CN107781397B - Wind power generation speed increasing gear box - Google Patents
Wind power generation speed increasing gear box Download PDFInfo
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- CN107781397B CN107781397B CN201711187350.3A CN201711187350A CN107781397B CN 107781397 B CN107781397 B CN 107781397B CN 201711187350 A CN201711187350 A CN 201711187350A CN 107781397 B CN107781397 B CN 107781397B
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- 238000010248 power generation Methods 0.000 title claims abstract description 37
- 238000007667 floating Methods 0.000 claims abstract description 78
- 230000005540 biological transmission Effects 0.000 claims abstract description 30
- 230000008878 coupling Effects 0.000 claims description 23
- 238000010168 coupling process Methods 0.000 claims description 23
- 238000005859 coupling reaction Methods 0.000 claims description 23
- 230000007246 mechanism Effects 0.000 claims description 9
- 230000008901 benefit Effects 0.000 abstract description 4
- 230000000694 effects Effects 0.000 description 5
- 235000000621 Bidens tripartita Nutrition 0.000 description 4
- 240000004082 Bidens tripartita Species 0.000 description 4
- 238000005516 engineering process Methods 0.000 description 4
- 208000006637 fused teeth Diseases 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000001133 acceleration Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000012545 processing Methods 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000005405 multipole Effects 0.000 description 1
- 230000035945 sensitivity Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Classifications
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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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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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
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H57/082—Planet carriers
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
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Abstract
The application provides a wind power generation speed-increasing gear box, which comprises a low-speed planetary gear train, a medium-speed planetary gear train and a high-speed cylindrical gear train, wherein the low-speed planetary gear train and the medium-speed planetary gear train are identical in structural arrangement, the input end of a low-speed planetary carrier inputs transmission torque and initial rotation speed, two low-speed planetary gears are arranged around a low-speed sun gear, one end of the external teeth of a low-speed floating coupler is in floating connection with the low-speed sun gear, and the other end of the external teeth of the low-speed floating coupler is in tooth connection with the input end of the medium-speed planetary carrier; one end of the outer tooth of the intermediate-speed-stage floating coupler is in floating connection with the intermediate-speed-stage sun gear, and the other end of the outer tooth of the intermediate-speed-stage floating coupler is connected with an input shaft gear of the high-speed-stage cylindrical gear train; the high-speed cylindrical gear train is output through the speed increasing function of the high-speed large gear and the high-speed small gear shaft. The wind power generation speed-increasing gearbox has the advantages of overcoming the unbalanced load problem generated in the transmission process of the planetary gear train and realizing uniform load transmission in the transmission structure of the planetary gear train.
Description
Technical Field
The application relates to the field of power generation gearboxes, in particular to a wind power generation speed-increasing gearbox.
Background
Because of the advantages of compact structure, small volume, high transmission efficiency, large transmission ratio and the like, the planetary gear transmission is widely applied to the fields of wind driven generator transmission systems, aviation power transmission systems, vehicle transmission systems and the like. Wind energy is one of clean, pollution-free and renewable important energy sources in the world, and along with energy shortage and increasing deterioration of ecological environment, the importance of new energy power generation technology is widely recognized. The gearbox is one of the key components of the wind power generation equipment, and the load born by the gearbox is very complex and is mainly used for speed-increasing transmission. The gear box is one of the components with the highest failure rate of the wind generating set, and in order to reduce the failure rate of the gear box and improve the service life and reliability of the gear box, the impact resistance of the planetary gear transmission needs to be studied intensively.
The development of wind power equipment technology is very rapid, such as variable speed constant frequency technology, variable pitch and variable speed, full power conversion technology, direct drive and semi-direct drive wind turbine generators. The direct-drive wind turbine generator adopts a mode that the multipole motor is directly connected with the impeller for driving, a gear box is omitted, and the share of the installed machine is continuously increased in recent years. However, for technical and cost reasons, wind turbines with speed increasing gearboxes will still dominate the market for a long time in the future. Moreover, the structure of the wind power generation speed increasing gearbox is quite large at present and is mostly designed by referring to transmission power and speed increasing ratio, but for high-power wind power generation, if a planet carrier floats in the rotating process, larger torque is caused, and the service life of the power generation gearbox is seriously damaged and the gearbox is caused to fail.
Accordingly, there is a great need in the art to develop a wind turbine gearbox that provides uniform force distribution.
Disclosure of Invention
The application aims to provide a wind power generation speed-increasing gearbox which can overcome the unbalanced load problem generated in the transmission process of a planetary gear train and realize uniform load transmission in a planetary gear train transmission structure.
