WO2015101288A1 - 一体化的半直驱风力发电机传动链及其所用齿轮箱 - Google Patents

一体化的半直驱风力发电机传动链及其所用齿轮箱 Download PDF

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Publication number
WO2015101288A1
WO2015101288A1 PCT/CN2014/095557 CN2014095557W WO2015101288A1 WO 2015101288 A1 WO2015101288 A1 WO 2015101288A1 CN 2014095557 W CN2014095557 W CN 2014095557W WO 2015101288 A1 WO2015101288 A1 WO 2015101288A1
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WO
WIPO (PCT)
Prior art keywords
gear
output shaft
planetary
shaft
bearing
Prior art date
Application number
PCT/CN2014/095557
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English (en)
French (fr)
Inventor
陆群峰
张保松
靳国忠
Original Assignee
南车戚墅堰机车车辆工艺研究所有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Priority claimed from CN201310747728.6A external-priority patent/CN103742607B/zh
Priority claimed from CN201320886569.3U external-priority patent/CN203717796U/zh
Application filed by 南车戚墅堰机车车辆工艺研究所有限公司 filed Critical 南车戚墅堰机车车辆工艺研究所有限公司
Priority to US15/109,038 priority Critical patent/US10215260B2/en
Publication of WO2015101288A1 publication Critical patent/WO2015101288A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/36—Toothed gearings for conveying rotary motion with gears having orbital motion with two central gears coupled by intermeshing orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D15/00—Transmission of mechanical power
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D15/00—Transmission of mechanical power
    • F03D15/10—Transmission of mechanical power using gearing not limited to rotary motion, e.g. with oscillating or reciprocating members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • F03D80/70—Bearing or lubricating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D9/00—Adaptations of wind motors for special use; Combinations of wind motors with apparatus driven thereby; Wind motors specially adapted for installation in particular locations
    • F03D9/20—Wind motors characterised by the driven apparatus
    • F03D9/25—Wind motors characterised by the driven apparatus the apparatus being an electrical generator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/082—Planet carriers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/40—Transmission of power
    • F05B2260/403—Transmission of power through the shape of the drive components
    • F05B2260/4031—Transmission of power through the shape of the drive components as in toothed gearing
    • F05B2260/40311—Transmission of power through the shape of the drive components as in toothed gearing of the epicyclic, planetary or differential type
    • 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

Definitions

  • the invention belongs to the technical field of wind power generation machinery, and relates to an integrated semi-direct drive wind power generator transmission chain and a gear box used therefor.
  • the structure of the semi-direct drive wind turbine is to increase the speed of the wind wheel to a certain multiple through the gear box and then input it to the generator (for example, a permanent magnet generator).
  • the direct drive wind turbine is equipped with a speed increasing gear box. .
  • the semi-direct drive wind turbine increases the rotational speed input from the hub by about 25-40 times through the gear transmission, and its size and weight can be greatly reduced compared to the direct drive wind turbine. Therefore, the semi-direct drive wind turbine not only has the following advantages of the direct drive wind turbine: it is easy to achieve low voltage ride through, there is no high-speed output shaft that is prone to failure, and the motor does not have fault points such as brushes and slip rings. The impact is small and the power quality is high; and the semi-direct drive wind turbine also effectively avoids the high cost brought by the large direct drive wind turbine and the difficulty of lifting.
  • the transmission chain of the semi-direct drive wind turbine and the gearbox used therein usually use the conventional two-stage NGW scheme, which has a large number of parts, a complicated structure, and is difficult to process and assemble; the existing NGW-based transmission chain, the planet The wheels are subjected to double-sided loads, increasing the likelihood of gear failure and the rotation of the planet carrier, adding to the complexity of the lubrication solution.
  • the invention patent application with the publication number CN101846155A discloses a MW that is easy to disassemble, can be overhauled at high altitude, light in weight, and has low manufacturing process difficulty.
  • Level quasi-planetary semi-direct drive wind power speed increase box the patent application uses "(input) inner ring gear - two second wheel - quasi-planetary wheel - intermediate wheel - (output) center gear" in one plane A single-stage quasi-planetary structure with two shunts.
  • the structure of the semi-direct drive wind power increaser box is double-flowed due to the addition of two intermediate wheels, so that the bearing capacity can be significantly improved, and because of the single-stage transmission, the axial length is short, and the installation is required.
  • the space is small; however, the semi-direct drive wind power increase box of the patent application obviously has the disadvantage of small transmission ratio and cannot meet the requirements of the high power fan.
  • One of the objects of the present invention is to integrate a gearbox with a generator to integrally implement a semi-direct drive wind turbine drive train.
  • Still another object of the present invention is to provide a gear box that is simple in structure, low in cost, and compact in structure to meet the requirements of a high-power fan.
  • a further object of the present invention is to provide an integrated semi-direct drive wind power generator transmission chain and a gear box therefor, which integrates the gear box and the generator, has high reliability, light weight, short axial length, and structure. Reasonable, easy to repair and disassemble.
  • the present invention provides the following technical solutions.
  • a gearbox for a semi-direct drive wind turbine drive chain, the gearbox including a front case, a rear case, a main shaft, and a carrier;
  • the planet carrier is fixedly disposed between the front box body and the rear box body, and the main shaft is rotatably disposed on the front box body and the planet carrier;
  • the gearbox also includes:
  • N planetary shafts axially rotatably disposed on the planet carrier and the rear casing, each of the planetary axles being provided with a first stage planetary gear and a second stage planetary gear, N ⁇ 3;
  • An output shaft the upper end of the output shaft being axially rotatably disposed on the planet carrier and having a lower windward end extending beyond the rear housing;
  • N of the intermediate wheels and the N first stage planetary gears are disposed in the carrier, the sun gear, N of the second stage planetary gears are disposed on the carrier and the rear Inside the cavity formed by the box;
  • the inner ring gear, the intermediate wheel and the first stage planetary gear constitute a first stage fixed axis transmission pair
  • the second stage planetary wheel and the sun wheel constitute a second stage fixed axis transmission pair
  • an integrated half using the gearbox a direct drive wind turbine drive chain, wherein a lower wind direction end of the output shaft is coupled to an upwind end of the generator rotor to drive the generator rotor to rotate, and a lower wind end of the generator rotor passes through a generator stator main
  • the bearing is supported on the inner bore of the generator stator.
  • a wind power plant that includes the integrated semi-direct drive wind turbine drive train described above.
  • FIG. 1 is a schematic view showing the structure of an integrated semi-direct drive wind power generator transmission chain and a gear box therefor according to an embodiment of the present invention.
  • FIG. 2 is a cross-sectional view of the semi-direct drive wind turbine transmission chain of FIG. 1 and its gear box taken along line A-A.
