CN203114536U - Power transmission system for wind turbine - Google Patents
Power transmission system for wind turbine Download PDFInfo
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- CN203114536U CN203114536U CN2012206799813U CN201220679981U CN203114536U CN 203114536 U CN203114536 U CN 203114536U CN 2012206799813 U CN2012206799813 U CN 2012206799813U CN 201220679981 U CN201220679981 U CN 201220679981U CN 203114536 U CN203114536 U CN 203114536U
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- Prior art keywords
- planet carrier
- main shaft
- transfer system
- dynamic transfer
- tooth group
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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
- F16H1/2854—Toothed gearings for conveying rotary motion with gears having orbital motion involving conical gears
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- A—HUMAN NECESSITIES
- A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
- A61C—DENTISTRY; APPARATUS OR METHODS FOR ORAL OR DENTAL HYGIENE
- A61C8/00—Means to be fixed to the jaw-bone for consolidating natural teeth or for fixing dental prostheses thereon; Dental implants; Implanting tools
- A61C8/0048—Connecting the upper structure to the implant, e.g. bridging bars
- A61C8/005—Connecting devices for joining an upper structure with an implant member, e.g. spacers
- A61C8/0066—Connecting devices for joining an upper structure with an implant member, e.g. spacers with positioning means
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- A—HUMAN NECESSITIES
- A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
- A61C—DENTISTRY; APPARATUS OR METHODS FOR ORAL OR DENTAL HYGIENE
- A61C8/00—Means to be fixed to the jaw-bone for consolidating natural teeth or for fixing dental prostheses thereon; Dental implants; Implanting tools
- A61C8/0048—Connecting the upper structure to the implant, e.g. bridging bars
- A61C8/005—Connecting devices for joining an upper structure with an implant member, e.g. spacers
- A61C8/0068—Connecting devices for joining an upper structure with an implant member, e.g. spacers with an additional screw
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- A—HUMAN NECESSITIES
- A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
- A61C—DENTISTRY; APPARATUS OR METHODS FOR ORAL OR DENTAL HYGIENE
- A61C8/00—Means to be fixed to the jaw-bone for consolidating natural teeth or for fixing dental prostheses thereon; Dental implants; Implanting tools
- A61C8/0048—Connecting the upper structure to the implant, e.g. bridging bars
- A61C8/0078—Connecting the upper structure to the implant, e.g. bridging bars with platform switching, i.e. platform between implant and abutment
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- 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
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- 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
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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
- F16H1/2809—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels
- F16H1/2827—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels by allowing limited movement of the planet carrier, e.g. relative to its shaft
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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
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
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- A—HUMAN NECESSITIES
- A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
- A61C—DENTISTRY; APPARATUS OR METHODS FOR ORAL OR DENTAL HYGIENE
- A61C8/00—Means to be fixed to the jaw-bone for consolidating natural teeth or for fixing dental prostheses thereon; Dental implants; Implanting tools
- A61C8/0048—Connecting the upper structure to the implant, e.g. bridging bars
- A61C8/005—Connecting devices for joining an upper structure with an implant member, e.g. spacers
- A61C8/006—Connecting devices for joining an upper structure with an implant member, e.g. spacers with polygonal positional means, e.g. hexagonal or octagonal
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- A—HUMAN NECESSITIES
- A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
- A61C—DENTISTRY; APPARATUS OR METHODS FOR ORAL OR DENTAL HYGIENE
- A61C8/00—Means to be fixed to the jaw-bone for consolidating natural teeth or for fixing dental prostheses thereon; Dental implants; Implanting tools
- A61C8/0048—Connecting the upper structure to the implant, e.g. bridging bars
- A61C8/005—Connecting devices for joining an upper structure with an implant member, e.g. spacers
- A61C8/0069—Connecting devices for joining an upper structure with an implant member, e.g. spacers tapered or conical connection
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- 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
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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
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
- F16H2048/085—Differential gearings with gears having orbital motion comprising bevel gears characterised by shafts or gear carriers for orbital gears
