Gear shifting device, transmission mechanism and wind turbine generator set

Abstract

This application discloses a gear transmission device, which includes a first planetary gear train. The first planetary gear train includes a first ring gear, a first planet carrier, first planet gears, a sun idler gear, and planet idler gears. Both the planet idler gears and the first planet gears are mounted on the first planet carrier. Each first planet gear includes a pinion and a large gear coaxially connected to the pinion. Both the planet idler gear and the pinion mesh internally with the first ring gear and externally with the sun idler gear. The pinion can float radially relative to the first planet carrier, with the maximum radial float of the pinion being greater than the maximum radial float of the planet idler gear. At least two of the large gears of the first planet gears are axially staggered and their projections overlap on a plane perpendicular to the axial direction. This gear transmission device has a high torque load density and can balance small size, large transmission ratio, and high torque load capacity.

Description

Technical Field

[0001] This invention relates to a gear transmission device that can be used in the transmission mechanism of a wind turbine generator set to increase the rotational speed of the blade hub to a speed suitable for the operation of the wind turbine generator set. It can also be widely used in other industrial equipment. Background Technology

[0002] Traditional wind turbine generators use gear transmission devices to convert the low-speed but high-torque power of the main shaft into high-speed, low-torque power that is more conducive to generator power generation.

[0003] Traditional wind turbine gear transmission systems use a simple planetary gear train, consisting of a sun gear, planetary gear carrier, planetary gears, and a ring gear. This type of planetary gear train experiences significant torque during transmission, limiting its overall torque load capacity and failing to meet high torque load requirements.

[0004] Increasing the number of planetary gears can improve torque load capacity, but this leads to a larger size of the gear transmission, which is not suitable for use in equipment with very limited space, such as wind turbine generators. On the other hand, to accommodate more planetary gears without changing the size of the gear transmission, the size of the gears needs to be reduced, which in turn leads to a smaller transmission ratio, failing to meet the high transmission ratio requirements of wind turbine generators.

[0005] Therefore, simply increasing the number of planetary gears to improve torque load capacity cannot meet the requirements of small size and large transmission ratio, and is therefore not ideal.

[0006] Application content

[0007] To address the aforementioned technical problems, this application provides a gear transmission device comprising a first planetary gear train, which includes a first ring gear, a first planet carrier, first planet gears, a sun idler gear, and planet idler gears. The planet idler gears and the first planet gears are both mounted on the first planet carrier. The first planet gears include pinions. Both the planet idler gears and the pinions mesh internally with the first ring gear and externally with the sun idler gear. The pinions are capable of floating radially relative to the first planet carrier.

[0008] In one embodiment of the gear transmission device, the planetary idler gear cannot float radially relative to the first planetary carrier, or the planetary idler gear can float radially relative to the first planetary carrier and the maximum radial float of the planetary idler gear is less than the maximum radial float of the first planetary gear.

[0009] In one embodiment of the gear transmission device, the first planetary gear train further includes a first sun gear; the first planetary gear also includes a large gear and a connecting shaft, the diameter of the large gear is larger than the diameter of the small gear, and the large gear and the small gear are axially offset from each other and achieve coaxial transmission through the connecting shaft.

[0010] In one embodiment of a gear transmission device, the large gear meshes externally with the first sun gear; the number of the first planet gears is multiple, wherein at least two of the large gears of the first planet gears are offset from each other along the axial direction and their projected portions overlap in a plane perpendicular to the axial direction.

[0011] In one embodiment of the gear transmission device, a first bearing is provided between the first planetary gear and the first planetary carrier.

[0012] In one embodiment of the gear transmission device, the first bearing is a self-aligning bearing, which enables the pinion to float radially relative to the first planetary carrier; and / or,

[0013] The connecting shaft includes a first shaft segment connected to the pinion and a second shaft segment connected to the large gear. The first and second shaft segments are connected by a radially movable coupling, thereby enabling the pinion to float radially relative to the first planetary carrier; and / or

[0014] The connecting shaft is a flexible shaft that can deform radially, thereby enabling the pinion to float radially relative to the first planetary carrier.

[0015] In one embodiment of the gear transmission device, the first bearing is disposed at one end near the large gear.