  • FIG. 3 is a cross-sectional view of the B-B of the semi-direct drive wind turbine transmission chain of FIG. 1 and the gear box used therein.
  • FIG. 4 is a schematic view showing the mounting of an output shaft bearing according to another embodiment of the present invention.
  • the "planetary wheel” (for example, the first-stage planetary gear and the second-stage planetary gear) rotates relative to its own planetary axle and does not revolve relative to the sun gear, but the concept of “planet” can be understood as “Planetary wheels” are a way of being distributed over the basic circular orbit of the sun gear.
  • FIG. 1 is a schematic structural view of an integrated semi-direct drive wind turbine transmission chain and a gear box therefor according to an embodiment of the present invention
  • FIG. 2 is a semi-direct drive wind turbine transmission chain of FIG. AA cross-sectional view of the gearbox used
  • FIG. 3 is a cross-sectional view of the BB section of the semi-direct drive wind turbine drive chain of Fig. 1 and the gearbox used therein.
  • a gear case according to an embodiment of the present invention and a semi-direct drive wind power generator drive chain using the same will be described with reference to FIGS. 1 to 3.
  • the gear case has a front case 6, a rear case 14, a main shaft 5, and a carrier 10, and the carrier 10 is fixedly disposed between the front case 6 and the rear case 14.
  • the front case 6 is placed in the upwind direction of the carrier 10
  • the rear case 14 is placed in the downwind direction of the carrier 10, and the accommodation space of the gear case is formed between the front case 6 and the rear case 14.
  • the planet carrier 10 A torsion arm 10-3 extending beyond the front case 6 and the rear case 14 is provided, and the entire gear case can be fixed to the wind turbine by the torsion arm 10-3.
  • the main shaft 5 includes a main shaft upper wind direction end 5-1, a main shaft lower wind direction end small diameter portion 5-2, and a main shaft lower wind direction end large diameter portion 5-3.
  • the upper wind direction end 5-1 is supported on the inner hole 6-1 of the front case through the upper wind direction bearing 2
  • the main shaft lower wind direction end small diameter portion 5-2 is supported on the carrier 10 through the main shaft downwind bearing 3.
  • the main shaft lower wind direction end large diameter portion 5-3 is fixedly connected with the inner ring gear 7, and the inner ring gear 7 and the main shaft 5 can be connected to each other by welding or bolt fixing; thus, the main shaft 5 is rotatably disposed at On the front case 6 and the carrier 10, the windward input end 5-1 of the main shaft rotates under the external wind input, thereby driving the lower wind direction end 5-2 of the main shaft to rotate, in particular, the inner ring gear 7 is synchronously rotated.
  • the external wind input can be realized by the hub connection flange 1 fixedly connected to the wind direction end 5-1 of the main shaft.
  • the hub connection flange 1 is directly connected to the hub of the wind power generator or through the fan.
  • the main shaft is connected to the hub of the wind turbine, and the hub connecting flange 1 can be connected to the main shaft upper wind end 5-1 of the main shaft 5 by bolts.
  • the main shaft 5 realizes double bearing support through the main shaft upper wind direction bearing 2 and the main shaft downwind bearing 3, and is more advantageous for bearing the pitching moment of the main shaft 5, and the rotation of the main shaft 5 is also more stable.
  • the carrier 10 is provided with N intermediate wheels 8 and N first-stage planetary gears in the gearbox, where N is an integer greater than or equal to 3, for example as shown in the figure.
  • N is an integer greater than or equal to 3, for example as shown in the figure.
  • Each of the first stage planetary gears is fixedly disposed on the corresponding planetary axle 13, and each of the planetary axles 13 is fixedly disposed with a second-stage planetary gear 15 that rotates synchronously with the first-stage planetary gears, and the diameter of the second-stage planetary gears 15 More than the diameter of the first stage planetary gear, for example, the transmission ratio of the second stage planetary gear 15 to the first stage planetary gear may range from 2-3.
  • the first end of the planetary axle 13, that is, the upper end of the upper wind direction, is supported by the windward bearing 4 on the planetary axle on the first planetary axle hole 102-1 of the upper windward auxiliary frame 102 of the planetary carrier, the planetary axle 13
  • the intermediate section is supported by the planetary axle intermediate bearing 12 on the planetary axle bore 10-1 of the main frame body 101 of the planet carrier.
  • the second end of the planetary axle 13, that is, the lower windward end passes through the planetary axle downwind bearing 16 Supported on the rear case 14; thus, the planetary axle 13 is axially rotatably disposed on the carrier 10 and the rear case 14, and the axial rotation stability of the planetary shaft 13 is good.
  • the gearbox includes an output shaft 21 that is axially rotatably disposed on the carrier 10 and has one end projecting outside the rear housing 14, and the output shaft 21 is provided with a sun gear 17, N second-stage planetary gears 15 are both meshed with the sun gear 17, thereby achieving a converging transmission at the sun gear 17.
  • the carrier 10 includes a main frame body 101 and an upwind auxiliary frame body 102.
  • the upwind direction auxiliary frame body 102 is fixedly disposed in the upwind direction of the main frame body 101, and a space formed therebetween can be used.
  • the intermediate wheel 8 and the first stage planetary gear are disposed; specifically, as shown in FIG. 1, the first end of each of the intermediate shafts 11 (ie, the end of the upwind direction) is fixedly mounted to the upwind auxiliary frame 102 of the carrier 10.
  • the second end of the intermediate shaft 11 (i.e., the end at the downwind direction) is fixedly mounted in the intermediate shaft hole 10-2 of the main frame body 101 of the carrier 10, and therefore, each of the intermediate shafts 11 It is fixed to the carrier 10 and is not rotatable (the relatively fixed intermediate shaft 11 does not rotate axially when the intermediate wheel 8 rotates), and the N intermediate shafts 11 and the N intermediate wheels 8 are distributed around the center of the carrier 10. Arrangement.
  • the first stage planetary gear is disposed at the upper wind direction end of the planetary axle 13, for example, disposed between the upper wind direction auxiliary frame body 102 of the carrier 10 and the main frame body 101; the second stage planetary gear 15 is disposed under the planetary wheel shaft 13 The wind direction end is disposed, for example, between the main frame body 101 of the carrier 10 and the rear case.
  • the N intermediate wheels 8 and the N first stage planetary gears are basically arranged in the carrier 10, and the sun gear 17 and the N second stage planetary gears 15 are arranged in the space formed by the carrier 10 and the rear case 14. Inside the cavity, the structure is arranged reasonably and compactly.