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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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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Health & Medical Sciences (AREA)
- Mechanical Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Combustion & Propulsion (AREA)
- Chemical & Material Sciences (AREA)
- Sustainable Energy (AREA)
- Oral & Maxillofacial Surgery (AREA)
- General Health & Medical Sciences (AREA)
- Public Health (AREA)
- Veterinary Medicine (AREA)
- Animal Behavior & Ethology (AREA)
- Epidemiology (AREA)
- Dentistry (AREA)
- Orthopedic Medicine & Surgery (AREA)
- Wind Motors (AREA)
- Gear Transmission (AREA)
Abstract
The utility model discloses a power transmission system for a wind turbine. The power transmission system (10) for increasing the rotating speed of a rotor of the wind turbine is provided with a main shaft (16) for driving around a main axis (14) through the rotor, and is further provided with a support structure which comprises at least one bearing (18, 20) for supporting the main shaft (16) to rotate around the main axis (14), and a gearbox (25) which is provided with gearbox shells (24, 30) rigidly connected to the support structure (60), and a planet carrier (26); a connecting member (50) is used for connecting the planet carrier (26) to the main shaft (16); the main shaft (16) is relevant to a gear group (74) protruding outwards along a radial direction; the planet carrier (26) is relevant to a gear group (76) protruding inwards along the radial direction; the connecting member comprises a gear group (78) which is jointed with the gear group (74) relevant to the main shaft (16) and protrudes inwards along the radial direction; and the connecting member further comprises a gear group (79) which is jointed with the gear group (76) relevant to the planet carrier (26) and protrudes outwards along the radial direction.
Description
Technical field
The utility model relates to dynamic transfer system.More specifically, the utility model relates to the dynamic transfer system for wind turbine.
Background technique
Wind turbine generally includes the rotor that has by wind-driven large-scale blade.Blade changes into the rotary machine energy with the kinetic energy of wind.Mechanical energy drives one or more generators usually to produce electric power.Therefore, wind turbine comprises that dynamic transfer system is to handle and rotary machine can be changed into electric energy.Dynamic transfer system is called as wind turbine " dynamical system " sometimes.The part from the wind turbine rotor to the generator of dynamic transfer system is called as power train.Realize the rotating speed of wind turbine rotor is increased to the speed that generator requires by the gear-box between wind turbine rotor and the generator.Therefore, gear-box forms the part of dynamic transfer system and is used for the input from the low speed of wind turbine rotor, high torque (HT) is changed into the output than low torque, fair speed for generator.
A plurality of other rotor loadings that the wind turbine dynamic transfer system is caused by variable wind condition, dynamic interaction, control aspect, gravity and other factors to cabin structure and the pylon transmission of supporting described system.
The Mod-1 wind turbine generator of the DOE/NASA/0058-79/2-that delivered on May 1st, 1979 volume 1 is analyzed and design report (" Mod-1Wind Turbine Generator Analysis and Design Report ") discloses and a kind ofly is intended to handle these loads by the route method of dynamic transfer system.Especially, this report relates to conduct for increasing the turbogenerator of the dynamic transfer system of the rotating speed of the rotor of wind turbine.It has the floating axle assembly that is configured to drive and rotor is connected to around main axis by rotor gear-box.Base plate is as the supporting structure of main bearing, and supporting spindle is around the main axis rotation and through its transmitting torque.All devices in the bearing plate cabin comprises rotor assembly and gear-box, and provides rigid foundation for all devices that is installed in the cabin.Described system comprises three rank parallel-axes gears casees with the housing that is rigidly connected to base plate, and its supporting gear case minor axis rotates around main axis, limits other motions of input link simultaneously.The gear-box minor axis is connected to main shaft via the flex link that is installed on each end of main shaft.Flex link has the terminal part relevant with main shaft, the terminal part of being correlated with the gear-box minor axis and is connected to each terminal part to adapt to the linkage member of inclination and side direction misalignment and axial float.Flex link comprises the gear coupling with crooked spline tooth coupling.The radially projecting teeth that flex link comprises the terminal part with projecting teeth radially and has a radially projecting teeth that engages described terminal part is to limit the linkage member of two gears engagements.In the engagement of each gear one group radially projecting teeth have straight substantially profile, another group has the profile that axially is crown.
