CN219317562U - Gear box and wind generating set - Google Patents
Gear box and wind generating set Download PDFInfo
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- CN219317562U CN219317562U CN202223576929.8U CN202223576929U CN219317562U CN 219317562 U CN219317562 U CN 219317562U CN 202223576929 U CN202223576929 U CN 202223576929U CN 219317562 U CN219317562 U CN 219317562U
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/70—Wind energy
- Y02E10/72—Wind turbines with rotation axis in wind direction
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Abstract
The utility model relates to a gear box and wind generating set, the gear box is used for cooperating with the main shaft transmission, and it includes base and drive assembly, and the base is formed with annular inner chamber, and drive assembly sets up in annular inner chamber and links to each other with the main shaft, and drive assembly includes the N level planetary gear train of the axial distribution along annular inner chamber, and N is greater than or equal to 2, and every level planetary gear train includes the driving flange as the input, as the sun gear of output to and be located ring gear, planet carrier and a plurality of planet gears of being connected on the planet carrier between driving flange and the sun gear. The at least two adjacent planetary gear trains comprise a first planetary gear train close to the main shaft and a second planetary gear train far away from the main shaft, one end of a driving flange of the second planetary gear train is connected with a sun gear of the first planetary gear train, supporting points are respectively formed on two sides of the first planetary gear train along the axial direction, and the other end of the driving flange of the second planetary gear train is connected with an inner gear ring of the second planetary gear train, so that the transmission reliability of the gearbox is improved.
Description
Technical Field
The application relates to the technical field of wind power, in particular to a gear box and a wind generating set.
Background
The wind generating set is a device for converting wind energy into electric energy, and is used as sustainable and renewable green energy, and the wind generating set is continuously developed to be large-scale.
The transmission system is a core component of the wind generating set, and the performance of the transmission system directly influences the whole cost of the fan, the reliability of the running of the set and the market competitiveness. The transmission system mainly comprises a main shaft which is in butt joint and a gear box which is connected with the main shaft, and as the power of the wind generating set is continuously increased, the transmission of each stage of planetary gear trains in the gear box generates larger unbalanced load and fluctuation load, so that the gear box has certain failure risk.
Disclosure of Invention
The embodiment of the application provides a gear box and wind generating set, can guarantee the equal load nature of ring gear and planet wheel meshing in the planetary gear train, improves the reliability of gear box transmission.
In one aspect, according to an embodiment of the present application, there is provided a gearbox for driving engagement with a main shaft, the gearbox comprising: a base formed with an annular cavity; the transmission assembly is arranged in the annular inner cavity and connected with the main shaft, the transmission assembly comprises N-level planetary gear trains distributed along the axial direction of the annular inner cavity, N is more than or equal to 2, and each level of planetary gear train comprises a driving flange serving as an input end, a sun gear serving as an output end, an annular gear, a planet carrier and a plurality of planet gears, wherein the annular gear, the planet carrier and the planet gears are positioned between the driving flange and the sun gear; the at least two adjacent planetary gear trains comprise a first planetary gear train close to the main shaft and a second planetary gear train far away from the main shaft, one end of a driving flange of the second planetary gear train is connected with a sun gear of the first planetary gear train, supporting points are respectively formed on two sides of the first planetary gear train along the axial direction, and the other end of the driving flange of the second planetary gear train is connected with an inner gear ring of the second planetary gear train.
According to an aspect of the embodiment of the application, the transmission assembly further comprises a first supporting piece and a second supporting piece which are distributed along the axial direction, wherein the first supporting piece and the second supporting piece are fixed at two ends of the planet carrier of the first planetary gear train along the axial direction and are respectively in running fit with the driving flange.
According to one aspect of the embodiments of the present application, the first support member and the second support member are rotatably connected to the driving flange by bearings, respectively.
According to one aspect of the embodiments of the present application, the driving flange of the first planetary gear train is connected to the ring gear of the first planetary gear train, and the carrier of the first planetary gear train is fixed to the base.