  • each of the intermediate wheels 8 meshes with the ring gear 7, and each of the first stage planetary gears meshes with a corresponding intermediate wheel 8, whereby the ring gear 7, the intermediate wheel 8 and the first stage
  • the planetary gears constitute a first-stage fixed-shaft transmission pair, and the inner ring gear 7 and the plurality of intermediate wheels 8 are shunt-driven to be shunt-driven to a plurality of first-stage planetary gears.
  • Such a gear transmission method can make the diameter of the first stage planetary gears smaller, which is very advantageous for increasing the transmission ratio in a relatively compact space, and has high transmission efficiency and is also suitable for high power transmission.
  • the specific diameter of the intermediate wheel 8 and the specific diameter of the first stage planetary gears can be selectively set according to the size requirements of the specific gear ratio.
  • each of the second-stage planetary gears 15 meshes with the sun gear 17, and the second-stage planetary gears 15 and the sun gear 17 constitute a second-stage fixed-shaft transmission pair, and the second-stage planetary gears 15 and the sun gear 17 are merged. transmission.
  • the diameter of the second stage planetary gear 15 is much larger than the diameter of the sun gear 17, so that it is also easy to achieve a high gear ratio and increase the rotational speed of the output shaft 21.
  • the fixed connection between the second stage planetary gear 15 and the planetary axle 13 is not limitative,
  • the interference fit connection, or the flat key plus the interference fit connection likewise, the fixed connection between the sun gear 17 and the output shaft 21 is not restrictive, for example, the inner side of the sun gear 17 may have internal splines, The outer portion of the output shaft 21 has external splines, and a splined connection 25 between the sun gear 17 and the output shaft 21 is used for fixed connection.
  • the gear ratio of the gearbox is affected by various factors, such as the ratio of the number of teeth of the inner ring gear to the gear ratio of the first stage planetary gear, the number of teeth of the second stage planetary gear and the number of teeth of the sun gear. Wait.
  • the intermediate wheel 7 between the first stage planetary gear and the ring gear 7 at least it can contribute to reducing the radial distance of the planetary axle 13 relative to the output shaft 21; within a certain range of transmission ratios (
  • the transmission ratio range is usually the basic requirement of the gearbox transmission, and the radial dimension of the second-stage fixed-shaft transmission sub-structure can be reduced, so that the radial dimension of the second-stage fixed-shaft transmission sub-structure can be compared with the first-order
  • the radial dimension of the fixed-shaft drive pair is designed to be smaller.
  • the generator rotor 22 is housed or includes the portion of the rear casing 14 that protrudes downward toward the windward end, that is, the generator rotor 22
  • the first stage fixed shaft drive pair (as shown in Figure 1) can be contained or contained at least in the radial direction. Therefore, the overall structure of the transmission chain is compact.
  • the upper wind direction end 21-1 of the output shaft 21 is supported by the output shaft bearing 24 on the main frame body 101 of the carrier 10, and the lower wind direction end 21-2 of the output shaft 21 is extended.
  • the output shaft 21 serves as the output shaft of the gearbox, and the lower wind direction end 21-2 and the upwind end 22 of the generator rotor 22 are 1 is connected together, so that the generator rotor 22 can be directly driven to rotate, so that the output shaft 21 is supported between the carrier 10 and the generator rotor 22.
  • the output shaft 21 is lengthened, the gearbox and the power generation are realized.
  • the integrated connection of the machine reduces the overall length of the transmission chain in the axial direction, and the structural integration is higher; and the extension of the output shaft 21 (because of its upper wind end 21- 1 is on the planet carrier, the downwind end 21-2 is on the generator rotor 22), and the length is even larger than the width of the second stage planetary gear 15, forming a longer force arm, so that the pitching moment of the generator rotor 22 can be made Subjected by a smaller output shaft bearing 24; further, by The direct connection of the output shaft 21 to the upwind end 22-1 of the generator rotor 22 reduces the possibility of misalignment between the main shaft 5, the output shaft 21 and the main shaft of the generator, which is advantageous for improving the performance of the wind turbine and life.
  • the main shaft 5 and the axis of the output shaft 21 are on the same straight line; the bearing housing of the output shaft bearing 24 may be integral with the center hole 10-4 of the main frame body 101 of the carrier 10.
  • the bearing housing of the output shaft bearing 24 is fixedly mounted on the upper wind direction of the main frame body 101 of the carrier 10, and facing the carrier downward wind direction center hole 10 -4 places.
  • the generator rotor 22 includes not only the upper wind direction end 22-1 but also the lower wind direction end 22-2, and the lower wind direction end 22-2 passes through the generator stator.
  • the main bearing 19 is supported on the inner bore of the generator stator 23, thus integrally forming the semi-direct drive wind turbine drive train of the embodiment of the present invention, which is very advantageous for reducing the axial dimension of the transmission chain.
  • the rear case 14 is at least partially protruded downward to form a cavity for accommodating at least the sun gear 17 and the N second stage planetary gears 15, and the radial size of the generator rotor 22 is larger than that of the second stage planetary gears.
  • the generator rotor 22 can easily accommodate the portion of the rear casing 14 that protrudes toward the downward wind direction; meanwhile, the maximum radial dimension of the generator stator 23 can be greater than or equal to
  • the maximum radial dimension of the rear casing 14 the generator stator 23 contains the generator rotor 22, and the circumferential end surface of the generator stator 23 is connected to the rear casing 14 by bolts (to facilitate the disassembly of the generator stator 23), so that the rear casing 14
  • the generator rotor 22 and the generator stator 23 form an integrated structure as shown in FIG. 1.
  • the generator and the gear box are well integrated, further reducing the axial dimension of the transmission chain, and the structure is more compact.
  • an air gap may be disposed between the generator rotor 22 and the generator stator 23.
  • the lower wind direction end 21-2 of the output shaft 21 can be detachably fixedly coupled to the inner hole 22-1- of the upper wind direction end 22-1 of the generator rotor 22 by the tensioning force locking disk 20. 1 , and the diameter of the inner hole 22-1-1 and the inner hole 14-1 of the rear case 14 are both larger than the diameter of the sun gear 17 (it is to be noted that when the output shaft 21 passes through the rear case 14-1, The rear case 14 may not provide support for the output shaft 21; the generator stator 23 is provided with an opening 23-1 at the output shaft 21, and the rear cover 18 is detachably mounted to the opening 23-1.
  • the diameter of the inner hole 22-1-1 at the upper wind direction end 22-1 of the generator rotor 22 and the inner hole 14-1 diameter of the rear case body 14 are both larger than the diameter of the sun gear 17 and the rear box cover 18 and the like.