The DOE/NASA/0163-2 that l day in August, 1980 delivers, Mod-0A 200kW wind turbine generator analyze and the open another kind of method of handling by the load paths of dynamic transfer system of design report (" Mod-0A200kW Wind Turbine Generator Analysis and Design Report ").Especially, this report relates to conduct for increasing the turbogenerator of the dynamic transfer system of the rotating speed of the rotor of wind turbine.Rotor blade is attached to the hub on the lower velocity shaft.Lower velocity shaft is by two big bearings supportings, and the housing of two big bearings is by bearing plate, and bearing reacts on vertically, sidepiece and axial load.Increase device or gear-box as the speed of three rank parallel-axes gears casees and have housing by bearing plate.Housing supporting input shaft, even have side direction or inclination misalignment, torque also is delivered to input shaft.Main shaft is connected to the gear-box input link by the flex link that the contrary wind end with lower velocity shaft is connected to the input shaft of gear-box.Flex link comprises the hub relevant with main shaft, the hub of being correlated with input link and the linkage member that is connected to each terminal part.Each hub has the tooth that can adapt to misalignment.Hub has radially projecting teeth, and linkage member has the radially projecting teeth of the radially projecting teeth of engage hub, thereby limits two gear engagements.Each hub has and is crown to adapt to the external gear teeth of misalignment.The flange component that two bolts get up is around hub.
Above the flex link of kind shown in two files be known, for example the Gearflex GFV coupling shown in Renold Power Transmission company in October, 2005 catalogue has one group of inside projecting teeth and the one group of outside projecting teeth that partly engages with corresponding terminal.
The feature of the open similar arrangement of WO2010/052022.
In epicyclic train, the function of planet carrier is torque load(ing) is delivered to planetary pinion from input shaft.Especially, in wind turbine application, planet carrier is also with the weight transmitting return air power turbine rotor axle of gear-box.
These loads can cause the planet carrier distortion, cause with the next item down or multinomial:
The misalignment of gear rank;
Because overcome the sphere of activities of gear-box assembling set, extra load is applied to gear-box; And
Too much vibration.
Increasing planet carrier rigidity comprises with the method for avoiding these problems:
Thickening planet carrier wall;
Change material into rigidity more; Perhaps
Add rib.
But these methods have been introduced other problem.
For example, thicker wall has increased weight.
The material that employing has more rigidity has increased the cost of raw material, and may need more complicated casting process (for example, changing cast steel into from SG iron).
Use rib can cause localized stress to rise, thereby can cause fatigue failure.This is for the brittle material of for example foundry goods problem especially.Rib also constitutes more complicated casting.
The model utility content
Disclose a kind of dynamic transfer system of rotating speed of the rotor for increasing wind turbine, this dynamic transfer system comprises: main shaft, and it can drive around main axis by described rotor; Supporting structure, it comprises at least one bearing that the described main shaft of supporting rotates around described main axis; Gear-box, it has the gear box casing that is rigidly connected to described supporting structure and the planet carrier that is connected to described main shaft; And coupling member, it is connected to described main shaft with described planet carrier; Wherein, described main shaft is relevant with the tooth group that radially outward is given prominence to, described planet carrier is relevant with the tooth group of radially inwardly giving prominence to, described coupling member comprises the tooth group of radially inwardly giving prominence to of closing with the tooth winding relevant with described main shaft, and described coupling member also comprises the outstanding tooth group of radially outward of closing with the tooth winding relevant with described planet carrier.This dynamic transfer system comprises can be by main shaft, supporting structure and the gear-box of rotor driving.Supporting structure comprises that supporting spindle centers at least one bearing that main axis rotated and limited other motions of main shaft.Therefore, the rotation except around main axis does not have other degrees of freedom between main shaft and supporting structure.