The application provides a wind power generation speed-increasing gear box, which comprises a low-speed planetary gear train, a medium-speed planetary gear train and a high-speed cylindrical gear train, wherein the structure of the low-speed planetary gear train is the same as that of the medium-speed planetary gear train,
the load balancing mechanism in the low-speed planetary gear train is a low-speed sun gear and external teeth of a low-speed floating coupler in floating connection with the low-speed sun gear; the uniform load mechanism in the medium-speed planetary gear train is a medium-speed sun gear and external teeth of a medium-speed floating coupler in floating connection with the medium-speed sun gear;
the input end of the low-speed-level planet carrier inputs transmission torque and initial rotation speed, two low-speed-level planet gears are arranged around a low-speed-level sun gear, one end of the outer tooth of the low-speed-level floating coupler is in floating connection with the low-speed-level sun gear, and the other end of the outer tooth of the low-speed-level floating coupler is in tooth connection with the input end of the medium-speed-level planet carrier;
the medium-speed planetary gear train is a second-stage planetary gear train, the input end of the medium-speed planetary carrier is the input end of the planetary carrier of the second-stage planetary gear train, two medium-speed planetary gears are arranged around a medium-speed sun gear, one end of the outer teeth of the medium-speed floating coupler is in floating connection with the medium-speed sun gear, and the other end of the outer teeth of the medium-speed floating coupler is in gear connection with the input shaft of the high-speed cylindrical gear train;
the high-speed input shaft is connected with the high-speed large gear through two keys, and finally is output through the speed increasing function of the high-speed large gear and the high-speed small gear shaft, and the high-speed small gear shaft is symmetrically arranged relative to the high-speed large gear, and the generated force is symmetrically distributed.
Preferably, the cross section of the floating tooth coupler in the tooth width direction adopts a straight tooth structure.
Preferably, the low-speed stage planet carrier is structurally characterized in that a shaft and planet carrier integrated double-arm split type planet carrier is adopted.
Compared with the prior art, the wind power generation speed increasing gearbox has the following beneficial effects:
1. the wind power generation speed-increasing gearbox adopts the two-stage planetary gear train and the one-stage cylindrical split transmission system, so that the problem of unbalanced load generated in transmission of the planetary gear train can be solved, namely, the uniform load transmission can be better realized by the planetary gear transmission structure.
2. The low-speed planetary gear train and the medium-speed planetary gear train in the wind power generation speed-increasing gear box adopt the arrangement of the same structure, so that the whole structure is compact and reasonable, and the force generated in the wind power generation process is symmetrical.
3. The application uses two sun gears as load balancing devices in the wind power generation speed increasing gear box, although the floating form of the sun gear and the planet carrier is better than that of using a single sun gear as a floating effect, the speed increasing gear is mainly used for wind power generation, and the transmission torque is larger, so that the planet carrier is also designed to be larger in size, and the planet carrier is used as the floating condition because the planet carrier is relatively lighter in weight and slower in speed, so that larger torque cannot be generated, and the sun gear is used as the load balancing mechanism for the conditions, so that the speed increasing gear is reasonable relative to high-power wind power generation.
4. The planetary gear transmission in the wind power generation speed-increasing gearbox is connected by using the floating tooth type coupling, so that the uniform load effect can be realized.
Drawings
The drawings, which will be used in connection with the present application, will be briefly described below, and it will be apparent that the drawings are only for explaining the concept of the present application.
FIG. 1 is a cross-sectional view of a wind power generation step-up gearbox construction of the present application;
FIG. 2 is a cross-sectional view of a single tooth floating tooth coupling;
FIG. 3 is a cross-sectional view of a double-tooth floating tooth coupling;
FIG. 4 is a cross-sectional view of a floating tooth coupling having a straight tooth cross-sectional shape in the tooth width direction;
FIG. 5 is a schematic cross-sectional view of a floating tooth coupling of a tooth side centering style;
FIG. 6 is a schematic cross-sectional view of a floating tooth coupling of a tooth side centering style II;
FIG. 7 is a cross-sectional view of a double arm split planetary carrier;
FIG. 8 is a cross-sectional view of the double arm split type carrier in the A-A direction.