  • the sun gear 17 and the output shaft 21 with the highest speed and the most problematic in the entire transmission chain can be directly extracted from the inner hole of the generator rotor 22 without greatly disassembling the whole chain of the transmission chain. Installation and maintenance convenience.
  • the torque obtained from the wind energy by the wind turbine impeller is transmitted through the hub to the flange 1
  • the input and transmission to the main shaft 5, while driving the main shaft 5 to rotate, simultaneously drive the inner ring gear 7, the inner ring gear 7 and the N medium wheel 8 mesh to form an N-split transmission, and the rotation of the N medium-disc wheels 8 can respectively transmit power to the N a first-stage planetary gear, the planetary axle 13 of each first-stage planetary gear drives the second-stage planetary gear 15 to rotate synchronously, and further, the N second-stage planetary gears 15 mesh with the same sun gear 17 to realize a combined transmission.
  • the sun gear 17 drives the output shaft 21 to rotate synchronously through the spline connection, thereby realizing the high-speed output of the output shaft 21.
  • the output shaft 21 can further drive the generator rotor 22 to rotate through the locking disk 20, thereby realizing the power generation function.
  • the gearbox of the above embodiment and the transmission chain using the same have at least one of the following advantages, in particular having the following advantages (1), (2), and (3):
  • the planet carrier is fixed, that is, it is not rotating, and its torsion arm can be fixed on other components.
  • the planet carrier and the torsion arm can bear the main torque input by the hub connection flange and the weight of the entire transmission chain. And capable of carrying the main shaft, the front case, the rear case, the intermediate wheel, the planetary axle and the output shaft;
  • the axis of the gearbox and the axis of the output shaft can be on the same line, and the gearbox is integrated with the generator, which reduces the possibility of misalignment of the main shaft, the output shaft and the generator main shaft, and improves the wind power generation. Machine performance and life;
  • the two planetary carriers rotate the two-stage planetary gears, and the revolutions are required to be lubricated.
  • the planetary gears of the present invention are not revolving, and the central axis of rotation, that is, the planets
  • the axle is fixed on the rigid body (ie, the first end of the planetary axle is supported by the windward bearing on the planetary axle on the planetary axle hole 102-1 of the upper windward of the carrier, and the middle section of the planetary axle is supported by the intermediate bearing of the planetary axle
  • the second end of the planetary axle is supported on the rear casing by the planetary winder downwind bearing, which eliminates the need to lubricate the revolution body, thereby simplifying the planetary gear Lubrication design;