[0016] In one embodiment of the gear transmission device, the first planetary carrier includes a base and a base plate connected to one end of the base. The base has a base plate, and a first accommodating space for accommodating the large gear is formed between the base plate and the base plate. Both the base plate and the base plate are provided with bearing seat holes for mounting the first bearing. A portion of the first planetary gears are supported on the base plate by the first bearing, and another portion of the first planetary gears are supported on the base plate by the first bearing.

[0017] In one embodiment of the gear transmission device, the base further includes an end cover connected to the other end of the base. The end cover has an end cover plate, and a second accommodating space for accommodating the planetary idler gear and the pinion is formed between the end cover plate and the base plate. The planetary idler gear is fitted onto a planetary idler gear shaft, and a second bearing is provided between the planetary idler gear and the planetary idler gear shaft. One end of the planetary idler gear shaft is connected to the end cover plate, and the other end is connected to the base plate. One end of the connecting shaft of the first planetary gear extends into the second accommodating space, and the pinion is fitted onto that end of the connecting shaft.

[0018] In one embodiment of the gear transmission device, the end cover further has an input shaft, one end of which is connected to the end cover plate, and the other end extends axially away from the end cover plate.

[0019] In one embodiment of the gear transmission device, the ratio P = torque of the planetary idler gear / torque of the first planetary gear, and the range of the ratio P is: 1 < P ≤ K, where K = pitch circle radius of the large gear / pitch circle radius of the small gear.

[0020] In one embodiment of the gear transmission device, the number of planetary idler gears is the same as the number of the first planetary gears, and each of the planetary idler gears and each of the first planetary gears are arranged alternately at equal intervals along the circumference of the first gear ring.

[0021] One embodiment of the gear transmission device further includes one or more stages of a second planetary gear train. The second planetary gear train includes a second ring gear, a second planet carrier, second planet gears, and a second sun gear. The second planet gears are mounted on the second planet carrier. The second planet gears mesh internally with the second ring gear and externally with the second sun gear. The second planet carrier is connected to the first sun gear or the second sun gear of the previous stage for transmission.

[0022] In one embodiment of the gear transmission device, the second planetary carrier includes two mounting plates spaced apart along the axial direction, forming a receiving space between the two mounting plates for accommodating the second planetary gear, the second planetary gear being fitted onto a second planetary gear shaft, a third bearing being provided between the second planetary gear and the second planetary gear shaft, and the two ends of the second planetary gear shaft being respectively connected to the two mounting plates.

[0023] In one embodiment of the gear transmission device, the second planetary carrier includes a connecting sleeve, one end of which is connected to a mounting plate, and the other end extends axially toward the first sun gear or the second sun gear of the previous stage, wherein the first sun gear or the second sun gear of the previous stage is connected to the connecting sleeve.

[0024] One embodiment of a gear transmission device includes a housing, a first gear ring and a second gear ring both fixed to the housing, a first planetary carrier and a second planetary carrier both at least partially installed inside the housing, the first planetary carrier being supported by a fourth bearing on the housing, and the second planetary carrier being supported by a fifth bearing on the housing.

[0025] In one embodiment of the gear transmission device, a torque arm with a balancing function is provided on the outer periphery of the housing, and the housing is also provided with a flange plate, through which the connection and fixation with external equipment is realized.

[0026] The various embodiments of the gear transmission device described above can be combined arbitrarily without conflict.

[0027] On the other hand, this application provides a transmission mechanism, which includes the gear transmission device described in any of the above claims.

[0028] In another aspect, this application also provides a wind turbine generator set, which includes a blade hub and a transmission mechanism, wherein the transmission mechanism adopts the aforementioned transmission mechanism.

[0029] The planetary idler gear and pinion of the gear transmission device provided in this application can share the torque, and the torque shared by the planetary idler gear is greater than that shared by the pinion gear (that is, the ratio P of the torque shared by the planetary idler gear to that shared by the pinion gear is greater than 1). Therefore, the torque load on the pinion gear can be reduced and the torque load capacity of the entire first planetary gear train can be improved.

