Semi-direct-drive wind power main gear box and four-stage transmission structure thereof

Abstract

The utility model discloses a semi-direct-drive wind power main gear box and a four-stage transmission structure thereof. The four-stage transmission structure comprises a first-stage planetary mechanism, a second-stage planetary mechanism, a third-stage planetary mechanism, a four-stage planetary mechanism 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. And a fourth-stage sun gear of the fourth-stage planetary mechanism is connected with the output shaft through a spline. According to the utility model, the torque density can be greatly improved, and the manufacturing cost is reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of wind power generation, in particular to a semi-direct-drive wind power main gear box and a four-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 gaining market opportunities. However, how to reduce the weight of the main gearbox of the wind turbine while ensuring product reliability is a difficult design point.

[0003] At present, in the industry, for the semi-direct drive wind turbine main gearbox, a two-stage planetary or three-stage planetary structure layout is usually adopted. The disadvantages of this gearbox structure 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 four-stage transmission structure of a semi-direct-drive 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 semi-direct drive wind turbine main gearbox.

[0011] The first object of the utility model is achieved through the following technical solutions: a four-stage transmission structure of a semi-direct-drive wind power main gearbox, the four-stage transmission structure comprising a primary planetary mechanism, a secondary planetary mechanism, a third planetary mechanism, a fourth planetary mechanism and an output shaft connected in sequence; wherein the primary planetary frame of the primary planetary mechanism serves as an input shaft for receiving power input, and its primary sun gear is connected to the secondary planetary frame of the secondary planetary mechanism through a spline, and transmits the power after the primary planetary mechanism speeds up to the secondary planetary mechanism; the secondary sun gear of the secondary planetary mechanism is connected to the third planetary frame of the third planetary mechanism through a spline, and transmits the power after the secondary planetary mechanism speeds up to the third planetary mechanism; the third sun gear of the third planetary mechanism is connected to the fourth planetary frame of the fourth planetary mechanism through a spline, and transmits the power after the third planetary mechanism speeds up to the fourth planetary mechanism; the fourth sun gear of the fourth planetary mechanism is connected to the output shaft through a spline, and transmits the power after the fourth planetary mechanism speeds up to the output shaft.

[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 3800-4000 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 10-11.

[0017] Specifically, the diameter of the secondary gear ring is 3100-3200 mm, and the tooth width is 400-450 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 9-10.

[0020] Specifically, the diameter of the three-stage gear ring is 2200-2300 mm, and the tooth width is 250-300 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 2000-2200 mm, and the tooth width is 280-320 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 2.6-2.7, the speed ratio of the third-stage planetary mechanism is 2.7-2.8, and the speed ratio of the fourth-stage planetary mechanism is 4-4.3.

[0025] Specifically, the total speed ratio of the four-stage transmission structure reaches 78.

[0026] The second purpose of the utility model is achieved through the following technical solution: a semi-direct drive wind turbine main gearbox, specifically a 20-24MW wind turbine main gearbox, having the above-mentioned four-stage transmission structure.

[0027] Specifically, the torque density of the 20-24MW wind turbine main gearbox reaches 250-260kNm / t.

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

[0029] 1. The number of first-stage planetary gears in the first-stage planetary mechanism is 10-12, the number of second-stage planetary gears in the second-stage planetary mechanism is 10-11, and the number of third-stage planetary gears in the third-stage planetary mechanism is 9-10. The speed of each stage is relatively 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 250kNm / 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 four-stage transmission structure of a semi-direct-drive 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 and an output shaft 5 connected in sequence;

