Gear box and wind generating set

Abstract

According to the gear box and the wind generating set, the bearing capacity of the gear box can be improved, and the transmission speed ratio can be increased. The gearbox comprises first, second and third planetary gear trains; the large planet gear is externally meshed with the first sun gear; the first gear ring is connected with the input shaft; the second planetary gear train comprises a second gear ring, a second planet gear, a second planet carrier and a second sun gear, one of the second gear ring and the second planet carrier is connected with the input shaft, and the other one of the second gear ring and the second planet carrier is connected with the first sun gear; the third planetary gear train comprises a third gear ring, a third planet gear, a third planet carrier and a third sun gear, the third planet carrier is connected with the input shaft, the third gear ring is connected with the second sun gear, and the third sun gear is connected with the output shaft.

Description

Technical Field

[0001] The present invention relates to the technical field of transmissions, and particularly to a gearbox and a wind power generating set. Background Art

[0002] A wind power generating set includes a gearbox, which converts the power of low speed but high torque of the main shaft into the power of high speed and low torque that is beneficial to the power generation of the generator. The gearbox generally adopts structural forms such as a series-connected planetary gear train and a parallel-axis gear transmission. However, it is difficult for a gearbox of this structural form to simultaneously meet the requirements of high torque load capacity and large transmission ratio. Summary of the Invention

[0003] The purpose of the present application is to provide a gearbox and a wind power generating set, which can improve the bearing capacity of the gearbox and increase the transmission ratio.

[0004] The present application provides a gearbox, which includes a first planetary gear train, a second planetary gear train, and a third planetary gear train;

[0005] The first planetary gear train includes a first ring gear and a first sun gear; the first ring gear is connected to the input shaft of the gearbox;

[0006] The second planetary gear train includes a second ring gear, second planet gears, a second planet carrier, and a second sun gear. One of the second ring gear and the second planet carrier is connected to the input shaft, and the other is connected to the first sun gear;

[0007] The third planetary gear train includes a third ring gear, third planet gears, a third planet carrier, and a third sun gear. One of the third ring gear and the third planet carrier is connected to the input shaft, and the other is connected to the second sun gear; the third sun gear is connected to the output shaft of the gearbox.

[0008] Optionally, the third planet carrier is connected to the input shaft, and the third ring gear is connected to the second sun gear; the second planetary gear train is located at one end of the first planetary gear train in the axial direction, and the third planetary gear train is located at the other end of the first planetary gear train in the axial direction; the input shaft passes through the second planetary gear train and the first planetary gear train and is connected to the third planet carrier.

[0009] Optionally, the third planetary gear train, the second planetary gear train, and the first planetary gear train are arranged in sequence along the axial direction, and the third planetary gear train is arranged close to the input shaft. The output shaft passes through the first planetary gear train and the second planetary gear train and is connected to the third sun gear.

[0010] Optionally, the first planetary gear train includes a first planetary gear set, a sun idler gear, a planetary idler gear, a first planet carrier, and a fourth planet carrier; the first planetary gear set includes a small planetary gear and a large planetary gear that are coaxially and floatingly connected along the axial direction, the planetary idler gear is mounted on the first planet carrier, and the large planetary gear is mounted on the fourth planet carrier; both the planetary idler gear and the small planetary gear are internally meshed with the first ring gear and externally meshed with the sun idler gear; the large planetary gear is externally meshed with the first sun gear.

[0011] Optionally, the second ring gear is connected to the input shaft, and the second planet carrier is connected to the first sun gear; the third planet carrier is connected to the input shaft, and the third ring gear is connected to the second sun gear.

[0012] Optionally, the torque borne by the first ring gear is greater than the torques borne by the second ring gear and the third planet carrier, and the proportions of the first ring gear, the second ring gear, and the third planet carrier in the input torque load are respectively:

[0013]

[0014]

[0015]

[0016] In the formula:

[0017] SR=(K1 + 1)(K2 + 1)K3 + 1

[0018]

[0019]

[0020] K1 = K 1A ·K 1B

[0021]

[0022]

[0023] Wherein, T R1 , T R2 , T C3 are the torques borne by the first ring gear, the second ring gear, and the third planet carrier respectively, Tin is the torque of the input shaft, ZR1, ZR2, and ZR3 are the number of teeth of the first ring gear, the second ring gear, and the third ring gear respectively; ZS1, ZS2, and ZS3 are the number of teeth of the first sun gear, the second sun gear, and the third sun gear respectively; ZPS and ZPL are the number of teeth of the small planetary gear and the large planetary gear respectively.

[0024] Optionally, the number of the small planet gears is equal to the number of the planet idler gears; the proportion of the balanced torque borne by the first planet carrier and the fourth planet carrier to the input torque is:

[0025]

[0026]

[0027] In the formula:

[0028] SR = (K1 + 1)(K2 + 1)K3 + 1

[0029]

[0030]

[0031] K1 = K 1A ·K 1B

[0032]

[0033]

[0034] wherein, T C1 , T C1’ are the balanced torques provided by the first planet carrier and the fourth planet carrier respectively, Tin is the torque of the input shaft; ZR1, ZR2 and ZR3 are the number of teeth of the first ring gear, the second ring gear and the third ring gear respectively; ZS1, ZS2 and ZS3 are the number of teeth of the first sun gear, the second sun gear and the third sun gear respectively; ZPS and ZPL are the number of teeth of the small planet gear and the large planet gear respectively.