According to one aspect of the embodiments of the present application, the rim thickness of the ring gears of the first and second planetary gear trains is less than or equal to 5 times the modulus.
According to one aspect of an embodiment of the present application, a planet carrier of at least one of a first planetary gear train and a second planetary gear train includes an end wall and a flexpin assembly, the plurality of flexpin assemblies being disposed in a cantilevered configuration on the end wall and supporting a planet.
According to one aspect of the embodiment of the application, in the N-stage planetary gear train, the first-stage planetary gear train is set as a first planetary gear train, the second-stage planetary gear train is set as a second planetary gear train, and a driving flange of the first-stage planetary gear train is connected with the main shaft. The transmission assembly further comprises a connecting piece, one end of the connecting piece is connected with the main shaft, and the other end of the connecting piece is connected with the planet carrier of the second-stage planetary gear train.
According to one aspect of the embodiment of the application, the transmission assembly further comprises a third support member fixed to an end of the planet carrier of the second-stage planetary gear train facing away from the main shaft and in rotary engagement with the base in a radial direction of the annular inner cavity.
According to one aspect of the embodiment of the application, the at least two adjacent planetary gear trains comprise a third planetary gear train close to the main shaft and a fourth planetary gear train far away from the main shaft, an inner gear ring of the fourth planetary gear train is fixed on the base, one end of a driving flange of the fourth planetary gear train is connected with a sun gear of the third planetary gear train, and the other end of the driving flange of the fourth planetary gear train is connected with a planet carrier of the fourth planetary gear train.
In another aspect, according to an embodiment of the present application, there is provided a wind generating set, including a main shaft and a gear box disposed on one side of the main shaft along an axial direction of the main shaft, where the gear box is the gear box of the above embodiment.
The embodiment of the application provides a gear box, including base and drive assembly, the base is formed with annular inner chamber, drive assembly sets up in annular inner chamber and links to each other with the main shaft, drive assembly includes N level planetary gear train, at least two-stage adjacent planetary gear train is including the first planetary gear train that is close to the main shaft and keep away from the second planetary gear train of main shaft, the one end of the driving flange of second planetary gear train extends to first planetary gear train and links to each other with the sun gear of first planetary gear train, the other end extends to the planetary gear train of subordinate and links to each other with the ring gear of second planetary gear train, thereby realize the transmission of adjacent two-stage planetary gear train. One end of the driving flange forms supporting points on two sides of the first planetary gear train along the axial direction respectively, on one hand, the positioning accuracy of the driving flange of the second planetary gear train can be improved through two-point support, on the other hand, as the two supporting points of the driving flange are respectively positioned on two sides of the sun gear along the axial direction, namely, a certain supporting span is provided, the amplitude of swing and vibration of the driving flange of the second planetary gear train in the transmission process is reduced, the meshing effect of an inner gear ring and a planetary gear of the second planetary gear train is further improved, and the transmission reliability of a gear box is improved.
Drawings
Features, advantages, and technical effects of exemplary embodiments of the present application will be described below with reference to the accompanying drawings.
FIG. 1 is a cross-sectional view of a transmission system provided in one embodiment of the present application;
FIG. 2 is a schematic diagram of the transmission of a gearbox provided in one embodiment of the present application;
FIG. 3 is a cross-sectional view of a gearbox provided in one embodiment of the present application;
fig. 4 is a cross-sectional view taken along the direction A-A in fig. 3.
Wherein:
10-a gear box; 20-a main shaft;
1-a base; 2-a transmission assembly; 21-planetary gear train; 211-driving flanges; 212-an inner gear ring; 213-a planet carrier; 214-a planet wheel; 215-sun gear; 22-a first support; 23-a second support; 24-connecting piece;
x-axis direction; y-radial direction.
In the drawings, like parts are designated with like reference numerals. The figures are not drawn to scale.