  • Generator rotor and generator stator can be designed with large radial size and small axial dimension, which shortens the axial dimension of the transmission chain; the entire generator structure contains part of the rear box, further shortening the axis of the transmission chain To the size, the radial dimension of the generator stator is equal to or close to the maximum dimension of the rear casing, thereby not increasing the radial dimension of the entire transmission chain; thus, reducing the volume of the entire transmission chain and reducing the weight of the transmission chain;

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Abstract

半直驱风力发电机传动链及其所用齿轮箱，包括前箱体（6）、后箱体（14）、主轴（5）、行星架（10），还包括：主轴（5）上的内齿圈（7）、N个介轮（8）、N个设置有第一级行星轮和第二级行星轮的行星轮轴（13）、一个输出轴（21）以及太阳轮（17），内齿圈（7）、介轮（8）与第一级行星轮构成第一级定轴传动副，第二级行星轮与太阳轮构成第二级定轴传动副；其中输出轴（21）的上风向端可轴向旋转地设置在行星架（10）上并且其下风向端伸出在后箱体（14）之外；伸出在外的下风向端与发电机转子（22）的上风向端连接以带动电机转子转动，发电机转子（22）的下风向端通过发电机定子主轴承支撑在发电机定子的内孔上。该结构的传动链具有集成度高、结构简单、重量轻、轴向长度短、高传动比等特点。

Description

一体化的半直驱风力发电机传动链及其所用齿轮箱 技术领域
本发明属于风力发电机械技术领域，涉及一种一体化的半直驱风力发电机传动链及其所用齿轮箱。
背景技术
半直驱风力发电机的结构是通过齿轮箱将风轮转速增速至一定倍数后输入给发电机(例如永磁发电机)，本质上就是直驱风力发电机加装了一个增速齿轮箱。半直驱风力发电机通过齿轮传动将从轮毂输入的转速增大了诸如25-40倍左右，相比于直驱风力发电机，其尺寸和重量都能得到大幅的减小。所以，半直驱风力发电机不仅具备直驱风力发电机存在的以下优点：易于实现低电压穿越，不存在容易出故障的高速输出轴，电机不存在电刷、滑环等故障点，对电网冲击小、电能质量高；并且半直驱风力发电机还有效避免了大型直驱风力发电机带来的高成本，吊装困难等缺点。
同时，当前大型风力发电机都有着轻量化、集成化、可靠性高的要求，以降低度电成本。半直驱风力发电机的特点特别适用于大型风机，具有广阔的发展前景。
目前，半直驱风力发电机的传动链及其所用齿轮箱通常使用常规的两级NGW方案，零件个数较多，结构复杂，加工及装配困难；现有基于NGW方案的传动链中，行星轮都承受双面载荷，增大了齿轮失效的可能性，并且行星架转动，增加了润滑解决方案的复杂性。
申请公布号为CN101846155A(名称为“兆瓦级准行星半直驱风电增速箱”)的发明专利申请公开了一种拆装方便、能在高空大修、重量轻、制造工艺难度低的兆瓦级准行星半直驱风电增速箱，该专利申请采用了“(输入)内齿圈-两只第二介轮-准行星轮-介轮-(输出)中心齿轮”这种在一个平面内进行两次分流的单级准行星结构。这种半直驱风电增速箱结构由于增加了两只介轮，形成了二次分流，因而承载能力可明显提高，同时因为是单级传动，轴向长度较短，所需安装 空间较小；但该专利申请的半直驱风电增速箱明显存在传动比小的缺点，不能满足大功率风机的要求。
发明内容
本发明的目的之一在于，将齿轮箱与发电机集成，以一体化地实现半直驱风力发电机传动链。
本发明的又一目的在于，减小半直驱风力发电机传动链的轴向长度。
本发明的还一目的在于，提出一种结构简单、实现成本低、结构紧凑合理的齿轮箱，以满足大功率风机的要求。
本发明的再一目的是提出一种一体化的半直驱风力发电机传动链及其所用齿轮箱，将齿轮箱与发电机集成化，具有可靠性高、重量轻，轴向长度短，结构合理，维修与拆装方便等特点。
为实现以上目的或者其他目的，本发明提供以下技术方案。
按照本发明的一方面，提供一种齿轮箱，用于半直驱风力发电机传动链，该齿轮箱包括前箱体、后箱体、主轴、行星架；
所述行星架固定地设置在所述前箱体和所述后箱体之间，所述主轴可旋转地设置在所述前箱体和所述行星架上；
所述齿轮箱还包括：
固定设置在所述主轴上的内齿圈；
N个可轴向旋转地设置在所述行星架和所述后箱体上的行星轮轴，每个所述行星轮轴上设置有第一级行星轮和第二级行星轮，N≥3；
对应设置在每个第一级行星轮与所述内齿圈之间的介轮；以及
一个输出轴，该输出轴的上风向端可轴向旋转地设置在所述行星架上并且其下风向端伸出在所述后箱体之外；
设置在所述输出轴上的太阳轮；
其中，N个所述介轮以及N个所述第一级行星轮布置在所述行星架中，所述太阳轮、N个所述第二级行星轮布置在所述行星架与所述后箱体构成的空腔内；
其中，所述内齿圈、介轮与第一级行星轮构成第一级定轴传动副，所述第二级行星轮与所述太阳轮构成第二级定轴传动副。
按照本发明的又一方面，提供一种使用所述的齿轮箱的一体化的半 直驱风力发电机传动链，其中，所述输出轴的下风向端与发电机转子的上风向端连接以带动所述发电机转子转动，所述发电机转子的下风向端通过发电机定子主轴承支撑在发电机定子的内孔上。
按照本发明的再一方面，提供一种风力发电设备，其包括以上所述的一体化的半直驱风力发电机传动链。
附图说明
从结合附图的以下详细说明中，将会使本发明的上述和其他目的及优点更加完整清楚，其中，相同或相似的要素采用相同的标号表示。
图1是按照本发明一实施例的一体化的半直驱风力发电机传动链及其所用齿轮箱的结构示意图。
图2是图1的半直驱风力发电机传动链及其所用齿轮箱的A-A截面示意图。
图3是图1的半直驱风力发电机传动链及其所用齿轮箱的B-B截面示意图。
图4是本发明另一实施例的输出轴轴承的安装示意图。
符号说明：