[0039] The primary planetary mechanism 1 includes a primary planetary 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 planetary 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 planetary carrier 101 serves as an input shaft for receiving power input. The number of primary planetary gears 103 is 12, and the speed ratio is about 2.5. The diameter of the primary ring gear 104 is 3800-4000mm, and the tooth width is 500-600mm. The primary sun gear 102 is connected to the secondary planetary 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, respectively meshing with the secondary ring gear 204 and the secondary sun gear 202. There are 11 secondary planetary gears 203, and the speed ratio is about 2.6. The diameter of the secondary ring gear 204 is 3100-3200mm, and the tooth width is 400-450mm. 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 increased by 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 2200-2300mm, and the tooth width is 250-300mm. 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 three-stage planetary mechanism 3 is increased in speed 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 2000-2200mm, and the tooth width is 280-320mm. The four-stage sun gear 402 is connected to the output shaft 5 through a spline, and transmits the power after the speed increase of the four-stage planetary mechanism 4 to the output shaft 5;

[0043] After the above four-stage transmission, the total speed ratio reaches about 78; the power is finally output from the output shaft 5 and transmitted to the generator, and the gearbox completes the functions of power transmission and speed increase.

[0044] Example 2

[0045] 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.

[0046] Example 3

[0047] Different from Example 1, in this embodiment, the number of first-stage planetary gears 103 of the first-stage planetary mechanism 1 is 10, and the speed ratio is about 2.7; the number of second-stage planetary gears 203 of the second-stage planetary mechanism 2 is 10, and the speed ratio is about 2.7; the speed ratio of the fourth-stage planetary mechanism 4 is about 4.3.

[0048] Example 4

[0049] This embodiment discloses a semi-direct drive wind turbine main gearbox, specifically a 20-24MW wind turbine main gearbox, which has the four-stage transmission structure described in any one of Embodiments 1 to 3, and the torque density of the gearbox reaches 250-260kNm / t.

[0050] 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 four-stage transmission structure of a semi-direct drive wind turbine main gearbox, characterized in that: The four-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) and an output shaft (5) 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 second-stage planet carrier (201) via a spline. The third-stage planetary frame (301) of the third-stage planetary mechanism (3) is connected to transmit the power accelerated by the second-stage planetary mechanism (2) to the third-stage planetary mechanism (3); the third-stage sun gear (302) of the third-stage planetary mechanism (3) is connected to the fourth-stage planetary frame (401) of the fourth-stage planetary mechanism (4) via a spline, and transmits the power accelerated by the third-stage planetary mechanism (3) to the fourth-stage planetary mechanism (4); the fourth-stage sun gear (402) of the fourth-stage planetary mechanism (4) is connected to the output shaft (5) via a spline, and transmits the power accelerated by the fourth-stage planetary mechanism (4) to the output shaft (5).

2. The four-stage transmission structure of a semi-direct drive 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 3800-4000 mm, and the tooth width is 500-600 mm.

3. The four-stage transmission structure of a semi-direct drive 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 10-11, the diameter of the secondary ring gear (204) is 3100-3200 mm, and the tooth width is 400-450 mm.

4. The four-stage transmission structure of a semi-direct drive 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 respectively meshed with the three-stage ring gear (304) and the three-stage sun gear (302); the number of the three-stage planetary gear (303) is 9-10, the diameter of the three-stage ring gear (304) is 2200-2300 mm, and the tooth width is 250-300 mm.

5. The four-stage transmission structure of a semi-direct drive 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 2000-2200 mm, and the tooth width is 280-320 mm.

6. The four-stage transmission structure of a semi-direct drive 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 2.6-2.7, the speed ratio of the third-stage planetary mechanism (3) is 2.7-2.8, and the speed ratio of the fourth-stage planetary mechanism (4) is 4-4.

3.

7. The four-stage transmission structure of a semi-direct drive wind turbine main gearbox according to claim 1 is characterized in that: The total speed ratio of this four-stage transmission structure reaches 78.

8. A semi-direct drive wind turbine main gearbox, characterized in that: It is a 20-24MW wind power main gearbox having a four-stage transmission structure as claimed in any one of claims 1 to 7.

9. A semi-direct drive wind turbine main gearbox according to claim 8, characterized in that: The torque density of the 20-24MW wind power main gearbox reaches 250-260kNm / t.

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