Detailed Description
Features and exemplary embodiments of various aspects of the present application are described in detail below. In the following detailed description, numerous specific details are set forth in order to provide a thorough understanding of the present application. It will be apparent, however, to one skilled in the art that the present application may be practiced without some of these specific details. The following description of the embodiments is merely intended to provide a better understanding of the present application by showing an example of the present application. In the drawings and the following description, at least some well-known structures and techniques are not shown in order to avoid unnecessarily obscuring the present application; also, the dimensions of some of the structures may be exaggerated for clarity. Furthermore, the described features, structures, or characteristics may be combined in any suitable manner in one or more embodiments.
The directional terms appearing in the following description are all directions shown in the drawings and are not limiting of the gearbox and wind turbine generator system of the present application. In the description of the present application, it should also be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be directly connected or indirectly connected. The specific meaning of the terms in the present application can be understood as appropriate by one of ordinary skill in the art.
For a better understanding of the present application, a gearbox and a wind turbine generator set according to embodiments of the present application are described in detail below with reference to the accompanying drawings.
Referring to fig. 1 to 3, an embodiment of the present application proposes a gear box 10 for driving cooperation with a main shaft 20, the gear box 10 includes a base 1 and a driving assembly 2, the base 1 is formed with an annular cavity, the driving assembly 2 is disposed in the annular cavity and connected with the main shaft 20, the driving assembly 2 includes N-stage planetary gear trains 21, n+.2 distributed along an axial direction X of the annular cavity, each stage planetary gear train 21 includes a driving flange 211 as an input end, a sun gear 215 as an output end, and an inner gear ring 212, a planet carrier 213 and a plurality of planet gears 214 connected to the planet carrier 213 between the driving flange 211 and the sun gear 215. The at least two adjacent planetary gear trains 21 include a first planetary gear train close to the main shaft 20 and a second planetary gear train far from the main shaft 20, wherein one end of a driving flange 211 of the second planetary gear train is connected with a sun gear 215 of the first planetary gear train, supporting points are respectively formed on two sides of the first planetary gear train along the axial direction X, and the other end of the driving flange is connected with an inner gear ring 212 of the second planetary gear train.
According to the gear box 10 in the embodiment of the application, the gear box comprises a base 1 and a transmission assembly 2, wherein the base 1 is provided with an annular inner cavity, the transmission assembly 2 is arranged in the annular inner cavity and is connected with a main shaft 20, the transmission assembly 2 comprises N stages of planetary gear trains 21, at least two stages of adjacent planetary gear trains 21 comprise a first planetary gear train close to the main shaft 20 and a second planetary gear train far away from the main shaft 20, one end of a driving flange 211 of the second planetary gear train extends to the first planetary gear train and is connected with a sun gear 215 of the first planetary gear train, and the other end of the driving flange is connected with an inner gear 212 of the second planetary gear train, so that transmission of the adjacent two stages of planetary gear trains 21 is realized. One end of the driving flange 211 forms supporting points on two sides of the first planetary gear train along the axial direction X, on one hand, positioning accuracy of the driving flange 211 of the second planetary gear train can be improved through two-point support, on the other hand, because the two supporting points of the driving flange 211 are located on two sides of the sun gear 215 along the axial direction X respectively, namely, a certain supporting span is provided, amplitude of swing and vibration of the driving flange 211 of the second planetary gear train in a transmission process is reduced, meshing effect of the inner gear ring 212 of the second planetary gear train and the planetary gears 214 is further improved, and transmission reliability of the gear box 10 is improved.
It should be understood that the first planetary gear system and the second planetary gear system are only used for limiting the relative positional relationship of the planetary gear systems 21, that is, for the same planetary gear system 21, the planetary gear system 21 of the previous stage may be used as the second planetary gear system, and for the planetary gear system 21 of the next stage may be used as the first planetary gear system, that is, in the N-stage planetary gear system 21, the transmission relationship between the first planetary gear system and the second planetary gear system can be satisfied between at least two adjacent planetary gear systems 21.