1——轮毂连接法兰盘；2——主轴上风向轴承；3——主轴下风向轴承；4——行星轮轴上风向轴承；5——主轴；5-1——主轴上风向端；5-2——主轴下风向端细径部；5-3——主轴下风向端粗径部；6——前箱体；6-1——前箱体的内孔，7——内齿圈；8——介轮；9——满滚子轴承；10——行星架；101——行星架的主架体；102——行星架的上风向辅助架体；102-1——第一行星轮轴孔；102-2——介轮轴孔；10-1——行星架的行星轮轴孔；10-2——介轮轴孔；10-3——扭力臂；10-4——行星架的中心孔；11——介轮轴；12——行星轮轴中间轴承；13——行星轮轴；14——后箱体；14-1——后箱体的内孔；15——第二级行星轮；16——行星轮轴下风向轴承；17——太阳轮；18——后箱盖；19——发电机定子主轴承；20——涨紧力锁紧盘；21——输出轴；21-1——输出轴的上风向端；21-2——输出轴的下风向端；22——发电机转子；22-1-——发电机转子的上风向端；22-1-1——发电机转子的上风向端的内孔；22-2——发电机转子的下风向端；23——发电机定子；23-1——开孔；24——输出轴轴承；25——花键连接。
具体实施方式
下面介绍的是本发明的多个可能实施例中的一些，旨在提供对本发明的基本了解，并不旨在确认本发明的关键或决定性的要素或限定所要保护的范围。容易理解，根据本发明的技术方案，在不变更本发明的实质精神下，本领域的一般技术人员可以提出可相互替换的其他实现方式。因此，以下具体实施方式以及附图仅是对本发明的技术方案的示例性说明，而不应当视为本发明的全部或者视为对本发明技术方案的限定或限制。
下面的描述中，为描述的清楚和简明，并没有对图中所示的所有多个部件进行详细描述。附图中示出了为本领域普通技术人员提供本发明的完全能够实现的多个部件。对于本领域技术人员来说，许多部件的操作都是熟悉而且明显的。
在本文中，“前”、“后”是相对风力传递方向来定义的、“上风向”和“下风向”是根据在利用风力发电时风力发电设备相对风的方向来定义的；应当理解到，这些方向性术语是相对的概念，它们用于相对性的描述和澄清，不是要将任何实施方式或任何实施方式的部件的定向限定到具体的方向或定向。
在以下描述中，“行星轮”(例如第一级行星轮和第二级行星轮)虽然仅相对自身的行星轮轴自转且不相对太阳轮发生公转，但是在此“行星”的概念可以理解为“行星轮”是在太阳轮的基本圆周轨道上分散布置的方式。
图1所示为按照本发明一实施例的一体化的半直驱风力发电机传动链及其所用齿轮箱的结构示意图，图2所示为图1的半直驱风力发电机传动链及其所用齿轮箱的A-A截面示意图，图3所示为图1的半直驱风力发电机传动链及其所用齿轮箱的B-B截面示意图。以下结合图1至图3，对本发明实施例的齿轮箱以及使用该齿轮箱的半直驱风力发电机传动链进行说明。
如图1所示，在该实施例中，齿轮箱具有前箱体6、后箱体14、主轴5、行星架10，行星架10固定地设置在前箱体6和后箱体14之间，前箱体6置于行星架10的上风向，后箱体14置于行星架10的下风向，前箱体6与后箱体14之间形成齿轮箱的容纳空间。具体地，行星架10 上设有延伸到前箱体6和后箱体14之外的扭力臂10-3，通过扭力臂10-3可以将整个齿轮箱固定在风力发电机上。
在该实施例中，主轴5包括主轴上风向端5-1、主轴下风向端细径部5-2和主轴下风向端粗径部5-3。其中，主轴上风向端5-1通过主轴上风向轴承2支撑在前箱体的内孔6-1上，主轴下风向端细径部5-2通过主轴下风向轴承3支撑在行星架10上，主轴下风向端粗径部5-3与内齿圈7固定连接，内齿圈7与主轴5之间可以但不限于通过焊接或者螺栓固定连接；这样，实现了主轴5可旋转地设置在前箱体6和行星架10上，在外部的风力输入下主轴上风向端5-1旋转，进而带动主轴下风向端5-2旋转，尤其带动内齿圈7同步旋转。具体地，外部的风力输入可以通过主轴上风向端5-1所固定连接的轮毂连接法兰盘1实现，可选的，轮毂连接法兰盘1直接与风力发电机的轮毂相连、或者通过风机主轴与风力发电机的轮毂相连，并且轮毂连接法兰盘1可以通过螺栓与主轴5的主轴上风向端5-1连接。
在以上实施例中，主轴5通过主轴上风向轴承2以及主轴下风向轴承3实现双轴承支撑，更有利于承受主轴5的俯仰力矩，主轴5的旋转也更平稳。
继续如图1至图3所示，行星架10上设置有齿轮箱中的N个介轮8和N个第一级行星轮，其中N为大于或等于3的整数，例如如图所示的3个。每个第一级行星轮固定设置在相应的行星轮轴13上，每个行星轮轴13上固定设置有与第一级行星轮同步转动的第二级行星轮15，第二级行星轮15的直径大于第一级行星轮的直径，例如，第二级行星轮15与第一级行星轮的传动比的范围可以为2-3。
其中，行星轮轴13的第一端，也即上风向的一端，是通过行星轮轴上风向轴承4支撑在行星架的上风向辅助架体102的第一行星轮轴孔102-1上，行星轮轴13的中间段通过行星轮轴中间轴承12支撑在行星架的主架体101的行星轮轴孔10-1上，行星轮轴13的第二端，也即下风向的一端，是通过行星轮轴下风向轴承16支撑在后箱体14上；这样，实现了行星轮轴13可轴向旋转地设置在行星架10和所述后箱体14上，并且行星轮轴13的轴向旋转稳定性好。
并且，齿轮箱中包括一个可轴向旋转地设置在行星架10上并且一端伸出在所述后箱体14之外的输出轴21，该输出轴21上设置太阳轮 17，N个第二级行星轮15均与太阳轮17啮合，从而在太阳轮17处实现合流传动。
其中，每个介轮8都与内齿圈7啮合，对应每个介轮8设置介轮轴11，介轮8可以通过满滚子轴承9与介轮轴11组装在一起。在该实施例中，行星架10包括主架体101以及上风向辅助架体102，上风向辅助架体102在主架体101的上风向固定设置，它们二者之间形成的空间可以用来置放介轮8和第一级行星轮；具体地，如图1所示，每个介轮轴11的第一端(即上风向的一端)固定安装在行星架10的上风向辅助架体102的介轮轴孔102-2中，介轮轴11的第二端(即下风向的一端)固定安装在行星架10的主架体101的介轮轴孔10-2中，因此，每个介轮轴11是固定在行星架10上并不可自转(介轮8转动时相对固定的介轮轴11不发生轴向旋转)，N个介轮轴11和N个介轮8是分布在行星架10的中心的周围布置。第一级行星轮设置在行星轮轴13的上风向端，例如，设置在行星架10的上风向辅助架体102与主架体101之间；第二级行星轮15设置在行星轮轴13的下风向端，例如设置在行星架10的主架体101与后箱体之间。这样，实现了N个介轮8以及N个第一级行星轮基本布置在行星架10中，太阳轮17、N个第二级行星轮15布置在行星架10与后箱体14构成的空腔内，结构布置合理、紧凑。
通过引入多个介轮8，每个介轮8都与内齿圈7啮合，每个第一级行星轮与对应的介轮8啮合，从而，内齿圈7、介轮8与第一级行星轮构成第一级定轴传动副，内齿圈7与多个介轮8之间分流传动，从而分流地传动至多个第一级行星轮。这样的齿轮传动方式可以使第一级行星轮的直径较小地设置，非常有利于在相对紧凑的空间内提高传动比，并且传动效率高，也适合大功率传动。介轮8的具体直径以及第一级行星轮的具体直径可以根据具体传动比的大小要求而选择地设置。
进一步地，每个第二级行星轮15与太阳轮17啮合，第二级行星轮15与太阳轮17构成第二级定轴传动副，第二级行星轮15与太阳轮17之间实现合流传动。一般地，第二级行星轮15的直径远大于太阳轮17的直径，这样，也易于实现高传动比，增加输出轴21的旋转速度。第二级行星轮15与行星轮轴13之间的固定连接方式不是限制性的，例 如，过盈配合连接、或者平键加过盈配合连接，同样，太阳轮17与输出轴21之间的固定连接方式也不是限制性的，例如，可以太阳轮17的内部具有内花键，输出轴21的外部具有外花键，太阳轮17与输出轴21之间采用花键连接25实现固定连接。