Gear-box comprises the gear box casing that is rigidly connected to supporting structure and the planet carrier that is connected to main shaft.Gear box casing supporting planet carrier rotates around main axis, limits other motions of planet carrier simultaneously.On the other hand, planet carrier is connected to main shaft, has translation freedoms in all directions, and has rotational freedom around the axis perpendicular to main axis.This flexibility between main shaft and the planet carrier plays a significant role aspect the mass motion of dynamic transfer system.Advantageously, by with this flexibility with and miscellaneous part between interaction be that the kinematic relation of feature combines, dynamic transfer system realizes transmission of torque with reliable fashion.Other internal forces are assigned with, and make dynamic transfer system may cause the situation of parasitic load to have low receptance to alignment error, tolerance, load deformation, thermal expansion and other.
Flexibility between main shaft and the planet carrier can provide by flex link, and this flex link limits by the terminal part relevant with main shaft, terminal part and the linkage member relevant with input link.Linkage member is connected to each terminal part to limit two joints.Each joint allows between linkage member and the corresponding terminal part to relatively rotate and along the relative translation of main axis around the axis perpendicular to main axis.Because this twin adapter, flex link adapt between main shaft and the gear-box input link radially, axially and the angle misalignment.
When sitting in supporting structure on the tower top suspending when gear box casing is from be installed on wind turbine, other benefit can provide by the internal distribution of power.Supporting structure in this mode of execution can comprise the bearing housing around the bearing of supporting spindle.Gear box casing can then directly or indirectly suspend from bearing housing.Therefore, do not arrive the load paths of pylon through gear box casing.When further comprising generator with the gear-box one, power transmission keeps this benefit.Especially, generator comprises rotor and the stator that is positioned in the generator housing, and generator housing is rigidly connected to gear box casing and suspends from gear box casing.
The utlity model has the feature of the rigidity that is designed to increase frame.The utility model is arranged on material the outermost edge of free space.
The utility model also is provided for the member of planet carrier, and this member is suitable for extending axially from planet carrier and leaves, and wherein this member is truncated cone shape.This member has been strengthened the structure of planet carrier, so torque load can not cause planet carrier to transmit with reversing.
Preferably, described member is connected to the planet carrier shank comprises described member and shank with formation assembly.Planet cage plate can be connected to described assembly.The planet pin can be connected to assembly via planet cage plate.Torque load is delivered to the planet pin and does not cause planet cage plate to reverse.
Preferably, described member is connected to planet cage plate comprises described member and planet carrier with formation assembly.This assembly comprises described member, and planet cage plate can be connected to the planet carrier shank, thereby shank is resisted with respect to reversing of planet cage plate.Shank can comprise the steel column between two planet cage plates.
Preferably, described member is around the location, periphery of planet carrier.
Preferably, described member is radially inwardly located with respect to the periphery of planet carrier.
Preferably, gear-box comprises that having axis along the longitudinal is positioned at the nonrotational support unit that the bearing of single track is arranged.This bearing is arranged to be provided between planet carrier zone and the nonrotational support unit provides supporting, and gear-box does not have other bearings on planet carrier between described track and truncated cone shape member.
Preferably, single track is in the radial and axial extension part office in planet carrier zone.
Preferably, bearing is arranged the nonrotational motion that is arranged between the described member of at least part of restriction and the described nonrotational support unit.Preferably, nonrotational motion is one or more in relative radial motion, motion to axial and the relative tilt motion between input shaft and the non-rotatable member.
Preferably, bearing is arranged and is comprised the biconial roller bearing.