[0035] Optionally, the second ring gear is connected to the input shaft, and the second planet carrier is connected to the first sun gear; the third ring gear is connected to the input shaft, and the third planet carrier is connected to the second sun gear.

[0036] Optionally, the torque borne by the first ring gear is greater than the torques borne by the second ring gear and the third ring gear, and the proportions of the first ring gear, the second ring gear and the third ring gear in the input torque load are respectively:

[0037]

[0038]

[0039]

[0040] In the formula:

[0041] SR = (K1 + 1)(K2 + 1)(K3 + 1) - 1

[0042]

[0043]

[0044] K1 = K 1A ·K 1B

[0045]

[0046]

[0047] Wherein, T R1 、T R2 、T R3 are the torques borne by the first ring gear, the second ring gear, and the third ring gear respectively, Tin is the torque of the input shaft, ZR1, ZR2, and ZR3 are the number of teeth of the first ring gear, the second ring gear, and the third ring gear respectively; ZS1, ZS2, and ZS3 are the number of teeth of the first sun gear, the second sun gear, and the third sun gear respectively; ZPS and ZPL are the number of teeth of the planet pinion and the planet gear respectively.

[0048] Optionally, the number of the planet pinions is equal to the number of the planet idle gears; the proportion of the balanced torque borne by the first planet carrier and the fourth planet carrier in the input torque is:

[0049] In the formula:

[0050]

[0051]

[0052] In the formula:

[0053] SR = (K1 + 1)(K2 + 1)(K3 + 1) - 1

[0054]

[0055]

[0056] K1 = K 1A ·K 1B

[0057]

[0058]

[0059] Wherein, T C1 、T C1’The balance torques provided for the first planet carrier and the fourth planet carrier respectively, Tin is the torque of the input shaft; ZR1, ZR2, and ZR3 are the number of teeth of the first ring gear, the second ring gear, and the third ring gear respectively; ZS1, ZS2, and ZS3 are the number of teeth of the first sun gear, the second sun gear, and the third sun gear respectively; ZPS and ZPL are the number of teeth of the small planet gear and the large planet gear respectively.

[0060] Optionally, the planet idler gear is supported on the first planet carrier through a first bearing, and the large planet gear of the first planet gear set is supported on the fourth planet carrier through a second bearing; the first bearing is a rolling bearing or a sliding bearing, and the outer raceway ring of the rolling bearing is integrated with the corresponding planet idler gear; the second bearing is a rolling bearing.

[0061] Optionally, the first planetary gear train includes a plurality of the first planetary gear sets, and at least two of the large planet gears are axially offset and at least partially overlap in the axial projection.

[0062] Optionally, the small planet gear can float circumferentially relative to the fourth planet carrier.

[0063] Optionally, the circumferential floating amount of the planet idler gear relative to the first planet carrier is less than the circumferential floating amount of the small planet gear relative to the fourth planet carrier.

[0064] The present application provides a wind turbine generator set, including a blade hub, a main shaft, and a gearbox. The gearbox is the gearbox described in any one of the above, and the input shaft of the gearbox is connected to the blade hub through the main shaft.

[0065] The gearbox in the present application introduces a torque splitting form of differential splitting, distributes the torque of the input shaft to each planetary gear train, so as to improve the load-bearing capacity of the gearbox, thereby greatly increasing the torque density, and at the same time achieving a large transmission ratio. Description of the Drawings

[0066] Figure 1 It is a schematic structural diagram of the gearbox in the first embodiment of the present application.

[0067] Figure 2 It is a schematic diagram of the first planetary gear train in the first embodiment of the present application;

[0068] Figure 3 is Figure 2 the end schematic diagram of the first planetary gear train in

[0069] Figure 4 is Figure 3 the sectional view taken along the A-B direction in

[0070] Figure 5 is Figure 3 the sectional view taken along line B-B in

[0071] Figure 6 the structural schematic diagram of the second planetary gear train in the first embodiment of the present application;

[0072] Figure 7 the structural schematic diagram of the third planetary gear train in the embodiment of the present application;

[0073] Figure 8 is Figure 1 the schematic diagram with the local position in bold;

[0074] Figure 9 the structural schematic diagram of the gearbox in the second embodiment of the present application;

[0075] Figure 10 the structural schematic diagram of the gearbox in the third embodiment of the present application;

[0076] Figure 11 the structural schematic diagram of the gearbox in the fourth embodiment of the present application;

[0077] Figure 12 the structural schematic diagram of the gearbox in the fifth embodiment of the present application.

[0078] Figure 1-12 The descriptions of the reference numerals in the drawings are as follows:

[0079] 1000 - gearbox;

[0080] 10 - housing; 20 - first connecting sleeve; 30 - second connecting sleeve; 40 - second bearing; 50 - first bearing;

[0081] 100 - first planetary gear train; R1 - first ring gear; Ps - small planet gear; P L - large planet gear; P D - planet idler gear; S D - sun idler gear; S1 - first sun gear; C1 - first planet carrier; C1’ - fourth planet carrier;

[0082] 200 - second planetary gear train; R2 - second ring gear; P2 - second planet gear; S2 - second sun gear; C2 - second planet carrier;

[0083] 300 - third planetary gear train; R3 - second ring gear; P3 - third planet gear; S3 - third sun gear; C3 - third planet carrier;

[0084] Tin - input shaft; Tout - output shaft. Detailed implementation manners

[0085] To enable those skilled in the art to better understand the solution of the present invention, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0086] Please refer to Figure 1 , Figure 1 , which is the structural schematic diagram of the gearbox 1000 in the first embodiment of the present application.