需要理解的是，齿轮箱的传动比的大小是多方面的因素影响的，例如：内齿圈齿数与第一级行星轮的齿数比值、第二级行星轮的齿数与太阳轮的齿数的比值等。在本发明中通过在第一级行星轮与内齿圈7之间引入介轮7，至少可以有助于减小行星轮轴13的相对输出轴21的径向距离；在一定传递比范围内(传动比范围通常是齿轮箱传动的基本要求)，进而可以减小第二级定轴传动副结构的径向尺寸，从而，第二级定轴传动副结构的径向尺寸可以相比第一级定轴传动副的径向尺寸设计得更小，在后续的传动链的设计中，使发电机转子22包容或包含后箱体14的向下风向端突出的部分，也即是发电机转子22的在至少径向上可以包容或包含第一级定轴传动副(如图1所示)。因此，传动链的整体结构紧凑。
继续如图1至图3所示，输出轴21的上风向端21-1通过输出轴轴承24支撑在行星架10的主架体101上，输出轴21的下风向端21-2伸出在后箱体14之外，用于与发电机一体连接，在本发明实施例中，输出轴21作为齿轮箱的输出轴，其下风向端21-2与发电机转子22的上风向端22-1连接在一起，从而可以直接带动发电机转子22转动，这样输出轴21是支撑设置在行星架10与发电机转子22之间，虽然输出轴21有所加长，但是，实现了齿轮箱与发电机的一体化连接，也即实现了一体化的传动链，使传动链在轴向上的整体长度减小，结构集成度更高；并且，输出轴21的加长(因为其上风向端21-1处于行星架上、下风向端21-2在发电机转子22上)，长度甚至大于第二级行星轮15的宽度，形成较长的力臂，从而可以使得发电机转子22的俯仰力矩能够被一个较小的输出轴轴承24所承受；进一步，由输出轴21与发电机转子22的上风向端22-1的直接连接，减小了主轴5、输出轴21和发电机的主轴之间不对心的可能性，有利于提高风力发电机的性能和寿命。
在一实施例中，主轴5与输出轴21的轴线在同一直线上；输出轴轴承24的轴承座可以与行星架10的主架体101的中心孔10-4一体成 型；在又一替换实施例中，如图4所示，输出轴轴承24的轴承座固定安装在行星架10的主架体101的上风向面上，并且正对行星架下风向中心孔10-4处。
继续如图1所示，在本发明实施例的传动链中，发电机转子22不但包括上风向端22-1，而且包括下风向端22-2，该下风向端22-2通过发电机定子主轴承19支撑在发电机定子23的内孔上，这样，一体化地形成了本发明实施例的半直驱风力发电机传动链，非常有利于减小传动链的轴向尺寸。其中，后箱体14至少部分地向下风向突出设置以形成容纳至少太阳轮17、N个第二级行星轮15的空腔，并且，发电机转子22的径向尺寸大于第二级行星轮15相对输出轴21在径向上分布的尺寸范围，从而发电机转子22可容易地包容后箱体14的向下风向端突出的部分；同时，发电机定子23的最大径向尺寸可以大于或等于后箱体14的最大径向尺寸，发电机定子23包容发电机转子22，发电机定子23的圆周端面通过螺栓与后箱体14连接(方便发电机定子23拆卸)，这样，后箱体14、发电机转子22、发电机定子23形成如图1所示的一体集成式结构，发电机与齿轮箱很好地集成在一起，进一步减小传动链的轴向尺寸，结构更紧凑。具体地，发电机转子22和发电机定子23之间可以设置有气隙。
在该实施例中，输出轴21的下风向端21-2可以通过涨紧力锁紧盘20可拆卸地固定连接所述发电机转子22的上风向端22-1的内孔22-1-1上，并且，内孔22-1-1直径和后箱体14的内孔14-1直径均大于太阳轮17的直径(需要说明的是，输出轴21穿过后箱体14-1时，后箱体14可以不为输出轴21提供支撑)；发电机定子23上正对输出轴21处开设有开孔23-1，开孔23-1上可拆卸地安装有后箱盖18。这样，在发电机转子22的上风向端22-1的内孔22-1-1的直径和后箱体14的内孔14-1直径均大于太阳轮17的直径以及后箱盖18等部件可拆卸的情况下，整个传动链中转速最高、最容易出问题的太阳轮17及输出轴21都可以直接从发电机转子22的内孔中抽出，不用拆开传动链的整机，大大提供安装和维修的便利性。
以上实施例的齿轮箱以及其传动链在应用于风力发电设备时，其传动工作原理如下：
由风力发电机叶轮从风能中获取的扭矩通过轮毂连接法兰盘1输 入并传递给主轴5，带动主轴5转动的同时同步带动内齿圈7，内齿圈7与N个介轮8啮合，形成N分流传动，N个介轮8的转动可以分别传递功率给N个第一级行星轮，每个第一级行星轮的行星轮轴13带动第二级行星轮15同步转动，进一步，N个第二级行星轮15与同一个太阳轮17啮合，实现合流传动，太阳轮17通过花键连接带动输出轴21同步转动，从而实现输出轴21的高速输出；输出轴21进一步可以通过锁紧盘20带动发电机转子22转动，从而实现发电功能。
以上实施例的齿轮箱以及使用该齿轮箱的传动链具有以下多个优点的至少一个，尤其具有以下第(一)、(二)、第(三)方面的优点：
(一)相比于常规的两级NGW方案，尽管多设置了N个介轮，但是也省去了一个内齿圈、一个太阳轮、一个行星架以及一个中箱体，结构简单，成本降低，却依然能实现较大的传动比，非常适合于大功率的风力发电设备；
(二)整个传动链***高度集成，通过合理布置主轴、行星架等关键零部件，并且通过独特的齿轮布局设计、以及巧妙的装配设计，在径向尺寸相对有限的前提下，可以较大地缩短轴向尺寸；
(三)行星架是固定不动的，也即不是旋转的，通过其扭力臂可以固定在其他部件上，行星架及扭力臂能承受轮毂连接法兰盘输入的主扭矩以及整个传动链的重量，并能够承载主轴、前箱体、后箱体、介轮、行星轮轴及输出轴等；
(四)齿轮箱的主轴与输出轴的轴线可以在同一直线上，并且齿轮箱与发电机一体化连接，减小了主轴、输出轴和发电机主轴的不对心的可能性，提高了风力发电机的性能和寿命；
(五)在常规的两级NGW方案中，由两个行星架带动两级行星轮公转，需要对公转体进行润滑，而本发明中的行星轮是不公转的，其旋转中心轴，即行星轮轴，固定在刚体上(即行星轮轴的第一端通过行星轮轴上风向轴承支撑在行星架的上风向辅助架体的行星轮轴孔102-1上，行星轮轴的中间段通过行星轮轴中间轴承支撑在行星架的主架体的行星轮轴孔10-1上，行星轮轴的第二端通过行星轮轴下风向轴承支撑在后箱体上)，可以不需要对公转体进行润滑，从而简化了行星轮的润滑设计；
(六)在常规的两级NGW方案中，2×N个行星轮都是双面受载，而本发明中的齿轮箱中，仅有N个介轮承受双面载荷，从而减小了齿轮失效的可能性；
(七)发电机转子和发电机定子可以设计为径向尺寸大而轴向尺寸小，缩短了传动链的轴向尺寸；整个发电机结构包容了部分后箱体，进一步缩短了传动链的轴向尺寸，发电机定子的径向尺寸与后箱体的最大尺寸相等或接近，从而并不增加整个传动链的径向尺寸；因此，减小了整个传动链的体积，降低了传动链重量；
(八)发电机与齿轮箱之间的安装与拆卸极为简便；
(九)整个传动***中转速最高、最容易出问题的太阳轮及输出轴都可以直接从发电机转子的内孔中抽出，不用拆开整机，安装和维修非常方便；
(十)在传动链的径向尺寸小的情况下，但是输出轴的长度保持较大(这是因为输出轴的上风向端处于行星架上，输出轴的下风向端在发电机转子上)，其长度甚至大于第二级行星轮的宽度，可以形成较长的力臂，因此，可以使得发电机转子的俯仰力矩能够被一个较小的输出轴轴承所承受。
