio of the fourth-stage planetary mechanism is 4-4.3, and the speed ratio of the parallel shaft cylindrical gear transmission is 3.

[0025] Specifically, the total speed ratio of the five-stage transmission structure reaches 260.

[0026] The second purpose of the utility model is achieved through the following technical solution: a doubly-fed wind turbine main gearbox, specifically a 13-16MW wind turbine main gearbox, having the above-mentioned five-stage transmission structure.

[0027] Specifically, the torque density of the 13-16MW wind turbine main gearbox reaches 240-250kNm / t.

[0028] Compared with the prior art, the utility model has the following advantages and beneficial effects:

[0029] 1. The number of planetary gears in the first three stages of the planetary mechanism is 8 to 12, and the speed ratio is small.

[0030] 2. The diameter of the first-stage gear ring is small, and the tooth width is much smaller than that of the planetary mechanism with a large speed ratio.

[0031] 3. Due to the small gear module and tooth width, the processing technology is easy to operate.

[0032] 4. The gearbox is light in weight and the torque density can reach over 240kNm / t.

[0033] 5. Effectively reduce manufacturing costs and improve market competitiveness. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] Figure 1 This is a simplified diagram of the five-stage transmission structure of Example 1.

[0035] Figure 2 It is a cross-sectional view of the five-stage transmission structure of Example 1. DETAILED DESCRIPTION

[0036] The present invention is further described in detail below in conjunction with embodiments and drawings, but the implementation manner of the present invention is not limited thereto.

[0037] Example 1

[0038] See also Figure 1 and Figure 2 As shown, this embodiment discloses a five-stage transmission structure of a doubly-fed wind turbine main gearbox, comprising a first-stage planetary mechanism 1, a second-stage planetary mechanism 2, a third-stage planetary mechanism 3, a fourth-stage planetary mechanism 4, a fifth-stage driving wheel 5 and an output shaft 6 connected in sequence;

[0039] The primary planetary mechanism 1 includes a primary planet carrier 101, a primary sun gear 102, a primary planetary gear 103 and a primary ring gear 104. The primary planetary gear 103 is mounted on the primary planet carrier 101 through a pin shaft and is located in the primary ring gear 104, respectively meshing with the primary ring gear 104 and the primary sun gear 102. The primary planet carrier 101 serves as an input shaft for receiving power input. The number of primary planetary gears 103 is 10, and the speed ratio is about 2.7. The diameter of the primary ring gear 104 is 2900-3000mm, and the tooth width is 500-600mm. The primary sun gear 102 is connected to the secondary planet carrier 201 of the secondary planetary mechanism 2 through a spline, and transmits the power after the primary planetary mechanism 1 is increased in speed to the secondary planetary mechanism 2;

[0040] The secondary planetary mechanism 2 includes a secondary planetary carrier 201, a secondary sun gear 202, a secondary planetary gear 203 and a secondary ring gear 204. The secondary planetary gear 203 is mounted on the secondary planetary carrier 201 through a pin shaft and is located in the secondary ring gear 204, meshing with the secondary ring gear 204 and the secondary sun gear 202 respectively. There are 10 secondary planetary gears 203, and the speed ratio is about 2.7. The diameter of the secondary ring gear 204 is 2500-2600mm, and the tooth width is 300-400mm. The secondary sun gear 202 is connected to the tertiary planetary carrier 301 of the tertiary planetary mechanism 3 through a spline, and transmits the power after the speed increase of the secondary planetary mechanism 2 to the tertiary planetary mechanism 3;

[0041] The three-stage planetary mechanism 3 includes a three-stage planetary carrier 301, a three-stage sun gear 302, a three-stage planetary gear 303 and a three-stage ring gear 304. The three-stage planetary gear 303 is installed on the three-stage planetary carrier 301 through a pin shaft and is located in the three-stage ring gear 304. It is meshed with the three-stage ring gear 304 and the three-stage sun gear 302 respectively. The number of the three-stage planetary gears 303 is 10, and the speed ratio is about 2.7. The diameter of the three-stage ring gear 304 is 2000-2150mm, and the tooth width is 250-280mm. The three-stage sun gear 302 is connected to the four-stage planetary carrier 401 of the four-stage planetary mechanism 4 through a spline, and transmits the power after the speed increase of the three-stage planetary mechanism 3 to the four-stage planetary mechanism 4;