[0087] The gearbox 1000 in this embodiment includes a plurality of coaxial planetary gear trains. In this embodiment, it includes a first planetary gear train 100, a second planetary gear train 200, and a third planetary gear train 300. Among them, the first planetary gear train 100 is a first planetary gear train, and the second planetary gear train 200 and the third planetary gear train 300 are simple planetary gear trains. The gearbox 1000 includes a housing 10, and the housing 10 includes a torque arm and a fixed flange. The torque arm can balance the input torque, and the fixed flange fixes the gearbox 1000 to the corresponding equipment. For example, when applied to a wind power generation unit, the fixed flange can fix the gearbox 1000 to the tower of the wind power generation unit or other components of the tower.

[0088] The following is a separate description of each planetary gear train.

[0089] As Figures 2-5 shown, Figure 2 is a schematic diagram of the first planetary gear train 100 in the first embodiment of the present application, and its planet carrier is not shown; Figure 3 is Figure 2 the end schematic diagram of the first planetary gear train 100 in D , mainly showing the first ring gear R1, the small planet gear Ps of the first planetary gear family P1, the planet idler gear P D ; Figure 4 is Figure 3 the sectional view taken along the A-B direction in Figure 5 is Figure 3 the sectional view taken along the B-B direction in

[0090] Specifically, the first planetary gear train 100 includes a first ring gear R1, a first planetary gear family P1, a sun idler gear S D , a planet idler gear P D , and a first sun gear S1. The first planetary gear family P1 includes a small planet gear Ps, a large planet gear P L and a connecting shaft Pz connecting the small planet gear Ps and the large planet gear P L . The diameter or number of teeth of the large planet gear P L is greater than that of the small planet gear Ps. The small planet gear Ps and the large planet gear P L are distributed axially, and the small planet gear Ps and the large planet gear P L are coaxially connected through the connecting shaft Pz.

[0091] and the planetary idler gear P D and the small planetary gear Ps are both in internal engagement with the first ring gear R1 and are both in external engagement with the sun idler gear S D ; the large planetary gear P L is in external engagement with the first sun gear S1.

[0092] The first planetary gear train 100 includes a planet carrier, and the planet carrier specifically includes a first planet carrier C1 and a fourth planet carrier C1'. The planetary idler gear P D can be installed on the first planet carrier C1, and the first planetary gear set P1 can be installed on the fourth planet carrier C1'. Specifically, the large planetary gear P L is installed on the fourth planet carrier C1', and the small planetary gear Ps is not installed on the planet carrier and is floatingly arranged. Among them, the small planetary gear Ps and the large planetary gear P of the first planetary gear set P1 L are axially coaxially floatingly connected to transmit torque, and there can be radial floating between them. The small planetary gear Ps is a floating planetary gear and can radially float relative to the fourth planet carrier C1'. And the planetary idler gear P D cannot radially float relative to the first planet carrier C1, or, the planetary idler gear P D although it can radially float relative to the first planet carrier C1, the maximum radial floating amount is not greater than the maximum radial floating amount of the small planetary gear Ps. In addition, the small planetary gear P S relative to the large planetary gear P L or the fourth planet carrier C1' allows a certain circumferential floating amount, that is, it can float along the circumferential direction of the fourth planet carrier C1'. The planetary idler gear P D does not allow an excessive circumferential floating amount relative to the first planet carrier C1, or its circumferential floating amount relative to the first planet carrier C1 is very small and less than the circumferential floating amount of the small planetary gear Ps.

[0093] The gearbox 1000 in this embodiment includes an input shaft Tin, and the first ring gear R1 of the first planetary gear train 100 is connected to the input shaft Tin. Due to the above floating design, when the first ring gear R1 rotates around the axis under the action of the input torque, at least part of the torque will be transmitted to the planetary idler gear P D , and then transmitted from the planetary idler gear P D to the sun idler gear S D ; the sun idler gear S D and the first ring gear R1 jointly drive the small planetary gear Ps of the first planetary gear set P1, so that the planetary idler gear P D and the small planetary gear Ps jointly share the torque load of the first ring gear R1. Therefore, the torque load of the small planetary gear Ps can be reduced, and the torque load capacity of the entire first planetary gear train 100 can be improved.

[0094] Moreover, since the torque load of the small planet gear Ps is reduced, even a small-sized small planet gear Ps can meet the load-bearing requirements. Therefore, more small planet gears Ps can be arranged under the same volume condition. Thus, while considering the small volume, the torque load capacity of the entire first planetary gear train 100 can be further improved by increasing the number of small planet gears Ps, so as to achieve a higher torque load density.

[0095] In this embodiment, the large planet gear P of the first planet gear family P1 L is externally meshed with the first sun gear S1, so that the torque can be further transmitted to the first sun gear S1, and the first sun gear S1 outputs the torque. Since the diameter of the large planet gear P L is larger than the diameter of the small planet gear Ps, using the large planet gear P L meshed with the first sun gear S1 for torque output can enable the first planetary gear train 100 to obtain a larger transmission ratio, and at the same time realize the redistribution of torque between the small planet gears Ps and the large planet gear P L .