In order to make the driving flange 211 form supporting points on both sides of the sun gear 215 along the axial direction X, in some alternative embodiments, the transmission assembly 2 further includes a first supporting member 22 and a second supporting member 23 distributed along the axial direction X, where the first supporting member 22 and the second supporting member 23 are fixed to both ends of the planet carrier 213 of the first planetary gear train along the axial direction X and are respectively in rotational fit with the driving flange 211. By fixing the first support 22 and the second support 23 to the two ends of the carrier 213 in the axial direction X, interference between the first support 22 and the second support 23 and other components in the planetary gear train 21 during transmission can be avoided, the structures of the first support 22 and the second support 23 can be simplified, and the supporting effect of the first support 22 and the second support 23 on the driving flange 211 can be ensured.
Optionally, the first support 22 and the second support 23 are respectively connected with the driving flange 211 through bearings in a rotating manner, that is, the first support 22 and the second support 23 are supported with the driving flange 211 along the radial direction Y of the annular inner cavity through bearings, and the bearings can be cylindrical roller bearings or deep groove ball bearings, so that friction between the first support 22 and the second support 23 and the driving flange 211 is reduced, and transmission of the transmission assembly 2 is smoother.
Referring to fig. 3 and 4, in some alternative embodiments, the ring gear 212 of the first planetary gear train is rotatably disposed, and the carrier 213 of the first planetary gear train is fixed to the base 1. Since the first support 22 and the second support 23 are fixed to both ends of the carrier 213 of the first planetary gear train in the axial direction X, by fixing the carrier 213 of the first planetary gear train to the base 1, the first support 22 and the second support 23 at both ends thereof are fixedly supported on the driving flange 211, thereby improving the supporting effect of the first support 22 and the second support 23 on the driving flange 211, further reducing the amplitude of the swing and vibration of the driving flange 211 during the transmission, and improving the transmission reliability of the gear box 10.
Alternatively, one ends of the first and second supports 22 and 23 facing away from the driving flange 211 may be extended to the base 1, and the carrier 213 of the first planetary gear train may be fixed to the base 1 by the first and second supports 22 and 23, thereby simplifying the structures of the first and second supports 22 and 23 and the carrier 213. In addition, since the carriers 213 of the first planetary gear train are fixed, one of the first support 22 and the second support 23 can be inserted through the gap between two adjacent planetary gears 214 or the gap of the carrier 213 is fixed and extended to the other and extended to the base 1 through the other, so that the end portions of the first support 22 and the second support 23 can be more conveniently extended to the base 1, and the arrangement structure of the first planetary gear train can be simplified.
It will be appreciated that in addition to improving the load uniformity of the engagement by improving the support effect of the drive flange 211, the at least one stage of planetary gear set 21 may also be provided in a flexible configuration to improve the reliability of the transmission. The components of the planetary gear system 21 at the same stage may be engaged with each other by adopting a flexible structure, or the components themselves may have a certain flexibility, that is, the components may be flexibly deformed in the transmission process of the planetary gear system 21.
In some alternative embodiments, the ring gear 212 of the first planetary gear train and the ring gear 212 of the second planetary gear train may be provided as flexible ring gears. By setting the ring gear 212 as a flexible ring gear, deformation generated by the upper planetary gear train 21 or the main shaft 20 can be absorbed by the flexible ring gear, so that uniform load of meshing of the ring gear 212 and the planet gears 214 is improved, and failure risk is reduced.
To provide the ring gear 212 as a flexible ring gear, the rim thickness of the ring gears 212 of the first and second planetary gear trains is optionally less than or equal to 5 times the modulus. Parameters such as rim thickness of the inner gear ring 212 can be adjusted according to the modulus of the inner gear ring 212, so that the strength of the inner gear ring 212 is improved while certain flexibility of the inner gear ring 212 is ensured. In addition, the adjustment of the compliance of the ring gear 212 may also be achieved by micro-shaping the tooth surfaces of the ring gear 212.