Summarizing the reference numerals:
1. input end 2 of low-speed planet carrier and low-speed sun gear
3. External teeth of low-speed planetary gear 4 and low-speed floating coupler
5. Low-speed planetary carrier output end 6 and low-speed planetary wheel shaft
7. Medium-speed planetary wheel shaft 8 and medium-speed planetary frame input end
9. Intermediate stage planetary gear 10, intermediate stage planetary carrier output end
11. External teeth of medium-speed sun gear 12 and medium-speed floating coupler
13. High-speed gear 14, key
15. High-speed pinion shaft 16, support shaft
Detailed Description
Hereinafter, an embodiment of a wind power generation speed increasing gearbox of the present application will be described with reference to the accompanying drawings.
The examples described herein are specific embodiments of the present application, which are intended to illustrate the inventive concept, are intended to be illustrative and exemplary, and should not be construed as limiting the application to the embodiments and scope of the application. In addition to the embodiments described herein, those skilled in the art can adopt other obvious solutions based on the disclosure of the claims and specification, including any obvious substitutions and modifications to the embodiments described herein.
The drawings in the present specification are schematic diagrams, assist in explaining the concept of the present application, and schematically represent interrelationships of the parts. Note that the relationship of the portions of the embodiments of the present application is clearly shown for convenience. The same or similar reference numerals are used to denote the same or similar parts.
Fig. 1 is a cross-sectional view of a wind power generation speed increasing gearbox structure of the present application, and as shown in fig. 1, the present application provides a wind power generation speed increasing gearbox, which comprises a low-speed planetary gear train, a medium-speed planetary gear train and a high-speed cylindrical gear train, namely, the system of the wind power generation speed increasing gearbox of the present application adopts a two-stage planetary gear train and a one-stage cylindrical split transmission system. The low-speed planetary gear train and the medium-speed planetary gear train are identical in structural arrangement, and the low-speed sun gear 2 and the medium-speed sun gear 11 serve as load balancing devices. The wind power generation speed-increasing gearbox is compact and reasonable in structure, and the generated force is symmetrically distributed, so that the planetary gear transmission structure can well realize uniform load transmission.
The load balancing mechanism in the low-speed planetary gear train is a low-speed sun gear 2 and low-speed floating coupler external teeth 4 in floating connection with the low-speed sun gear; the uniform load mechanism in the intermediate-speed planetary gear train is an intermediate-speed sun gear 11 and intermediate-speed floating coupler external teeth 12 which are in floating connection with the intermediate-speed sun gear.
The transmission torque and the initial rotation speed are input by the low-speed-level planet carrier input end 1, two low-speed-level planet gears 3 are arranged around the low-speed-level sun gear 2, the low-speed-level planet carrier output end 5 is connected with the low-speed-level planet gears 3, one end of the low-speed-level floating coupler external teeth 4 is in floating connection with the low-speed-level sun gear 2, the other end of the low-speed-level floating coupler external teeth 4 is in tooth connection with the medium-speed-level planet carrier input end 8, namely one end of the low-speed-level floating coupler external teeth 4 in tooth connection with the medium-speed-level planet carrier input end 8 is a low-speed-level planet gear train output end, and first-level acceleration is realized in the low-speed-level planet gear train.
The medium-speed planetary gear train is a second-stage planetary gear train, the medium-speed planetary carrier input end 8 is a planetary carrier input end of the second-stage planetary gear train, two medium-speed planetary gears 9 are arranged around a medium-speed sun gear 11, the medium-speed planetary carrier output end 10 is connected with the medium-speed planetary gears 9, one end of the medium-speed floating coupling external teeth 12 is in floating connection with the medium-speed sun gear 11, the other end of the medium-speed floating coupling external teeth 12 is in gear connection with an input shaft of the high-speed cylindrical gear train, and second-stage acceleration is realized in the medium-speed planetary gear train.
The high-speed input shaft 20 is connected with the high-speed large gear 13 by two keys 14, and finally outputs through the speed increasing function of the high-speed large gear 13 and the high-speed small gear shaft 15, and the output meets a certain rotating speed requirement. The high-speed pinion shaft 15 is symmetrically disposed with respect to the high-speed large gear 13, and the generated forces are symmetrically distributed.
It should be noted that the main function of the outer gear 4 of the low-speed floating coupling and the outer gear 12 of the medium-speed floating coupling is to serve as a connection function and it is in floating connection with the sun gear of the planetary gear train, so that the sun gear can serve as a load balancing function.