[0096] In this embodiment, when multiple first planet gear families P1 are included, that is, the number of the small planet gears Ps and the large planet gears P L are both two or more, then the large planet gears P of at least two first planet gear families P1 L are axially staggered from each other and partially overlap in the projection on the plane perpendicular to the axial direction. Since the large planet gears P L are axially staggered, along the direction away from the input shaft Tin, the distances between the staggered large planet gears P L and the small planet gears Ps are not equal. The large planet gear P L with a long distance from the small planet gears Ps and the coaxial small planet gears Ps form a long planet gear family, and the large planet gear PL with a short distance from the small planet gears Ps and the coaxial small planet gears Ps form a short planet gear family. The long planet gear family and the short planet gear family are arranged crosswise in the circumferential direction. By arranging the large planet gears P L axially staggered, the size of the large planet gears P L can be set larger under the same volume condition, which is beneficial for the first planetary gear train 100 to obtain a larger transmission ratio.

[0097] By adopting the above differential floating design and making at least two large planet gears P L axially staggered from each other and partially overlap in the projection on the plane perpendicular to the axial direction, the first planetary gear train 100 has a high torque load capacity, a large transmission ratio and a small volume.

[0098] Please see again Figure 6 、 7 , Figure 6Schematic diagram of the structure of the second planetary gear train 200 in the first embodiment of the present application; Figure 7 Schematic diagram of the structure of the third planetary gear train 300 in the embodiment of the present application. The second planetary gear train 200 and the third planetary gear train 300 have the same structure, and both are simple planetary gear trains.

[0099] The second planetary gear train 200 includes a second ring gear R2, second planet gears P2, a second planet carrier C2, and a second sun gear S2. The second ring gear R2 and the second planet gears P2 are in internal meshing, and the second planet gears P2 and the second sun gear S2 are in external meshing.

[0100] The third planetary gear train 300 includes a third ring gear R3, third planet gears P3, a third planet carrier C3, and a third sun gear S3. The third ring gear R3 and the third planet gears P3 are in internal meshing, and the third planet gears P3 and the second sun gear S2 are in external meshing.

[0101] Look again Figure 1 In this embodiment, the first ring gear R1 of the first planetary gear train 100 is connected to the input shaft Tin of the gearbox 1000, the second ring gear R2 in the second planetary gear train 200 is connected to the input shaft Tin, and the third planet carrier C3 in the third planetary gear train 300 is connected to the input shaft Tin. That is, the torque of the input shaft Tin is transmitted to the first ring gear R1, the second ring gear R2, and the third planet carrier C3 of the three planetary gear trains at the same time.

[0102] In addition, the first sun gear S1 of the first planetary gear train 100 is connected to the second planet carrier C2 of the second planetary gear train 200, and the second sun gear S2 of the second planetary gear train 200 is connected to the third ring gear R3 of the third planetary gear train 300. The third sun gear S3 of the third planetary gear train 300 is connected to the output shaft Tout of the gearbox 1000.

[0103] In this embodiment, the first ring gear R1 of the first planetary gear train 100 and the second ring gear R2 of the second planetary gear train 200 are both connected to the input shaft Tin, that is, the first ring gear R1 and the second ring gear R2 are connected, and the first sun gear S1 of the first planetary gear train 100 is connected to the second carrier C2 of the second planetary gear train 200; the second ring gear R2 of the second planetary gear train 200 and the third carrier C3 of the third planetary gear train 300 are both connected to the input shaft Tin, that is, the second ring gear R2 and the third carrier C3 are connected, and the second sun gear S2 of the second planetary gear train 200 is connected to the third ring gear R3 of the third planetary gear train 300. It can be seen that the first ring gear R1 and the first sun gear S1 of the first planetary gear train 100 are connected to two relatively rotating components of the second planetary gear train 200, and the second ring gear R2 and the second sun gear S2 of the second planetary gear train 200 are connected to two relatively rotating components of the third planetary gear train 300. The rotation directions of the first sun gear S1 and the first ring gear R1 are opposite, and the rotation directions of the second sun gear S2 and the second ring gear R2 are opposite. Two components with opposite rotation directions and coaxial rotation are defined as differential components. Then, the differential components of the first planetary gear train 100 and the second planetary gear train 200 are both connected to two components of another stage of planetary gear train.

[0104] In summary, in this embodiment, the first planetary gear train 100 of the gearbox 1000 is a compound planetary gear train, and through the planetary idler gear P D and by setting the first planetary gear set P1, the first planetary gear train 100 has a higher torque load capacity, a larger transmission ratio and a smaller volume; at the same time, the second planetary gear train 200 and the third planetary gear train 300 are also configured to jointly transmit torque with the first planetary gear train 100, and the ring gears and carriers of the second planetary gear train 200 and the third planetary gear train 300 have torque input at the same time, and the input torque is transmitted by the differential components of the upper-stage planetary gear train, which can further improve the torque load capacity and increase the transmission ratio.