Alternatively, the number of the planetary gears 214 of the first planetary gear train and the planetary gears 214 of the second planetary gear train may be set to four or more. In the conventional planetary gear system 21, the number of the planet gears 214 is often required to be increased for the high-power gear box 10, but for the planetary gear system 21, increasing the number of the planet gears 214 causes the rigidity of the planet carrier 213 to be reduced, and the deformation of the planetary gear system 21 is increased, so that the planetary gear system 21 generates larger unbalanced load and fluctuating load, and the failure risk of the gear box 10 is increased. In the first planetary gear train and the second planetary gear train, due to the good uniform load of the gear engagement, any plurality of the planetary gears 214 can be arranged in the first planetary gear train and the second planetary gear train, so that the power of the planetary gear train 21 is improved, and the risk caused by the increase of the number of the planetary gears 214 of the conventional planetary gear train 21 is avoided.
Referring to fig. 3, when the components of the planetary gear set 21 are engaged with each other using a compliant structure, in some alternative embodiments, the planet carrier 213 of at least one of the first and second planetary gear sets includes an end wall and a compliant pin assembly disposed in a cantilevered configuration on the end wall and supporting the planet 214. The flexible pin can be used as a supporting pin of each planetary gear 214, so that bending moment deformation of the main shaft 20 is absorbed through the flexible pin, meanwhile, loads among the planetary gears 214 can be equally distributed through the flexible pin structure, the problems of unbalanced load and fluctuating load caused by uneven inter-tooth load distribution are avoided, and the failure risk of a transmission system is further reduced.
In addition, flexible structure engagement can be adopted between the adjacent two-stage planetary gear trains 21 to improve the transmission reliability of the gearbox. Alternatively, the drive flange 211 of the second planetary gear train may be engaged with the sun gear 215 of the first planetary gear train by a key tooth. The key tooth portion has a connecting tooth portion and a connecting groove portion with matched shapes, one of the connecting tooth portion and the connecting groove portion is integrated on the sun gear 215 of the first planetary gear train, and the other of the connecting tooth portion and the connecting groove portion is integrated on the driving flange 211 of the second planetary gear train. The plurality of connecting tooth parts are distributed along the circumference of the annular inner cavity, and in the radial direction Y of the annular inner cavity, each connecting tooth part is arranged opposite to one of the connecting groove parts and at least partially stretches into the connecting groove part. The meshing transmission from the sun gear 215 of the first planetary gear system to the driving flange 211 of the second planetary gear system can be realized through the meshing of the connecting tooth part and the connecting groove part, so that the reliability of the first planetary gear system to the second planetary gear system is further improved.
Alternatively, a plurality of connection teeth may be integrated on the driving flange 211 and a connection groove may be integrated on the sun gear 215, or a plurality of connection grooves may be integrated on the driving flange 211 and a connection tooth may be integrated on the sun gear 215, where the specific setting position may be adjusted according to the transmission structure and the manufacturing process, that is, the engagement between the driving flange 211 and the sun gear 215 may be achieved.
In some alternative embodiments, the connection teeth are provided as crowned teeth. The connecting tooth part can be set to be a drum-shaped tooth by micro-shaping the connecting tooth part, so that when the sun gear 215 drives the driving flange 211 to rotate, a certain meshing gap can be formed between the connecting tooth part and the connecting groove part, deformation generated by the upper planetary gear train 21 is allowed to be absorbed, the uniform load of meshing of all gear structures of the planetary gear train 21 is further improved, the loads of the gear structures and the bearings are reduced, and the transmission reliability of the gear box 10 is further improved.