[0030] Moreover, since the torque load of the pinion is reduced, even if a smaller pinion is used, the load-bearing requirements can be met. Therefore, more pinions can be arranged under the same volume conditions, so the torque load capacity of the entire first planetary gear system can be further improved by increasing the number of pinions while taking into account the small volume. Thus, it has a high torque load density.

[0031] In one embodiment of the gear transmission device described above, by arranging the large gears of at least two first planetary gears axially offset and having their projections partially overlap on a plane perpendicular to the axial direction, the gear transmission device can achieve both small size and large transmission ratio.

[0032] The transmission mechanism and wind turbine generator set provided in this application also have the above-mentioned technical effects because they include the aforementioned gear transmission device. Attached Figure Description

[0033] Figure 1 A disassembled schematic diagram of the first planetary gear train of one embodiment of the gear transmission device provided in this application;

[0034] Figure 2 for Figure 1 A cross-sectional view of the first planetary carrier;

[0035] Figure 3 A cross-sectional view of an embodiment of the gear transmission device provided in this application, in its assembled state, with the cutting line along... Figure 1 AA;

[0036] Figure 4 for Figure 3 The gear transmission device shown is a cross-sectional view from another perspective, with the cutting line along... Figure 1 BB;

[0037] Figure 5 for Figure 3 An overall view of the gear transmission device shown;

[0038] Figure 6 Force analysis diagram for when the floating amount of the pinion is sufficiently large;

[0039] Figure 7 A disassembled schematic diagram of the second planetary gear train of one embodiment of the gear transmission device provided in this application;

[0040] Figure 8 and Figure 9 This is a simplified diagram of the transmission path of one embodiment of the gear transmission device provided in this application.

[0041] The annotations in the attached figures are explained as follows:

[0042] 100 First Planetary Gear System;

[0043] 101 First gear ring;

[0044] 102 First planetary carrier, 1021 base, 1021a base plate, 1021b support ring, 1021c support arm, 1022 base plate, 1023 end cover, 1023a end cover plate, 1023b input shaft, A bearing connection part, B bearing seat hole.

[0045] 103 First planetary gear, 103a Small gear, 103b Large gear, 103c Connecting shaft;

[0046] 104 Sun idler gear; 105 Planetary idler gear; 106 First sun gear; 107 First bearing; 108 Planetary idler gear shaft; 109 Second bearing.

[0047] 200 Second Planetary Gear Train;

[0048] 201 Second gear ring;

[0049] 202 Second planetary carrier, 202a Mounting plate, 202b Connecting arm, 202c Connecting sleeve;

[0050] 203 Second planetary gear; 204 Second planetary gear shaft; 205 Third bearing;

[0051] 206 Second Sun Gear;

[0052] 207 output shaft.

[0053] 300 housing, 300a torque arm, 300b flange plate.

[0054] 400 Fourth Bearing.

[0055] 500 Fifth Bearing. Detailed Implementation

[0056] To enable those skilled in the art to better understand the technical solution of this application, the technical solution of this application will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0057] like Figure 1 The gear transmission device includes a first planetary gear train 100.

[0058] The first planetary gear train 100 includes a first gear ring 101, a first planet carrier 102, a first planet gear 103, a sun idler gear 104, and a planet idler gear 105.

[0059] The first planetary gear 103 includes a pinion 103a, which is mounted between the first gear ring 101 and the sun idler gear 104. The pinion 103a meshes internally with the first gear ring 101 and externally with the sun idler gear 104.

[0060] Planetary idler gear 105 is also installed between the first gear ring 101 and the sun idler gear 104. Planetary idler gear 105 meshes internally with the first gear ring 101 and externally with the sun idler gear 104. Planetary idler gear 105 directly transmits torque only with the first gear ring 101 and the sun idler gear 104. Sun idler gear 104 directly transmits torque only with planetary idler gear 105 and pinion 103a.

[0061] Both the first planetary gear 103 and the planetary idler gear 105 are supported and mounted on the first planetary carrier 102. After installation, the pinion 103a of the first planetary gear 103 can float radially relative to the first planetary carrier 102 (the radial direction of the pinion 103a). The planetary idler gear 105 cannot float radially relative to the first planetary carrier 102 (the radial direction of the planetary idler gear 105), or the planetary idler gear 105 can float radially relative to the first planetary carrier 102 with a maximum radial float less than the maximum radial float of the first planetary gear 103.