[0042] The four-stage planetary mechanism 4 includes a four-stage planetary carrier 401, a four-stage sun gear 402, a four-stage planetary gear 403 and a four-stage ring gear 404, wherein the four-stage planetary gear 403 is mounted on the four-stage planetary carrier 401 through a pin shaft, and is located in the four-stage ring gear 404, and is respectively meshed with the four-stage ring gear 404 and the four-stage sun gear 402. The number of the four-stage planetary gears 403 is 5, and the speed ratio is about 4. The diameter of the four-stage ring gear 404 is 1800-1900mm, and the tooth width is 200-300mm. The four-stage sun gear 402 is connected to the five-stage driving wheel 5 through a spline, and transmits the power after the speed increase of the four-stage planetary mechanism 4 to the five-stage driving wheel 5;

[0043] The five-stage driving wheel 5 is used as a parallel stage transmission, meshing with the output shaft gear 7 on the output shaft 6 to form a parallel shaft cylindrical gear transmission for speed increase, with a speed ratio of about 3;

[0044] After the above five-stage transmission, the total speed ratio reaches about 260; the power is finally output from the output shaft 6 and transmitted to the generator, and the gearbox completes the functions of power transmission and speed increase.

[0045] Example 2

[0046] Different from Example 1, in this embodiment, the number of the first-stage planetary gears 103 of the first-stage planetary mechanism 1 is 11, and the speed ratio is about 2.6; the number of the third-stage planetary gears 303 of the third-stage planetary mechanism 3 is 9, and the speed ratio is about 2.8.

[0047] Example 3

[0048] Different from Example 1, in this embodiment, the number of first-stage planetary gears 103 of the first-stage planetary mechanism 1 is 12, and the speed ratio is about 2.5, the number of second-stage planetary gears 203 of the second-stage planetary mechanism 2 is 8, and the speed ratio is about 2.9, the number of third-stage planetary gears 303 of the third-stage planetary mechanism 3 is 8, and the speed ratio is about 2.9, and the speed ratio of the fourth-stage planetary mechanism 4 is about 4.3.

[0049] Example 4

[0050] This embodiment discloses a doubly-fed wind turbine main gearbox, specifically a 13-16MW wind turbine main gearbox, which has the five-stage transmission structure described in any one of Embodiments 1 to 3, and the torque density of the gearbox reaches 240-250kNm / t.

[0051] The above embodiments are preferred implementation modes of the present invention, but the implementation modes of the present invention are not limited by the above embodiments. Any other changes, modifications, substitutions, combinations, and simplifications that do not deviate from the spirit and principle of the present invention should be equivalent replacement methods and are included in the protection scope of the present invention.

Claims

1. A five-stage transmission structure of a doubly-fed wind turbine main gearbox, characterized in that: The five-stage transmission structure comprises a first-stage planetary mechanism (1), a second-stage planetary mechanism (2), a third-stage planetary mechanism (3), a fourth-stage planetary mechanism (4), a fifth-stage driving wheel (5) and an output shaft (6) which are connected in sequence; wherein the first-stage planet carrier (101) of the first-stage planetary mechanism (1) serves as an input shaft for receiving power input, and the first-stage sun gear (102) thereof is connected to the second-stage planet carrier (201) of the second-stage planetary mechanism (2) via a spline, so as to transmit the power increased by the first-stage planetary mechanism (1) to the second-stage planetary mechanism (2), and the second-stage sun gear (202) of the second-stage planetary mechanism (2) is connected to the third-stage planet carrier (301) of the third-stage planetary mechanism (3) via a spline, so as to transmit the power increased by the first-stage planetary mechanism (1) to the second-stage planetary mechanism (2). The power increased in speed by the secondary planetary mechanism (2) is transmitted to the tertiary planetary mechanism (3); the tertiary sun gear (302) of the tertiary planetary mechanism (3) is connected to the tertiary planet carrier (401) of the tertiary planetary mechanism (4) via a spline, and the power increased in speed by the tertiary planetary mechanism (3) is transmitted to the tertiary planetary mechanism (4); the tertiary sun gear (402) of the tertiary planetary mechanism (4) is connected to the tertiary driving gear (5) via a spline, and the power increased in speed by the tertiary planetary mechanism (4) is transmitted to the tertiary driving gear (5); the tertiary driving gear (5) serves as a parallel stage transmission and meshes with an output shaft gear (7) on the output shaft (6) to form a parallel shaft cylindrical gear transmission.