In some alternative embodiments, among the N-stage planetary gear trains 21, the planetary gear train 21 of the first stage is provided as a first planetary gear train, the planetary gear train 21 of the second stage is provided as a second planetary gear train, and the driving flange 211 of the planetary gear train 21 of the first stage is provided in connection with the main shaft 20. Since the planetary gear system 21 of the first stage and the planetary gear system 21 of the second stage bear a large load, by setting the planetary gear system 21 of the first stage as the first planetary gear system and the planetary gear system 21 of the second stage as the second planetary gear system, the uniform load of the meshing between the gear structures can be improved, the load of the gear structures is reduced, and the reliability is improved.
Meanwhile, by setting the first-stage planetary gear train 21 as the first planetary gear train and the second-stage planetary gear train 21 as the second planetary gear train, in the first-stage planetary gear train 21 and the second-stage planetary gear train 21, the driving flange 211 of the second-stage planetary gear train 21 can extend to the sun gear 215 of the first-stage planetary gear train 21, and support points are formed on both sides of the sun gear 215 of the first-stage planetary gear train 21 in the axial direction X, so that the amplitude of the swing and vibration of the driving flange 211 of the second-stage planetary gear train 1 is reduced, the transmission effect of the first-stage planetary gear train 21 to the second-stage planetary gear train 21 is ensured, and the transmission reliability of the gearbox 10 is further improved.
Referring to fig. 3, when the first stage planetary gear system 21 is configured as a first planetary gear system and the second stage planetary gear system 21 is configured as a second planetary gear system, in some alternative embodiments, the transmission assembly 2 further includes a connection member 24, where one end of the connection member 24 is connected to the main shaft 20 and the other end is connected to the planet carrier 213 of the second stage planetary gear system 21.
It will be appreciated that by providing the connection 24 and enabling the connection of the main shaft 20 to the planet carrier 213 of the second stage planetary gear train 21 via the connection 24, two transmission lines can be formed, in which the main shaft 20 is connected to the driving flange 211 of the first stage planetary gear train 21, via the first stage planetary gear train 21 and then to the ring gear 212 of the second stage planetary gear train 21 via the driving flange 211 of the second stage planetary gear train 21. In the second transmission line, the main shaft 20 is connected to the carrier 213 of the planetary gear train 21 of the second stage through the connection member 24, and the transmission power of the main shaft 20 is converged to the planetary gear train 21 of the second stage via the first transmission line and the second transmission line to be output.
Namely, the planetary gear system 21 of the first stage and the planetary gear system 21 of the second stage form a power split differential structure, and for different gear box 10 designs, through adjusting the parameters of each part of the planetary gear system 21 of the first stage and the planetary gear system 21 of the second stage, the proportion of the power directly transmitted to the planetary gear system 21 of the first stage to the total power is about 60%, and the proportion of the power split to the planetary gear system 21 of the second stage to the total power is about 40%, so that the torque of the planetary gear system 21 of the first stage is effectively reduced, the volume and the weight of the gear box 10 can be reduced, and the torque density of the gear box 10 can be improved.
Alternatively, the connection member 24 may be connected to the main shaft 20 through a key tooth portion, which may be provided in a flexible structure to reduce the influence of bending moment deformation of the main shaft 20 on the planetary gear train 21 of the second stage.
Since the planet carrier 213 of the second stage planetary gear train 21 is connected to the main shaft 20 by means of the connection 24, i.e. the planet carrier 213 of the second stage planetary gear train 21 rotates during transmission, the transmission assembly 2 in some alternative embodiments further comprises a third support member which is fixed to the end of the planet carrier 213 of the second stage 2 planetary gear 1 train facing away from the main shaft 20 and is in a rotating fit with the base 1 in the radial direction Y of the annular inner cavity. By providing the third support member connected to the carrier 213 of the second-stage planetary gear train 21 to support the base 1, the swing and vibration of the carrier 213 of the second-stage planetary gear train 21 can be reduced, thereby improving the meshing effect of each gear structure in the second-stage planetary gear train 21 and improving the reliability of the transmission of the gear box 10.