Description of drawings
Only by by way of example the utility model is described referring now to accompanying drawing, wherein:
Fig. 1 is a kind of perspective view of exemplary wind turbine;
Fig. 2 is the sectional view for the dynamic transfer system of the wind turbine of Fig. 1;
Fig. 3 is the sectional view of coupling that further in detail shows the dynamic transfer system of Fig. 2;
Fig. 4 and Fig. 5 are the sectional views of a kind of mode of execution of planet carrier of the present utility model, and Fig. 4 shows planet pin and planetary position; And
Fig. 6 is the schematic representation of a kind of mode of execution of planet carrier of the present utility model, and wherein the member that extends from the planet carrier shank towards input shaft is taper.
Embodiment
Fig. 1 shows a kind of wind turbine 2 of example.Although what show is the offshore wind turbine, should be noted that following description is applicable to the wind turbine of other types.Wind turbine 2 comprises the rotor blade 4 that is installed to hub 6, and hub is by cabin 8 supportings on the pylon 12.Wind causes that rotor blade 4 and hub 6 rotate (Fig. 2) around main axis 14.This rotational energy is passed to the dynamic transfer system (or " dynamical system ") 10 that is contained in the cabin 8.
As shown in Figure 2, dynamic transfer system 10 comprises the main shaft 16 that is connected to hub 6 (Fig. 1).Dynamic transfer system 10 also comprises clutch shaft bearing 18 and second bearing 20 of supporting spindle 16, the gear-box 25 that centers on the bearing housing 22 of clutch shaft bearing 18 and second bearing 20 and have the gear-box planet carrier 26 that is driven by main shaft 16.Gear-box 25 increases the rotational velocity of main shaft 16 to drive generator 28 (not shown)s.Supporting structure 60 block bearing housings 22, gear-box 25 suspend from bearing housing.
Fig. 2 also shows the three-dimensional system of coordinate based on main axis 14.In this system of coordinates, the y axle is considered to the main axis of system.X axle and z axle are perpendicular to the y axle, and the z axle is aimed at substantially with gravitational direction.Translation and sense of rotation limit with reference to this system of coordinates.
Clutch shaft bearing 18 and second bearing, 20 supporting spindles 16 rotate around y axle 14, but prevent other relative movement between bearing housing 22 and the main shaft 16.In structure shown in Figure 2, bearing housing 22 is forms of bearing support tube.
Gear-box 25 suspends from bearing housing 22 and main shaft 16, itself does not support for gear-box 25.More specifically, gear-box 25 comprises the planet carrier 26 that is connected to main shaft 16 and the gear box casing 24 that suspends from bearing housing 22.24 of gear box casings are at one end supported.
Fig. 3 shows coupling 50 in further detail.Coupling 50 is connecting flanges 69 of connecting flange 42, planet carrier 26 by main shaft 16 and circumferentially engages the crooked spline tooth coupling that connecting flange 42,68 linkage member 70 limit.Connecting flange 42,68 is shown as respectively and is integral with main shaft 16 and planet carrier 26, but in the connecting flange 42,68 one or two also can be bolt or otherwise be attached to main shaft 16 and the independent parts of planet carrier 26.
Connecting flange 42 ends at the outstanding tooth 74 of radially outward, and connecting flange 68 ends at the tooth of radially inwardly giving prominence to 76.Linkage member 70 at one end comprises the tooth of radially inwardly giving prominence to 78, comprises the tooth 79 that radially outward is outstanding in the opposite end, with difference soldered tooth 74,76.Therefore, two gear engagements are defined the gear ratio that had 1: 1.One group of tooth of each gear engagement has straight substantially profile, and another group is crown profile at axial direction shown in having.Therefore, the tooth 74, the 79th that radially outward is outstanding has the tooth of coronal contour.Radially the tooth of inwardly giving prominence to 76,78 has straight profile and extends to mesh with tooth 74,79 along its length.Because this layout, linkage member 70 is as the twin adapter that can adapt to dissimilar misalignment.More specifically, coupling 50 can be decomposed into 3 kinology main bodys: main shaft 16 (comprising connecting flange 42), linkage member 70 and planet carrier 26 (comprising connecting flange 68).Each connecting flange 42,68 and linkage member 70 between limit joint.In this specific implementations, joint is the gear engagement.Each joint is because crown tooth 74,76 allows relatively rotating around x axle and z axle.Also allow the relative translation of axial direction (namely along main axis 14), because straight-tooth 78 is not at this direction restriction crown tooth 74,46.Joint is not designed for other relative movement.This kinematic relation provides the translation freedoms of all directions for coupling 50 and centers on the rotational freedom of x axle and z axle.