以上例子主要说明了本发明的齿轮箱以及使用该齿轮箱的传动链。尽管只对其中一些本发明的实施方式进行了描述，但是本领域普通技术人员应当了解，本发明可以在不偏离其主旨与范围内以许多其他的形式实施。因此，所展示的例子与实施方式被视为示意性的而非限制性的，在不脱离如所附各权利要求所定义的本发明精神及范围的情况下，本发明可能涵盖各种的修改与替换。

Claims (22)

  1. 一种齿轮箱，用于半直驱风力发电机传动链，该齿轮箱包括前箱体(6)、后箱体(14)、主轴(5)、行星架(10)；其特征在于：
    所述行星架(10)固定地设置在所述前箱体(6)和所述后箱体(14)之间，所述主轴(5)可旋转地设置在所述前箱体(6)和所述行星架(10)上；
    所述齿轮箱还包括：
    固定设置在所述主轴(5)上的内齿圈(7)；
    N个可轴向旋转地设置在所述行星架(10)和所述后箱体(14)上的行星轮轴(13)，每个所述行星轮轴(13)上设置有第一级行星轮和第二级行星轮(15)，N≥3；
    对应设置在每个第一级行星轮与所述内齿圈(7)之间的介轮(8)；以及
    一个输出轴(21)，该输出轴(21)的上风向端(21-1)可轴向旋转地设置在所述行星架(10)上并且其下风向端(21-2)伸出在所述后箱体(14)之外；
    设置在所述输出轴(21)上的太阳轮(17)；
    其中，N个所述介轮(8)以及N个所述第一级行星轮布置在所述行星架(10)中，所述太阳轮(17)、N个所述第二级行星轮(15)布置在所述行星架(10)与所述后箱体(14)构成的空腔内；
    其中，所述内齿圈(7)、介轮(8)与第一级行星轮构成第一级定轴传动副，所述第二级行星轮(15)与所述太阳轮(17)构成第二级定轴传动副。
  2. 如权利要求1所述的齿轮箱，其特征在于，所述主轴(5)包括主轴上风向端(5-1)、主轴下风向端细径部(5-2)和主轴下风向端粗径部(5-3)；
    其中，所述主轴上风向端(5-1)通过主轴上风向轴承(2)支撑在所述前箱体(6)的内孔(6-1)上，所述主轴下风向端细径部(5-2)通过主轴下风向轴承(3)支撑在所述行星架(10)上，所述主轴下风向端粗径部(5-3)与内齿圈(7)固定连接。
  3. 如权利要求2所述的齿轮箱，其特征在于，所述主轴上风向端(5-1)与轮毂连接法兰盘(1)连接。
  4. 如权利要求3所述的齿轮箱，其特征在于，所述轮毂连接法兰盘(1)直接与风力发电机的轮毂相连、或者通过风机主轴与风力发电机的轮毂相连。
  5. 如权利要求1所述的齿轮箱，其特征在于，所述第一级行星轮设置在所述行星轮轴(13)的上风向端，所述第二级行星轮(15)设置在所述行星轮轴(13)的下风向端。
  6. 如权利要求1所述的齿轮箱，其特征在于，所述行星轮轴(13)的第一端通过行星轮轴上风向轴承(4)支撑在所述行星架(10)的上风向辅助架体(102)的第一行星轮轴孔(102-1)上，所述行星轮轴(13)的中间段通过行星轮轴中间轴承(12)支撑在所述行星架(10)的主架体(101)的第二行星轮轴孔(10-1)上，所述行星轮轴(13)的第二端通过行星轮轴下风向轴承(16)支撑在所述后箱体(14)上。
  7. 如权利要求1所述的齿轮箱，其特征在于，对应每个所述介轮设置介轮轴(11)，所述介轮(8)通过满滚子轴承(9)与所述介轮轴(11)连接，所述介轮轴(11)的第一端固定安装在所述行星架(10)的上风向辅助架体(102)的第一介轮轴孔(102-2)中，所述介轮轴(11)的第二端固定安装在所述行星架(10)的主架体(101)的第二介轮轴孔(10-2)中。
  8. 如权利要求1所述的齿轮箱，其特征在于，所述太阳轮(17)与所述输出轴(21)之间采用花键连接(25)。
  9. 如权利要求1所述的齿轮箱，其特征在于，所述输出轴(21)的上风向端(21-1)通过输出轴轴承(24)支撑在所述行星架(10)上。
  10. 如权利要求9所述的齿轮箱，其特征在于，所述输出轴轴承(24)的轴承座与所述行星架的主架体(101)的中心孔(10-4)一体成型，或者所述输出轴轴承(24)的轴承座对应所述行星架(10)的主架体(101)的中心孔(10-4)、并固定安装在所述行星架(10)的主架体(101)的上风向面上。
  11. 如权利要求1所述的齿轮箱，其特征在于，所述内齿圈(7)与所述介轮(8)啮合，每个所述介轮(8)与相应的第一级行星轮啮合，多个所述第二级行星轮(15)与所述太阳轮(17)啮合，所述第 二级行星轮(15)的直径大于所述第一级行星轮的直径。
  12. 如权利要求1所述的齿轮箱，其特征在于，所述主轴(5)与所述输出轴(21)的轴线基本在同一直线上。
  13. 如权利要求1所述的齿轮箱，其特征在于，所述行星架(10)上设有径向地延伸到所述前箱体(6)和后箱体(14)之外的扭力臂(10-3)。
  14. 一种使用权利要求1-13中任一项所述的齿轮箱的一体化的半直驱风力发电机传动链，其特征在于：所述输出轴(21)的下风向端(21-2)与发电机转子(22)的上风向端(22-1)连接以带动所述发电机转子(22)转动，所述发电机转子(22)的下风向端(22-2)通过发电机定子主轴承(19)支撑在发电机定子(23)的内孔上。
  15. 如权利要求14所述的半直驱风力发电机传动链，其特征在于，所述发电机转子(22)和发电机定子(23)之间有气隙。
  16. 如权利要求14所述的半直驱风力发电机传动链，其特征在于，所述后箱体(14)部分地向下风向端突出设置以形成容纳至少所述太阳轮(17)和N个所述第二级行星轮(15)的空腔，并且，所述发电机转子(22)包容后箱体(14)的向下风向端突出的部分。
  17. 如权利要求15所述的半直驱风力发电机传动链，其特征在于，所述发电机定子(23)的最大径向尺寸大于或等于所述后箱体(14)的最大径向尺寸，所述发电机定子(23)包容所述发电机转子(22)。
  18. 如权利要求14所述的半直驱风力发电机传动链，其特征在于，所述发电机转子(22)的上风向端(22-1)的内孔(22-1-1)直径和后箱体(14)的内孔(14-1)直径均大于所述太阳轮(17)的直径。
  19. 如权利要求14所述的半直驱风力发电机传动链，其特征在于，所述发电机定子(23)可拆卸地固定连接在所述后箱体(14)上。
  20. 如权利要求14所述的半直驱风力发电机传动链，其特征在于，在所述发电机定子(23)上正对所述输出轴(21)处设置有开孔(23-1)，所述开孔(23-1)上可拆卸地安装有后箱盖(18)。
  21. 如权利要求14所述的半直驱风力发电机传动链，其特征在于，所述输出轴(21)的下风向端(21-2)通过涨紧力锁紧盘(20)可拆卸地固定连接所述发电机转子(22)的上风向端(22-1)的内孔(22-1-1)上。
  22. 一种风力发电设备，其特征在于，包括如权利要求14至21项 中任一项所述的一体化的半直驱风力发电机传动链。
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