[0062] With the above floating design, when the first planetary carrier 102 rotates around the axis under the action of the input torque (at which time the first gear ring 101 is fixed), at least part of the torque will be transmitted to the planetary idler gear 105 first, and then transmitted from the planetary idler gear 105 to the pinion 103a of the first planetary gear 103 via the sun idler gear 104. This allows the planetary idler gear 105 and the pinion 103a to share the torque, and the torque shared by the planetary idler gear 105 is greater than that shared by the pinion 103a (that is, the ratio P of the torque shared by the planetary idler gear 105 to that shared by the pinion 103a is greater than 1). Therefore, the torque load on the pinion 103a can be reduced, and the torque load capacity of the entire first planetary gear train 100 can be improved.

[0063] Moreover, since the torque load of the pinion 103a is reduced, even if a smaller pinion 103a is used, the load-bearing requirements can be met. Therefore, more pinions 103a can be arranged under the same volume conditions, so that the torque load capacity of the entire first planetary gear train 100 can be further improved by increasing the number of pinions 103a while taking into account the small volume, thereby achieving a higher torque load density.

[0064] Furthermore, the first planetary gear train 100 also includes a first sun gear 106. The first planetary gear 103 also includes a large gear 103b and a connecting shaft 103c. The diameter of the large gear 103b is larger than the diameter of the small gear 103a, and the large gear 103b and the small gear 103a are offset from each other axially and are coaxially connected by the connecting shaft 103c.

[0065] The large gear 103b of the first planetary gear 103 meshes externally with the first sun gear 106, thereby further transmitting torque to the first sun gear 106 for torque output. Since the diameter of the large gear 103b is larger than the diameter of the small gear 103a, the torque output through the meshing of the large gear 103b with the first sun gear 106 enables the first planetary gear train 100 to achieve a larger transmission ratio.

[0066] When there are multiple (two or more) first planetary gears 103, the large gears 103b of at least two first planetary gears 103 are staggered along the axial direction and their projected portions overlap in a plane perpendicular to the axial direction. This arrangement allows for a larger size of the large gears 103b under the same volume conditions, thereby enabling the first planetary gear train 100 to obtain a larger transmission ratio.

[0067] Specifically, the large gears 103b of the two first planetary gears 103 can be offset from each other axially by setting the connecting shafts 103c of the two first planetary gears 103 to different lengths.

[0068] By adopting the above-mentioned floating design and having the large gears 103b of at least two first planetary gears 103 staggered along the axial direction and partially overlapping in 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, thus solving the problem that traditional gear transmission devices cannot take all three into account.

[0069] Specifically, such as Figure 4 A first bearing 107 is provided between the first planetary gear 103 and the first planetary carrier 102 so that the first planetary gear 103 can rotate relative to the first planetary carrier 102 around its own axis when the first planetary carrier 102 rotates.

[0070] Specifically, there are various ways to enable the pinion 103a of the first planetary gear 103 to float radially relative to the first planetary carrier 102.

[0071] For example, one approach is to use a self-aligning bearing for the first bearing 107, and to use the self-aligning angle of the self-aligning bearing to achieve radial floating of the pinion 103a. The magnitude of the maximum radial floating is related to the magnitude of the self-aligning angle.

[0072] In this implementation, it is preferable to place the self-aligning bearing at the end closer to the large gear 103b or at the end farther away from the small gear 103a. This ensures that the small gear 103a maintains good meshing with the sun idler gear 104 and the first gear ring 101 during the floating process.

[0073] For example, one approach is to segment the connecting shaft 103c, which includes a first shaft segment connected to the pinion 103a and a second shaft segment connected to the gear 103b. The first and second shaft segments are connected by a coupling that can move radially.

[0074] For example, one approach is to use a flexible shaft that can deform radially for the connecting shaft 103c.

[0075] For example, any combination of two or more of the above methods can be used.

[0076] Specifically, the magnitude of the maximum radial float of the pinion 103a is related to the ratio P of the torque shared by the planetary idler gear 105 and the torque shared by the pinion 103a.