Referring to fig. 1 and 3, because of the running fit between the spindle 20 and the bearing seat, when the planet carrier 213 of the second-stage planetary gear train 21 is connected to the spindle 20 through the connecting piece 24, one end of the second-stage planetary gear train 21 in the axial direction X may be multiplexed into a supporting structure between the spindle 20 and the bearing seat, and the other end may be supported with the base 1 through the third supporting piece 25, thereby forming a two-point supporting structure with a certain span, further improving the supporting effect on the planet carrier 213 of the second-stage planetary gear train 21, further ensuring the meshing effect of each gear structure of the second-stage planetary gear train 21, and improving the reliability of the transmission system.
Alternatively, in the radial direction Y, the third support 25 may be in a running fit with the base 1 via a bearing, as well as between the spindle 20 and the bearing housing. The bearing can be a cylindrical roller bearing or a tapered roller bearing, so that the transmission effect is improved.
Referring to fig. 1 to 3, in some alternative embodiments, at least two adjacent planetary gear trains 21 include a third planetary gear train close to the main shaft 20 and a fourth planetary gear train far from the main shaft 20, wherein an inner gear ring 212 of the fourth planetary gear train is fixed to the base 1, and a driving flange 211 of the fourth planetary gear train has one end connected to a sun gear 215 of the third planetary gear train and the other end connected to a planet carrier 213 of the fourth planetary gear train. By fixing the ring gear 212 of the fourth planetary gear train to the base 1, the transmission relation of the fourth planetary gear train 212 can be made simpler and more reliable and the cost can be reduced as compared with the first planetary gear train and the second planetary gear train.
Furthermore, since the driving flange 211 of the fourth planetary gear train is directly connected to the carrier 213 of the fourth planetary gear train, the carrier 213 of the fourth planetary gear train can be rotatably coupled to the base 1 via a bearing, which can be provided as a tapered roller bearing.
Alternatively, one end of the driving flange 211 of the fourth planetary gear train may be connected to the sun gear 215 of the third planetary gear train through a key gear portion, the other end of the driving flange 211 of the fourth planetary gear train may be connected to the planet carrier 213 of the fourth planetary gear train through bolts or screws, and the driving flange 211 of the fourth planetary gear train may be integrally provided with the planet carrier 213, which may be adjusted according to the space and size of the planetary gear train 21.
The third planetary gear system and the fourth planetary gear system are only used for limiting the relative positional relationship of the planetary gear systems 21, that is, the same stage planetary gear system 21 can be used as the second planetary gear system or can be used as the third planetary gear system at the same time.
Wherein, when n=3, the planetary gear system 21 of the first stage can be set as a first planetary gear system, the planetary gear system 21 of the second stage is set as a second planetary gear system and a third planetary gear system at the same time, and the planetary gear system 21 of the third stage is set as a fourth planetary gear system, so that bending moment deformation of the main shaft 20 is reduced through the planetary gear system 21 of the first stage and the planetary gear system 21 of the second stage, and cost is reduced through the planetary gear system 21 of the third stage while reliability of a transmission system is ensured.
The embodiment of the application also provides a wind generating set, which comprises the gearbox of the embodiment. Therefore, the wind generating set provided in the embodiment of the present application has the technical effects of the technical solution of the gearbox in any of the above embodiments, and the explanation of the same or corresponding structure and terms as those of the above embodiments is not repeated herein.
While the present application has been described with reference to a preferred embodiment, various modifications may be made and equivalents may be substituted for elements thereof without departing from the scope of the present application. In particular, the technical features mentioned in the respective embodiments may be combined in any manner as long as there is no structural conflict. The present application is not limited to the specific embodiments disclosed herein, but encompasses all technical solutions falling within the scope of the claims.