[0105] That is, in this embodiment, the gearbox 1000 introduces two different torque splitting forms: idler gear splitting and differential splitting. First, the input torque is distributed to each planetary gear train according to a certain ratio, and then the torque on the first planetary gear train 100 with a higher load is distributed to two different sets of planetary gears. One set is the planetary idler gear P D , and the other set is the small planetary gear P S . In this way, multiple torque splittings are realized, the load-bearing capacity of the gearbox 1000 is improved, and the torque density is greatly increased.

[0106] As described above, the torque of the input shaft Tin is transmitted to the three planetary gear trains, and the input shaft Tin is respectively connected to the first ring gear R1, the second ring gear R2 and the third carrier C3. It is defined that the torques borne by the first ring gear R1, the second ring gear R2 and the third carrier C3 are TR1 、T R2 、T C3 At this time, the proportions of the first ring gear R1, the second ring gear R2, and the third planet carrier C3 in the input torque load are respectively:

[0107]

[0108]

[0109]

[0110] In the formula:

[0111] SR = (K1 + 1)(K2 + 1)K3 + 1

[0112]

[0113]

[0114] K1 = K 1A ·K 1B

[0115]

[0116]

[0117] Among them, ZR1, ZR2, and ZR3 are the number of teeth of the first ring gear R1, the second ring gear R2, and the third ring gear R3 respectively; ZS1, ZS2, and ZS3 are the number of teeth of the first sun gear S1, the second sun gear S2, and the third sun gear S3 respectively; ZP S and ZP L are the number of teeth of the small planet gear Ps and the large planet gear P L respectively. It can be seen that the number of teeth of each tooth component can be adjusted to adjust the torque ratio of the first ring gear R1, the second ring gear R2, and the third planet carrier C3.

[0118] In this embodiment, the number of small planet gears Ps in the first planetary gear train 100 is equal to the number of planetary idler gears P D , so that their sizes and numbers are equal, which is beneficial to further improving the speed ratio.

[0119] The first planetary gear train 100 includes a first planet carrier C1 and a fourth planet carrier C1', and the planetary idler gear P D is installed on the first planet carrier C1, and the large planet gear P LIt is installed on the fourth planet carrier C1'. The first planet carrier C1 and the fourth planet carrier C' are installed on the housing 10 of the gearbox 1000. In this way, the first planet carrier C1 and the fourth planet carrier C' can jointly provide counter-torque to balance the input and output of the gearbox 1000. Define the balance torques borne by the first planet carrier C1 and the fourth planet carrier C1' as T C1 , T C2 , T C1 , T C2 . The proportions of T

[0120]

[0121]

[0122] in the input torque are as follows:

[0123] SR = (K1 + 1)(K2 + 1)K3 + 1

[0124]

[0125] K1 = K 1A ·K 1B

[0126]

[0127]

[0128] The planet idler P D in this embodiment is supported on the first planet carrier C1 through the first bearing 50, and the large planet gear P of the first planet gear set P1 L is supported on the fourth planet carrier C1' through the second bearing 40. The first bearing 50 can be a rolling bearing or a sliding bearing. When it is a rolling bearing, the outer raceway ring of the rolling bearing as the first bearing 50 can be integrated with the planet idler P D to form a simple structure. The second bearing 40 is a rolling bearing.

[0129] As Figure 1 shown, the second planetary gear train 200 in this embodiment is located at one axial end of the first planetary gear train 100, and the third planetary gear train 300 is located at the other axial end of the first planetary gear train 100. At this time, the connection between the third sun gear S3 of the third planetary gear train 300 and the output shaft Tout is relatively simple.

[0130] At this time, the input shaft Tin needs to pass through the second planetary gear train 200 and the first planetary gear train 100 and be connected to the third planet carrier C3. As Figure 8 shown, Figure 8 for Figure 1Schematic diagram with local positions in bold, showing the first connecting sleeve 20 and the second connecting sleeve 30. Figure 8 In Figure 8 , the third ring gear R3 is connected to the second sun gear S2 through the first connecting sleeve 20, and the first sun gear S1 is connected to the second planet carrier C2 through the second connecting sleeve 30. Therefore, the second connecting sleeve 30 is sleeved outside the first connecting sleeve 20, and the first connecting sleeve 20 is sleeved outside the input shaft Tin, with a relatively complex structure.

[0131] At this time, you can continue to view Figure 9 , Figure 9 which is the structural schematic diagram of the gearbox 1000 in the second embodiment of the present application.

[0132] The structure in this embodiment is basically the same as that in the first embodiment, except that the azimuth of the third planetary gear train 300 and the first planetary gear train 100 in the first embodiment is different. In the second embodiment, the third planetary gear train 300, the second planetary gear train 200, and the first planetary gear train 100 are arranged axially in sequence, and relative to the first planetary gear train 100 and the second planetary gear train 200, the third planetary gear train 300 is arranged closer to the input shaft Tin. At this time, the input shaft Tin is directly connected to the third planet carrier C3, and the connection is relatively simple.

[0133] In this arrangement, the output shaft Tout needs to pass through the first planetary gear train 100 and the second planetary gear train 200 to be connected to the third sun gear S3. In the second embodiment, the first connecting sleeve 20 connecting the third ring gear R3 and the second sun gear S2, and the second connecting sleeve 30 connecting the first sun gear S1 and the second planet carrier C2 are axially distributed and do not need to be nested with each other. The output shaft Tout passes through the first connecting sleeve 20 and the second connecting sleeve 30. Compared with the first embodiment, the structural form of the gearbox 1000 in the second embodiment is simpler and easier to manufacture.