[0077] When the maximum radial float of the pinion 103a is large enough, all the torque will first be transmitted to the planetary idler gear 105, and then from the planetary idler gear 105 to the pinion 103a of the first planetary gear 103 via the sun idler gear 104. At this time, as... Figure 5As shown, the force 2F on the planetary idler gear 105 is equal to the force F0 × K on the pinion 103a, where K = the pitch circle radius of the gear 103b / the pitch circle radius of the pinion 103a. In other words, when the maximum radial float of the pinion 103a is sufficiently large, the ratio of the torque shared by the planetary idler gear 105 to the torque shared by the pinion 103a is P = K.

[0078] Of course, the maximum radial float of the pinion 103a can be flexibly set according to actual needs, as long as the ratio P of the torque shared by the planetary idler gear 105 and the torque shared by the pinion 103a is satisfied: 1 < P ≤ K.

[0079] Specifically, such as Figure 1 The number of planetary idler gears 105 can be set to be the same as the number of first planetary gears 103, and the planetary idler gears 105 and the first planetary gears 103 can be arranged alternately at equal intervals along the circumference of the first gear ring 101. In this way, the overall force of the first planetary gear train 100 is more balanced, the transmission is smoother, and the service life is longer.

[0080] Specifically, such as Figure 1 and Figure 2 The first planetary carrier 102 includes a base 1021 and a base plate 1022. The base 1021 has a base plate 1021a and a support arm 1021c, one end of the support arm 1021c is connected to the base plate 1021a, and the other end is connected to the base plate 1022.

[0081] A first accommodating space for accommodating the large gear 103b is formed between the base plate 1021a and the bottom plate 1022. Both the base plate 1021a and the bottom plate 1022 are provided with bearing seat holes B for mounting the first bearing 107.

[0082] like Figure 3 The longer first planetary gear 103 of the connecting shaft 103c is supported and connected to the base plate 1021a by a first bearing 107. The shorter first planetary gear 103 of the connecting shaft 103c is supported and connected to the base plate 1022 by a first bearing 107. This satisfies the installation requirement that the large gears 103b of at least two first planetary gears 103 be staggered axially, and also satisfies the requirement that the first bearing 107 be installed close to the large gear 103b.

[0083] Specifically, such as Figure 1 and Figure 2The first planetary carrier 102 also includes an end cap 1023. The end cap 1023 has an end cap plate 1023a. The base 1021 also includes a support ring 1021b, one end of which is connected to the base plate 1021a, and the other end is connected to the end cap plate 1023a by fasteners. A second receiving space is formed between the end cap plate 1023a and the base plate 1021a for accommodating the planetary idler gear 105 and the pinion 103a.

[0084] like Figure 3 One end of the connecting shaft 103c of the first planetary gear 103 extends into the second accommodating space, and the pinion 103a is fitted onto that end of the connecting shaft 103c. This satisfies the installation requirements of the planetary idler gear 105 and the pinion 103a.

[0085] like Figure 4 The planetary idler gear 105 is mounted on the planetary idler gear shaft 108, and a second bearing 109 is provided between the planetary idler gear 105 and the planetary idler gear shaft 108. One end of the planetary idler gear shaft 108 is connected to the end cover plate 1023a, and the other end is connected to the base plate 1021a.

[0086] Specifically, such as Figure 1 and Figure 2 The first planetary carrier 102 is also provided with a bearing connection part A. In the illustrated embodiment, a bearing connection part A is provided at one end of the first planetary carrier 102 where the end cap 1023 is located and at one end of the base plate 1022.

[0087] like Figure 3 The first planetary carrier 102 is at least partially installed inside the housing 300. A fourth bearing 400 is fitted on each of the two bearing connection parts A at both ends of the first planetary carrier 102, and is supported on the bearing mounting surface of the housing 300 by the fourth bearing 400.

[0088] Specifically, such as Figure 3 The end cover 1023 of the first planetary carrier 102 also has an input shaft 1023b, one end of which is connected to the end cover plate 1023a, and the other end extends axially away from the end cover plate 1023a and extends out of one end port of the housing 300 for torque introduction by an external drive device.