Claims (10)
1. A gearbox for driving engagement with a main shaft, said gearbox comprising:
a base (1) formed with an annular cavity;
the transmission assembly (2) is arranged in the annular inner cavity and is connected with the main shaft, the transmission assembly (2) comprises N-level planetary gear trains (21) which are distributed along the axial direction of the annular inner cavity, N is more than or equal to 2, each level of planetary gear trains (21) comprises a driving flange (211) serving as an input end, a sun gear (215) serving as an output end, an annular gear (212) positioned between the driving flange (211) and the sun gear (215), a planet carrier (213) and a plurality of planet gears (214) connected to the planet carrier (213);
the planetary gear trains (21) adjacent in at least two stages comprise a first planetary gear train close to the main shaft and a second planetary gear train far away from the main shaft, one end of a driving flange (211) of the second planetary gear train is connected with a sun gear (215) of the first planetary gear train, supporting points are respectively formed on two sides of the first planetary gear train along the axial direction, and the other end of the driving flange is connected with an inner gear ring (212) of the second planetary gear train.
2. Gearbox according to claim 1, characterized in that the transmission assembly (2) further comprises a first support (22) and a second support (23) distributed along the axial direction, the first support (22) and the second support (23) being fixed to the planet carrier (213) of the first planetary train at both ends along the axial direction and in a running fit with the driving flange (211) respectively.
3. Gearbox according to claim 2, characterised in that the first support (22) and the second support (23) are each rotatably connected to the drive flange (211) by means of bearings.
4. Gearbox according to claim 2, characterised in that the drive flange (211) of the first planetary train is connected to the annulus gear (212) of the first planetary train and in that the planet carrier (213) of the first planetary train is fixed to the base (1).
5. The gearbox of claim 4, wherein a rim thickness of the annulus gear (212) of the first and second planetary gear trains is less than or equal to 5 times a modulus.
6. The gearbox of claim 4, wherein the planet carrier (213) of at least one of the first and second planetary gear trains includes an end wall and a flexpin assembly, a plurality of the flexpin assemblies being disposed in a cantilevered configuration on the end wall and supporting the planet (214).
7. Gearbox according to claim 1, characterised in that in the N stages of the planetary gear trains (21), the planetary gear train (21) of the first stage is arranged as the first planetary gear train, the planetary gear train (21) of the second stage is arranged as the second planetary gear train, the driving flange (211) of the planetary gear train (21) of the first stage is arranged in connection with the main shaft;
the transmission assembly (2) further comprises a connecting piece (24), one end of the connecting piece (24) is connected with the main shaft, and the other end of the connecting piece is connected with the planet carrier (213) of the planetary gear train (21) of the second stage.
8. Gearbox according to claim 7, characterised in that the transmission assembly (2) further comprises a third support fixed to the end of the planet carrier (213) of the planetary train (21) of the second stage facing away from the main shaft and in a running fit with the base (1) in the radial direction of the annular inner cavity.
9. Gearbox according to claim 1, characterised in that the planetary trains (21) adjacent at least two stages comprise a third planetary train close to the main shaft and a fourth planetary train remote from the main shaft, the annulus gear (212) of which is fixed to the base (1), the drive flange (211) of which is connected at one end to the sun gear (215) of the third planetary train and at the other end to the planet carrier (213) of the fourth planetary train.
10. A wind power generator set, comprising a main shaft and a gear box arranged at one side of the main shaft along the axial direction of the main shaft, wherein the gear box is the gear box of any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202223576929.8U CN219317562U (en) | 2022-12-30 | 2022-12-30 | Gear box and wind generating set |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202223576929.8U CN219317562U (en) | 2022-12-30 | 2022-12-30 | Gear box and wind generating set |
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| Publication Number | Publication Date |
|---|---|
| CN219317562U true CN219317562U (en) | 2023-07-07 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202223576929.8U Active CN219317562U (en) | 2022-12-30 | 2022-12-30 | Gear box and wind generating set |
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| CN (1) | CN219317562U (en) |
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