[0134] Let's look at Figure 10 , Figure 10 which is the structural schematic diagram of the gearbox 1000 in the third embodiment of the present application.

[0135] The third embodiment is basically the same as the first embodiment, except that in the first planetary gear train 100 of the third embodiment, the multiple large planetary gears PL of the first planetary gear family P1 are not staggered axially, and this is also a feasible solution. However, in the first embodiment, the large planetary gears PL are staggered and at least two large planetary gears PL overlap in the axial projection, which is beneficial to achieving a larger transmission ratio.

[0136] In the above embodiments, the differential component of the first planetary gear train 100 is connected to two rotating components of the second planetary gear train 200. Specifically, the first sun gear S1 is connected to the second planet carrier C2, and the first ring gear R1 and the second ring gear R2 are both connected to the input shaft Tin. It can be seen that it is also possible to connect the first sun gear S1 to the second ring gear R2 and the second planet carrier C2 to the input shaft Tin. Comparatively speaking, connecting the first sun gear S1 to the second planet carrier C2 and the first ring gear R1 to the second ring gear R2 is simpler in structure.

[0137] Continue to view Figure 11 , Figure 11 is the structural schematic diagram of the gearbox 1000 in the fourth embodiment of the present application.

[0138] In the foregoing first to third embodiments, the torque of the input shaft Tin is split into three planetary gear trains by means of differential splitting. In all three embodiments, the second sun gear S2 is connected to the third ring gear R3 of the third planetary gear train 300, and the input shaft Tin is connected to the third planet carrier C3 of the third planetary gear train 300. It can be seen that it is also possible to connect the second sun gear S2 to the third planet carrier C3 and the input shaft Tin to the third ring gear R3, which is also differential splitting and increases the transmission speed ratio.

[0139] At this time, the calculation methods for the proportions of the input torque loads borne by each planetary gear train are different. As described above, the torque of the input shaft Tin is transmitted to the three planetary gear trains. As Figure 11 shown, the input shaft Tin is respectively connected to the first ring gear R1, the second ring gear R2, and the third planet carrier C3. Define that the torques borne by the first ring gear R1, the second ring gear R2, and the third ring gear R3 are T R1 , T R2 , T R3 , respectively. At this time, the proportions of the first ring gear R1, the second ring gear R2, and the third ring gear R3 in the input torque load are respectively:

[0140]

[0141]

[0142]

[0143] In the formula:

[0144] SR = (K1 + 1)(K2 + 1)(K3 + 1) - 1

[0145]

[0146]

[0147] K1 = K 1A ·K1B

[0148]

[0149]

[0150] Among them, ZR1, ZR2, and ZR3 are the number of teeth of the first ring gear R1, the second ring gear R2, and the third ring gear R3 respectively; ZS1, ZS2, and ZS3 are the number of teeth of the first sun gear S1, the second sun gear S2, and the third sun gear S3 respectively; ZP S and ZP L are the number of teeth of the planet pinion Ps and the planet gear P L respectively. It can be seen that the number of teeth of each tooth component can be adjusted to adjust the torque ratio of the first ring gear R1, the second ring gear R2, and the third planet carrier C3.

[0151] Similarly, in the fourth embodiment, the number of planet pinions Ps in the first planetary gear train 100 is equal to the number of planet idle gears P D , so that their sizes and numbers are equal, which is beneficial to further improving the speed ratio.

[0152] The first planetary gear train 100 includes a first planet carrier C1 and a fourth planet carrier C1'. The planet idle gear P D is installed on the first planet carrier C1, and the planet gear P L is installed on the fourth planet carrier C1'. The first planet carrier C1 and the fourth planet carrier C' are installed on the housing 10 of the gearbox 1000. In this way, the first planet carrier C1 and the fourth planet carrier C' can jointly provide counter torque to balance the input and output of the gearbox 1000. Define the balance torques borne by the first planet carrier C1 and the fourth planet carrier C1' as T C1 , T C2 , T C1 , T C2 The proportions of the input torque are:

[0153]

[0154]

[0155] In the formula:

[0156] SR = (K1 + 1)(K2 + 1)(K3 + 1) - 1

[0157]

[0158]

[0159] K1 = K 1A ·K 1B

[0160]

[0161]

[0162] As Figure 11 shown, in the fourth embodiment, the second planetary gear train 200 is located at one axial end of the first planetary gear train 100, and the third planetary gear train 300 is located at the other axial end of the first planetary gear train 100. At this time, the connection between the third sun gear S3 of the third planetary gear train 300 and the output shaft Tout is relatively simple.

[0163] The third planetary gear train 300, the second planetary gear train 200, and the first planetary gear train 100 are arranged axially in sequence, and the third planetary gear train 300 is closer to the input shaft Tin relative to the first planetary gear train 100 and the second planetary gear train 200. At this time, the input shaft Tin is directly connected to the third planet carrier C3, and the connection is relatively simple.

[0164] In this arrangement, the output shaft Tout needs to pass through the first planetary gear train 100 and the second planetary gear train 200 to be connected to the third sun gear S3. The first connecting sleeve 20 connecting the third ring gear R3 and the second sun gear S2, and the second connecting sleeve 30 connecting the first sun gear S1 and the second planet carrier C2 are axially distributed and do not interfere with each other. The output shaft Tout passes through the first connecting sleeve 20 and the second connecting sleeve 30, and the connection is simple and easy to manufacture.