[0089] The first planetary carrier 102 with the above structure can meet the assembly requirements with the first planetary gear 103, the planetary idler gear 105, and the outer casing 300, and it is small in size and highly integrated. Of course, the structure of the first planetary carrier 102 can be flexibly set according to actual needs, and is not limited to the above structure, as long as the structure can meet the assembly requirements with the first planetary gear 103, the planetary idler gear 105, and the outer casing 300.

[0090] Specifically, such as Figure 5The outer periphery of the housing 300 can be provided with a torque arm 300a for balancing purposes. The housing 300 can also be provided with a flange plate 300b, which is used to connect and fix it to external equipment.

[0091] Furthermore, such as Figure 7 As shown, the gear transmission device can also be equipped with a second planetary gear train 200, which includes a second ring gear 201, a second planet carrier 202, a second planet gear 203, and a second sun gear 206.

[0092] The second planetary gear 203 is mounted on the second planetary carrier 202. The second planetary gear 203 is mounted between the second ring gear 201 and the second sun gear 206. The second planetary gear 203 meshes internally with the second ring gear 201 and externally with the second sun gear 206.

[0093] Specifically, a single-stage second planetary gear train 200 can be set, or multiple stages (two or more stages) of second planetary gear train 200 can be set. When multiple stages of second planetary gear train 200 are set, each stage of the second planetary gear train 200 is arranged sequentially along the axial direction. The second planet carrier 202 of the next stage of the second planetary gear train 200 is connected to the second sun gear 206 of the previous stage of the second planetary gear train 200 for transmission.

[0094] Specifically, such as Figure 7 The second planetary carrier 202 includes two mounting plates 202a spaced apart along the axial direction and a connecting arm 202b connecting the two mounting plates 202a. A receiving space for accommodating the second planetary gear 203 is formed between the two mounting plates 202a.

[0095] like Figure 3 The second planetary gear 203 is mounted on the second planetary gear shaft 204. A third bearing 205 is provided between the second planetary gear 203 and the second planetary gear shaft 204. Both ends of the second planetary gear shaft 204 are connected to two mounting plates 202a respectively. This satisfies the installation requirements of the second planetary gear 203.

[0096] Specifically, such as Figure 7 The second planetary carrier 202 may further include a connecting sleeve 202c, one end of which is connected to a mounting plate 202a, and the other end extends axially toward the first sun gear 106 or the second sun gear 206 of the preceding stage. The connecting sleeve 202c is used to connect the first sun gear 106 or the second sun gear 206 of the preceding stage. The second sun gear 206 of the final stage is connected to an output shaft 207, which transmits torque to external devices.

[0097] Specifically, such as Figure 7The second planetary carrier 202 is also provided with a bearing connection part A. In the illustrated embodiment, a bearing connection part A is provided at one end of the second planetary carrier 202 where the connecting sleeve 202c is located and at the other end where the mounting plate 202a is located away from the connecting sleeve 202c. Figure 7 (Only one is visible in the middle). The second planetary carrier 202 is at least partially installed inside the housing 300. Each of the two bearing connection parts A at both ends of the second planetary carrier 202 is fitted with a fifth bearing 500, which supports the bearing mounting surface of the housing 300.

[0098] The second planetary carrier 202 with the above-described structure can meet the assembly requirements with the second planetary gear 203 and the outer casing 300, and it is small in size and highly integrated. Of course, the structure of the second planetary carrier 202 can be flexibly set according to actual needs, and is not limited to the above-described structure, as long as the structure can meet the assembly requirements with the second planetary gear 203 and the outer casing 300.

[0099] like Figure 8 and Figure 9 The transmission path of the gearbox in this embodiment is:

[0100] The input torque acts on the first planetary carrier 102, driving it to rotate. The first planetary carrier 102 distributes the torque P proportionally to the planetary idler gear 105 and the pinion 103a of the first planetary gear 103, causing the planetary idler gear 105 and the pinion 103a to rotate on their own axes while revolving around the first planetary carrier 102. During the torque distribution process, at least a portion of the torque is first transmitted to the planetary idler gear 105, then from the planetary idler gear 105 to the sun idler gear 104, and finally from the sun idler gear 104 to the pinion 103a of the first planetary gear 103.

[0101] Each pinion 103a transmits the torque load it receives to the connected large gear 103b. Each large gear 103b further transmits the torque to the first sun gear 106, and the large gears 103b together drive the first sun gear 106 and the connected second planet carrier 202 to rotate.