In addition, the low-speed planetary gear train load balancing mechanism of the wind power generation speed increasing gearbox is characterized in that a low-speed sun gear 2 is in floating connection with a low-speed floating coupler external tooth 4, and the other end of the low-speed floating coupler external tooth 4 is in tooth connection with a medium-speed planetary carrier input end 8. Because the middle-speed planet carrier part is provided with a bearing, the input part of the middle-speed planet carrier cannot float, wherein the middle-speed planet wheel 9 is a uniform load mechanism, and the middle-speed sun wheel 11 is in floating connection with the outer teeth of the middle-speed floating coupler, so that the floating effect is achieved. Because the wind power generation speed increasing gear box uses two sun gears as load balancing devices, although the floating form of the sun gear and the planet carrier is better than that of using a single sun gear as floating, the speed increasing gear is mainly used for wind power generation, and the transmission torque is larger, so that the planet carrier is also designed to be larger in size, and the planet carrier is used as floating under the condition that the planet carrier is relatively lighter in weight and slower in speed, so that larger torque cannot be generated, and the sun gear is designed to be used as a load balancing structure for the conditions, and is more reasonable compared with high-power wind power generation. In addition, two pinion shafts are used at the output end and are symmetrically arranged, so that the force distribution is more reasonable.
In a further embodiment of the application, the planetary gear drive connection uses a floating tooth coupling to achieve uniform load. The floating tooth type coupling has a structure of single tooth and double tooth. Fig. 2 is a cross-sectional view of a single tooth floating tooth coupling, as shown in fig. 2, which requires a sufficient length Lg. FIG. 3 is a cross-sectional view of a double-tooth floating tooth coupling, as shown in FIG. 3, which is more complex than a single tooth, yet allows for both tilting and radial translational movement of the floating gear, which reduces K β Thus in order to reduce K β The floating tooth coupling of the present application uses a double tooth coupling.
The cross section shape of the floating tooth type coupler in the tooth width direction is provided with two types of straight teeth and drum-shaped teeth, wherein the cross section shape is of a straight tooth type structure, and the floating tooth type coupler has the advantages of simple processing, small inclined angle, no more than 30', easy occurrence of loading of the end parts of the gear teeth during running, large tooth surface abrasion and lower strength and service life. The drum-shaped tooth structure with the cross section of 2 degrees can be inclined relatively, the gear teeth are well loaded, the floating sensitivity is high, and the strength and the service life are improved compared with those of straight teeth. Fig. 4 is a cross-sectional view of a floating tooth type coupling having a straight tooth type cross-sectional shape in the tooth width direction, and as shown in fig. 4, in order to make the wind power generation speed increasing gearbox of the present application simple and compact in structure, reasonable in design, a floating tooth type coupling having a straight tooth type cross-sectional shape in the tooth width direction is preferably selected.
In addition, the centering mode of the coupler also has two modes of outer diameter centering and tooth side centering, and the benefit of tooth side centering relative to outer diameter centering is that the centering mode has an active centering effect, is favorable for uniformity among loads between teeth of the coupler, and adopts the tooth side centering method.
Fig. 5 is a schematic cross-sectional view of a floating tooth clutch of the tooth side centering type, fig. 6 is a schematic cross-sectional view of a floating tooth clutch of the tooth side centering type, and as shown in fig. 5 and 6, the engagement of the floating tooth clutch is not generally standardized due to the limitation of structural conditions, and the tooth angle α thereof is generally not used 0 =20° to 30 °. The external gear and the internal gear can be meshed with each other in a shifting manner, and the shifting coefficients x1 and x2 of the external gear and the internal gear are equal in size and same in direction under the shifting condition, and x=0.3-0.5 can be usually adopted. The main geometry is calculated as follows:
pitch circle diameter: d, d g1 ＝d g2 ＝mz
Diameter of tip circle:
root circle diameter:
tooth profile mean pressure angle:
in the middle of
Since the method of tooth side centering is used, the addendum coefficient and dedendum coefficient at this point are as follows:
the basic geometric parameters of the low-speed shaft and the medium-speed shaft can be obtained according to the above calculation formula, and the following table is referred to:
common planet carrier structural forms include a double-wall integrated type, a double-wall split type and a single-wall type. Fig. 7 is a sectional view of the double-arm split type carrier, and fig. 8 is a sectional view of the double-arm split type carrier in A-A direction, as shown in fig. 7 and 8, wherein the low-speed stage carrier in the wind power generation speed increasing gearbox of the present application adopts a double-arm split type carrier with an integrated shaft and carrier, and the material is 40Cr as same as the input large shaft, in consideration of assembly and processing. The medium-speed stage planet carrier structure also adopts a split type planet carrier, and the material is 40Cr.
In a further embodiment of the application, the bearings of the low-speed planetary axle 6 are self-aligning roller bearings, model 22338, with a diameter d=190 mm and a length l=760 mm.