2. The five-stage transmission structure of the doubly-fed wind turbine main gearbox according to claim 1 is characterized in that: The primary planetary mechanism (1) comprises a primary planet carrier (101), a primary sun gear (102), a primary planet gear (103) and a primary ring gear (104), wherein the primary planet gear (103) is mounted on the primary planet carrier (101) via a pin shaft and is located in the primary ring gear (104), respectively meshing with the primary ring gear (104) and the primary sun gear (102), the number of the primary planet gears (103) is 10-12, the diameter of the primary ring gear (104) is 2900-3000 mm, and the tooth width is 500-600 mm.

3. The five-stage transmission structure of a doubly-fed wind turbine main gearbox according to claim 1 is characterized in that: The secondary planetary mechanism (2) comprises a secondary planet carrier (201), a secondary sun gear (202), a secondary planetary gear (203) and a secondary ring gear (204), wherein the secondary planetary gear (203) is mounted on the secondary planet carrier (201) via a pin shaft and is located in the secondary ring gear (204), respectively meshing with the secondary ring gear (204) and the secondary sun gear (202), the number of the secondary planetary gears (203) is 8-10, the diameter of the secondary ring gear (204) is 2500-2600 mm, and the tooth width is 300-400 mm.

4. The five-stage transmission structure of a doubly-fed wind turbine main gearbox according to claim 1 is characterized in that: The three-stage planetary mechanism (3) comprises a three-stage planetary carrier (301), a three-stage sun gear (302), a three-stage planetary gear (303) and a three-stage ring gear (304), wherein the three-stage planetary gear (303) is mounted on the three-stage planetary carrier (301) via a pin shaft and is located in the three-stage ring gear (304), and is meshed with the three-stage ring gear (304) and the three-stage sun gear (302), respectively; the number of the three-stage planetary gear (303) is 8-10, the diameter of the three-stage ring gear (304) is 2000-2150 mm, and the tooth width is 250-280 mm.

5. The five-stage transmission structure of the doubly-fed wind turbine main gearbox according to claim 1 is characterized in that: The four-stage planetary mechanism (4) comprises a four-stage planetary carrier (401), a four-stage sun gear (402), a four-stage planetary gear (403) and a four-stage ring gear (404), wherein the four-stage planetary gear (403) is mounted on the four-stage planetary carrier (401) via a pin shaft and is located in the four-stage ring gear (404), respectively meshing with the four-stage ring gear (404) and the four-stage sun gear (402), the number of the four-stage planetary gear (403) is five, the diameter of the four-stage ring gear (404) is 1800-1900 mm, and the tooth width is 200-300 mm.

6. The five-stage transmission structure of the doubly-fed wind turbine main gearbox according to claim 1 is characterized in that: The speed ratio of the first-stage planetary mechanism (1) is 2.5-2.7, the speed ratio of the second-stage planetary mechanism (2) is 2.7-2.9, the speed ratio of the third-stage planetary mechanism (3) is 2.7-2.9, the speed ratio of the fourth-stage planetary mechanism (4) is 4-4.3, and the speed ratio of the parallel shaft cylindrical gear transmission is 3.

7. The five-stage transmission structure of the doubly-fed wind turbine main gearbox according to claim 1 is characterized in that: The total speed ratio of this five-stage transmission structure reaches 260.

8. A doubly-fed wind turbine main gearbox, characterized in that: It is a 13-16MW wind power main gearbox having a five-stage transmission structure as claimed in any one of claims 1 to 7.

9. A doubly-fed wind turbine main gearbox according to claim 8, characterized in that: The torque density of the 13-16MW wind power main gearbox reaches 240-250kNm / t.