[0102] The second planetary carrier 202 transmits torque to the second planetary gear 203, which in turn transmits it to the second sun gear 206 and the output shaft 207 connected thereto. The output shaft 207 then transmits the torque to external devices.

[0103] In summary, the core idea of ​​this application is to make the maximum radial float of the pinion 103a of the first planetary gear 103 greater than the maximum radial float of the planetary idler gear 105 (if it does not float, the maximum radial float is zero), thereby utilizing the planetary idler gear 105 to share the torque and reduce the torque load borne by the first planetary gear 103. This achieves a balance between small size and high torque load capacity, resulting in a high torque load density. Furthermore, by arranging at least two large gears 103b of the first planetary gears 103 axially staggered and with their projected portions overlapping on a plane perpendicular to the axial direction, a balance between small size and a large transmission ratio is achieved.

[0104] The above examples illustrate the principles and implementation methods of this application. The descriptions of these embodiments are merely for the purpose of helping to understand the method and core ideas of this application. It should be noted that those skilled in the art can make various improvements and modifications to this application without departing from its principles, and these improvements and modifications also fall within the protection scope of the claims of this application.

Claims

1. A gear transmission device, characterized in that, The gear transmission device includes a first planetary gear train (100), which includes a first ring gear (101), a first planet carrier (102), first planet gears (103), a sun idler gear (104), and a planet idler gear (105). The planet idler gear (105) and the first planet gear (103) are both mounted on the first planet carrier (102). The first planet gear (103) includes a pinion (103a). The planet idler gear (105) and the pinion (103a) are both internally meshed with the first ring gear (101) and externally meshed with the sun idler gear (104). The pinion (103a) can float radially relative to the first planet carrier (102). The number of the first planetary gears (103) is multiple, and the first planetary gears (103) also include a large gear (103b) coaxially connected to the small gear (103a), and the large gears (103b) of at least two of the first planetary gears (103) are offset from each other along the axial direction; At least two of the large gears (103b) that are axially offset from each other are provided with extensions, wherein the extension of the large gear (103b) that is relatively closer to the input end extends toward the small gear (103a), and the extension of the large gear (103b) that is relatively farther away from the input end extends away from the small gear (103a), and a first bearing (107) is provided between the extension and the first planetary carrier (102).

2. The gear transmission device according to claim 1, characterized in that, The planetary idler wheel (105) cannot float radially relative to the first planetary carrier (102), or the planetary idler wheel (105) can float radially relative to the first planetary carrier (102) and the maximum radial float of the planetary idler wheel (105) is less than the maximum radial float of the first planetary wheel (103).

3. The gear transmission device according to claim 2, characterized in that, The first planetary gear train (100) further includes a first sun gear (106); the first planet gear (103) further includes a connecting shaft (103c), the diameter of the large gear (103b) is larger than the diameter of the small gear (103a), the large gear (103b) and the small gear (103a) are offset from each other along the axial direction and are coaxially connected through the connecting shaft (103c).

4. The gear transmission device according to claim 3, characterized in that, The large gear (103b) meshes externally with the first sun gear (106); the large gears (103b) which are offset from each other along the axial direction partially overlap in a plane perpendicular to the axial direction.

5. The gear transmission device according to claim 3, characterized in that, The first bearing (107) is a self-aligning bearing, which enables the pinion (103a) to float radially; and / or, The connecting shaft (103c) includes a first shaft segment connected to the pinion (103a) and a second shaft segment connected to the large gear (103b). The first shaft segment and the second shaft segment are connected by a radially movable coupling, thereby enabling the pinion (103a) to float radially; and / or The connecting shaft (103c) is a flexible shaft that deforms radially, thereby enabling the pinion (103a) to float radially.

6. The gear transmission device according to claim 5, characterized in that, The first planetary carrier (102) includes a base (1021) and a base plate (1022) connected to one end of the base (1021). The base (1021) has a base plate (1021a). A first accommodating space for accommodating the large gear (103b) is formed between the base plate (1021a) and the base plate (1022). Both the base plate (1021a) and the base plate (1022) are provided with bearing seat holes (B) for mounting the first bearing (107). A portion of the first planetary gears (103) are supported on the base plate (1021a) through the first bearing (107), and another portion of the first planetary gears (103) are supported on the base plate (1022) through the first bearing (107).