In a further embodiment of the application, the diameter d=130 mm and the length l=540 mm of the intermediate-stage planetary axle 7 are self-aligning roller bearings, model 22326. Wherein, the medium speed shaft and the medium speed stage planet carrier are integrated, and the medium speed stage planet carrier is connected with the low speed cascade shaft device, so the size of the medium speed stage input shaft is determined by comprehensive consideration. The input rotating speed of the medium speed shaft is 69r/min, and the output rotating speed is 372r/min. The middle speed shaft is connected with the sun gear of the low speed stage planetary gear through a floating coupling, and the middle speed shaft is integrated with the planet carrier, so that the middle speed shaft is only provided with two parts of a bearing and a positioning shaft shoulder, the problems of bearing installation and coupling are considered, the diameter d1=460 mm and the length l1=56 mm of the middle speed shaft are considered, the diameter d2=490 mm and the length l2=20 mm of the positioning shaft shoulder are considered, the final stage floating coupling is connected with a transmission shaft of a high speed stage, and the bearing is needed to be installed at the high speed stage, so that the bearing is not installed at the output end of the middle speed stage, and the type of the bearing installed at the input end of the middle speed stage is 61892.
In a further embodiment of the application, since the high-speed input is connected to the medium-speed coupling and the shaft is also connected to the gearwheel by means of the key 14, it is possible to determine the diameter d=280 mm and the length l=135 mm of the section associated with the bearing, the positioning of which is by means of the positioning shoulder of the shaft itself and the protruding part of the gearwheel, the diameter d2=302 mm and the length l2=20 mm of the positioning shoulder of the shaft being the bearing mounting point of the support shaft 16, the bearing model of the high-speed input being NJ1056.
The embodiment of the wind power generation step-up gearbox of the present application has been described above. The specific features of the wind power generation step-up gearbox of the present application may be specifically designed according to the effects of the features disclosed above, all of which are within the ability of a person skilled in the art. Moreover, the above disclosed features are not limited to the disclosed combinations with other features, and other combinations between features may be made by those skilled in the art in accordance with the purpose of the present application to achieve the purpose of the present application.
Claims (1)
1. The wind power generation speed-increasing gear box is characterized by comprising a low-speed planetary gear train, a medium-speed planetary gear train and a high-speed cylindrical gear train, wherein the low-speed planetary gear train and the medium-speed planetary gear train are identical in structural arrangement, and the wind power generation speed-increasing gear box comprises a high-speed cylindrical gear train,
the load balancing mechanism in the low-speed planetary gear train is a low-speed sun gear and external teeth of a low-speed floating coupler in floating connection with the low-speed sun gear; the uniform load mechanism in the medium-speed planetary gear train is a medium-speed sun gear and external teeth of a medium-speed floating coupler in floating connection with the medium-speed sun gear;
the input end of the low-speed-level planet carrier inputs transmission torque and initial rotation speed, two low-speed-level planet gears are arranged around a low-speed-level sun gear, one end of the outer tooth of the low-speed-level floating coupler is in floating connection with the low-speed-level sun gear, and the other end of the outer tooth of the low-speed-level floating coupler is in tooth connection with the input end of the medium-speed-level planet carrier;
the medium-speed planetary gear train is a second-stage planetary gear train, the input end of the medium-speed planetary carrier is the input end of the planetary carrier of the second-stage planetary gear train, two medium-speed planetary gears are arranged around a medium-speed sun gear, one end of the outer teeth of the medium-speed floating coupler is in floating connection with the medium-speed sun gear, and the other end of the outer teeth of the medium-speed floating coupler is in gear connection with the input shaft of the high-speed cylindrical gear train;
the high-speed input shaft is connected with a high-speed large gear through two keys, and is finally output through the speed increasing function of the high-speed large gear and a high-speed small gear shaft, and the high-speed small gear shaft is symmetrically arranged relative to the high-speed large gear, and the generated force is symmetrically distributed;
wherein, the cross section shape of the floating tooth type coupling in the tooth width direction adopts a straight tooth type structure;
the structure of the low-speed-level planet carrier adopts a double-arm split type planet carrier with an integrated shaft and a planet carrier.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711187350.3A CN107781397B (en) | 2017-11-24 | 2017-11-24 | Wind power generation speed increasing gear box |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711187350.3A CN107781397B (en) | 2017-11-24 | 2017-11-24 | Wind power generation speed increasing gear box |
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| CN107781397A CN107781397A (en) | 2018-03-09 |
| CN107781397B true CN107781397B (en) | 2023-11-28 |
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