[0165] Reference may continue to be made to Figure 12 understand that Figure 12 is the structural schematic diagram of the gearbox 1000 in the fourth embodiment of the present application.

[0166] The fifth embodiment is basically the same as the fourth embodiment, except that in the first planetary gear train 100 of the fifth embodiment, the multiple large planetary gears P of the first planetary gear family P1 L do not stagger axially, and this is also a feasible solution. Only in the fourth embodiment, the large planetary gears P L are staggeredly arranged, and at least two large planetary gears P L overlap in the axial projection, which is beneficial to achieving a larger transmission ratio.

[0167] For the fourth and fifth embodiments, the differential component of the first planetary gear train 100 is connected to two rotating components of the second planetary gear train 200. Specifically, the first sun gear S1 is connected to the second planet carrier C2, and the first ring gear R1 and the second ring gear R2 are both connected to the input shaft Tin. It can be seen that it is also possible to connect the first sun gear S1 and the second ring gear R2, and connect the second planet carrier C2 and the input shaft Tin. In comparison, connecting the first sun gear S1 and the second planet carrier C2, and connecting the first ring gear R1 and the second ring gear R2 is simpler in structure.

[0168] It should be noted that in the above-mentioned multiple embodiments, the first planetary gear train 100 is a compound planetary gear train. Thus, on the basis of differential shunt, idle gear shunt is further carried out, which can preferably improve the torque density and increase the transmission speed ratio. However, it can be known that the first planetary gear train 100 can also be a simple planetary gear train, that is, the same structure as the second planetary gear train 200 and the third planetary gear train 300 can be adopted.

[0169] The embodiment of the present application also provides a wind turbine generator, including a blade hub, a main shaft and a gearbox 1000. The gearbox 1000 is the gearbox 1000 described in any of the above embodiments. The input shaft Tin of the gearbox 1000 is connected to the main shaft, and the main shaft is connected to the blade hub. Then the gearbox 1000 is connected through the main shaft and the blade hub, and the output shaft Tout of the gearbox 1000 outputs power.

[0170] During the operation of the wind turbine generator, the power and torque of the blade hub are transmitted to the input shaft Tin of the gearbox 1000 through the main shaft system and then transmitted to the generator through the gearbox 1000. The power and torque transmission path is as follows: The input shaft Tin transmits power and torque to the first ring gear R1, the second ring gear R2, and the third planet carrier C3 or the third ring gear R3. The first ring gear R1, the second ring gear R2 and the third planet carrier C3 (or the third ring gear R3) share the input torque load in a certain proportion. Among them, the torque shared by the first ring gear R1 accounts for a relatively large proportion. The torque borne by the first ring gear R1 is evenly distributed to the planetary idle gear P again D and the small planet gear P S on these two groups of planet gears. The small planet gear P S transmits the torque it bears to the large planet gear P in the rear row L subsequently driving the first sun gear S1 and the second planet carrier C2 of the second planetary gear train 200 connected thereto. The first planet carrier C1 and the fourth planet carrier C1' are distributed front and back. The gearbox 1000 provides a reaction torque for balancing the input and output torque loads, and this reaction torque is shared by the first planet carrier C1 in the front row and the fourth planet carrier C1' in the rear row of the first planetary gear train 100 in a certain proportion.

[0171] Specific examples are used in this article to elaborate on the principles and implementation manners of the present invention. The description of the above embodiments is only used to help understand the method and its core idea of the present invention. It should be noted that for those of ordinary skill in the art in this technical field, without departing from the principle of the present invention, several improvements and modifications can be made to the present invention, and these improvements and modifications also fall within the protection scope of the claims of the present invention.

Claims

1. A gearbox, characterized in that, It includes a first planetary gear train, a second planetary gear train, and a third planetary gear train; The first planetary gear train includes a first ring gear and a first sun gear; the first ring gear is connected to the input shaft of the gearbox; The second planetary gear train includes a second ring gear, second planet gears, a second planet carrier, and a second sun gear. One of the second ring gear and the second planet carrier is connected to the input shaft, and the other is connected to the first sun gear; The third planetary gear train includes a third ring gear, third planet gears, a third planet carrier, and a third sun gear. One of the third ring gear and the third planet carrier is connected to the input shaft, and the other is connected to the second sun gear; the third sun gear is connected to the output shaft of the gearbox.

2. The gearbox according to claim 1, characterized in that The third planet carrier is connected to the input shaft, and the third ring gear is connected to the second sun gear; the second planetary gear train is located at one axial end of the first planetary gear train, and the third planetary gear train is located at the other axial end of the first planetary gear train; the input shaft passes through the second planetary gear train and the first planetary gear train and is connected to the third planet carrier.

3. The gearbox according to claim 1, characterized in that, The third planetary gear train, the second planetary gear train, and the first planetary gear train are arranged axially in sequence, and the third planetary gear train is arranged close to the input shaft. The output shaft passes through the first planetary gear train and the second planetary gear train and is connected to the third sun gear.