7. The gear transmission device according to claim 6, characterized in that, The base (1021) further includes an end cap (1023) connected to the other end of the base (1021). The end cap (1023) has an end cap plate (1023a). A second receiving space for accommodating the planetary idler gear (105) and the pinion (103a) is formed between the end cap plate (1023a) and the base plate (1021a). The planetary idler gear (105) is fitted onto the planetary idler gear shaft (108) and... A second bearing (109) is provided between the planetary idler gear (105) and the planetary idler gear shaft (108). One end of the planetary idler gear shaft (108) is connected to the end cover plate (1023a) and the other end is connected to the base plate (1021a). One end of the connecting shaft (103c) of the first planetary gear (103) extends into the second accommodating space, and the pinion (103a) is fitted onto that end of the connecting shaft (103c).

8. The gear transmission device according to claim 7, characterized in that, The end cap (1023) also has an input shaft (1023b), one end of which is connected to the end cap plate (1023a), and the other end extends axially away from the end cap plate (1023a).

9. The gear transmission device according to any one of claims 3-5, characterized in that, The torque of the planetary idler gear (105) / the torque of the first planetary gear (103) = proportional P, wherein the range of proportional P is: 1 < P ≤ K, where K = pitch circle radius of the large gear (103b) / pitch circle radius of the small gear (103a).

10. The gear transmission device according to any one of claims 4-5, characterized in that, The number of planetary idler gears (105) is the same as the number of the first planetary gears (103), and each of the planetary idler gears (105) and each of the first planetary gears (103) are arranged alternately at equal intervals along the circumference of the first gear ring (101).

11. The gear transmission device according to any one of claims 3-5, characterized in that, The gear transmission device further includes one or more stages of a second planetary gear train (200). The second planetary gear train (200) includes a second ring gear (201), a second planetary carrier (202), a second planetary gear (203), and a second sun gear (206). The second planetary gear (203) is mounted on the second planetary carrier (202). The second planetary gear (203) meshes internally with the second ring gear (201) and externally with the second sun gear (206). The second planetary carrier (202) is connected to the first sun gear (106) or the second sun gear (206) of the previous stage.

12. The gear transmission device according to claim 11, characterized in that, The second planetary carrier (202) includes two mounting plates (202a) spaced apart along the axial direction. A receiving space for accommodating the second planetary gear (203) is formed between the two mounting plates (202a). The second planetary gear (203) is fitted onto a second planetary gear shaft (204). A third bearing (205) is provided between the second planetary gear (203) and the second planetary gear shaft (204). The two ends of the second planetary gear shaft (204) are respectively connected to the two mounting plates (202a).

13. The gear transmission device according to claim 12, characterized in that, The second planetary carrier (202) includes a connecting sleeve (202c), one end of which is connected to a mounting plate (202a), and the other end extends axially toward the first sun gear (106) or the second sun gear (206) of the previous stage, which is connected to the connecting sleeve (202c).

14. The gear transmission device according to claim 13, characterized in that, The gear transmission device includes a housing (300), the first gear ring (101) and the second gear ring (201) are both fixed to the housing (300), the first planetary carrier (102) and the second planetary carrier (202) are at least partially installed inside the housing (300), the first planetary carrier (102) is supported on the housing (300) by a fourth bearing (400), and the second planetary carrier (202) is supported on the housing (300) by a fifth bearing (500).

15. The gear transmission device according to claim 14, characterized in that, The outer periphery of the housing (300) is provided with a torque arm (300a) for balancing purposes. The housing (300) is also provided with a flange plate (300b) for connecting and fixing with external equipment.

16. A transmission mechanism, characterized in that, The transmission mechanism includes the gear transmission device according to any one of claims 1-15.

17. A wind turbine generator set, comprising blade hubs and a transmission mechanism, characterized in that, The transmission mechanism is the transmission mechanism of claim 16, wherein the gear transmission device of the transmission mechanism is connected to the blade hub to increase the speed of the blade hub to the target speed.

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