4. The gearbox according to any one of claims 1-3, characterized in that, The first planetary gear train includes a first planetary gear set, a sun idler gear, a planet idler gear, a first planet carrier, and a fourth planet carrier. The first planetary gear set includes a small planet gear and a large planet gear that are coaxially and floatingly connected axially. The planet idler gear is mounted on the first planet carrier, and the large planet gear is mounted on the fourth planet carrier; both the planet idler gear and the small planet gear are in internal meshing with the first ring gear and in external meshing with the sun idler gear; the large planet gear is in external meshing with the first sun gear.

5. The gearbox according to claim 4, characterized in that, The second ring gear is connected to the input shaft, and the second planet carrier is connected to the first sun gear; the third planet carrier is connected to the input shaft, and the third ring gear is connected to the second sun gear.

6. The gearbox according to claim 5, characterized in that, The torque borne by the first ring gear is greater than the torques borne by the second ring gear and the third planet carrier, and the proportions of the first ring gear, the second ring gear, and the third planet carrier in the input torque load are respectively: Where: SR = (K1 + 1)(K2 + 1)K3 + 1 K1 = K 1A ·K 1B Among them, T R1 , T R2 , T C3 are the torques borne by the first ring gear, the second ring gear and the third planet carrier respectively, Tin is the torque of the input shaft, ZR1, ZR2 and ZR3 are the number of teeth of the first ring gear, the second ring gear and the third ring gear respectively; ZS1, ZS2 and ZS3 are the number of teeth of the first sun gear, the second sun gear and the third sun gear respectively; ZPS and ZPL are the number of teeth of the small planet gear and the large planet gear respectively.

7. The gearbox according to claim 5, characterized in that The number of the small planet gears is equal to the number of the planet idler gears; the proportion of the balanced torque borne by the first planet carrier and the fourth planet carrier in the input torque is: Where: SR = (K1 + 1)(K2 + 1)K3 + 1 K1 = K 1A ·K 1B Among them, T C1 and T C1’ are the balance torques provided for the first planet carrier and the fourth planet carrier respectively, Tin is the torque of the input shaft; ZR1, ZR2 and ZR3 are the number of teeth of the first ring gear, the second ring gear and the third ring gear respectively; ZS1, ZS2 and ZS3 are the number of teeth of the first sun gear, the second sun gear and the third sun gear respectively; ZPS and ZPL are the number of teeth of the small planet gear and the large planet gear respectively.

8. The gearbox according to claim 4, characterized in that The second ring gear is connected to the input shaft, and the second planet carrier is connected to the first sun gear; the third ring gear is connected to the input shaft, and the third planet carrier is connected to the second sun gear.

9. The gearbox according to claim 8, characterized in that, The torque borne by the first ring gear is greater than the torques borne by the second ring gear and the third ring gear, and the proportions of the first ring gear, the second ring gear, and the third ring gear in the input torque load are respectively: Where: SR = (K1 + 1)(K2 + 1)(K3 + 1) - 1 K1 = K 1A ·K 1B Among them, T R1 , T R2 , T R3 are the torques borne by the first ring gear, the second ring gear, and the third ring gear respectively, Tin is the torque of the input shaft, ZR1, ZR2, and ZR3 are the number of teeth of the first ring gear, the second ring gear, and the third ring gear respectively; ZS1, ZS2, and ZS3 are the number of teeth of the first sun gear, the second sun gear, and the third sun gear respectively; ZPS and ZPL are the number of teeth of the small planet gear and the large planet gear respectively.

10. The gearbox according to claim 8, characterized in that, The number of the small planet gears is equal to the number of the planet idle gears; the proportion of the balanced torque borne by the first planet carrier and the fourth planet carrier to the input torque is as follows: In the formula: In the formula: SR = (K1 + 1)(K2 + 1)(K3 + 1) - 1 K1 = K 1A ·K 1B where T C1 and T C1’ are the balancing torques provided for the first planet carrier and the fourth planet carrier respectively, Tin is the torque of the input shaft; ZR1, ZR2 and ZR3 are the number of teeth of the first ring gear, the second ring gear and the third ring gear respectively; ZS1, ZS2 and ZS3 are the number of teeth of the first sun gear, the second sun gear and the third sun gear respectively; ZPS and ZPL are the number of teeth of the small planet gear and the large planet gear respectively.

11. The gearbox according to any one of claims 4 to 10, characterized in that, The planet idle gears are supported on the first planet carrier through the first bearings, and the large planet gears of the first planet gear set are supported on the fourth planet carrier through the second bearings; the first bearings are rolling bearings or sliding bearings, and the outer raceway rings of the rolling bearings are integrated with the corresponding planet idle gears; the second bearings are rolling bearings.

12. The gearbox according to claim 11, characterized in that, The first planetary gear train includes a plurality of the first planet gear sets, and at least two of the large planet gears are axially offset and at least partially overlap in the axial projection.

13. The gearbox according to any one of claims 4 to 10, characterized in that The small planet gears can float circumferentially relative to the fourth planet carrier.

14. The gearbox according to claim 13, wherein The floating amount of the planet idle gears circumferentially relative to the first planet carrier is less than the floating amount of the small planet gears circumferentially relative to the fourth planet carrier.

15. A wind turbine generator, comprising a blade hub, a main shaft and a gearbox, characterized in that, The gearbox is the gearbox according to any one of claims 1-14, and the input shaft of the gearbox is connected to the blade hub through the main shaft.

Images