Referring now to Fig. 4-6, a kind of mode of execution demonstration of the present utility model comprises truncated cone shape member 110 and 120 planet carriers that extend from planet carrier shank 108 towards input shaft.
Thisly with the favourable powerful ground of extension part on the structure of shank 108 that extends axially truncated cone shape member 110 forms left from described planet carrier shank 108 is linked together.This has strengthened the structure of planet carrier 100 and has reduced shank 110 reversing with respect to planet cage plate 102 on every side.
Planet pin 104 is connected to the leg structure 108/110 of extension via planet cage plate 102.Member 110 is the parts that constitute the structure of shank 108, this means on the function that shank 108 is not the parts that disperse, because they interconnect now securely.
Although to the maximum resistance of shear-loaded and bending (all at vertical plane and reverse) from 0 degree tapering, i.e. cylindrical body, the degree of depth of material in loaded planar determined the operation rigidity in this design.With reference to Fig. 6, it shows truncated cone shape member 110, and the end near output shaft 120 has less diameter, this means that dull and stereotyped 122 have than minor diameter, perhaps can not do requirement.Therefore, although cylindrical body itself can be rigidity more, it is better idea that truncated cone shape is arranged, because dull and stereotyped 122 be less, does not perhaps need dull and stereotyped 122.
Referring again to Fig. 2, planet carrier 26 has the part 27 of radially inwardly and axially extending to side with the wind from planetary pinion.The bearing that is used for the part 27 of planet carrier arranges that 40 are positioned at the side with the wind of the first rank planet carrier 26 as shown at single track place.The housing 24 non rotatable support units 39 of supporting and bearing arrange 40.This has reduced diameter, weight and cost that bearing is arranged.For example, diameter can be less than the external diameter of input shaft.The bearing that is positioned at the first rank planet carrier, 26 contrary wind sides is unwanted.For example, bearing arranges that 40 can be pair of bearings, for example the tapered roller bearing shown in.Therefore, the weight of gear-box 25 is located between two theoretical supporting points of 40 pairs of tapered roller bearings back-to-back of side with the wind of the first rank planet carrier 26.Compare with the traditional arrangement with face-to-face bearing that the weight of gear-box wherein is positioned on the elongation line of two theoretical supporting points, more stable for the supporting of gear-box.The contrary wind side bearing that lacks for the first rank planet carrier 26 is that linkage arrangement 50 has been created the space effectively.
Claims (13)
1. dynamic transfer system for increasing the rotating speed of the rotor of wind turbine comprises:
Main shaft, it can drive around main axis by described rotor;
Supporting structure, it comprises at least one bearing that the described main shaft of supporting rotates around described main axis;
Gear-box, it has the gear box casing that is rigidly connected to described supporting structure and the planet carrier that is connected to described main shaft; And
Coupling member, it is connected to described main shaft with described planet carrier;
Wherein, described main shaft is relevant with the tooth group that radially outward is given prominence to, described planet carrier is relevant with the tooth group of radially inwardly giving prominence to, described coupling member comprises the tooth group of radially inwardly giving prominence to of closing with the tooth winding relevant with described main shaft, and described coupling member also comprises the outstanding tooth group of radially outward of closing with the tooth winding relevant with described planet carrier.
2. dynamic transfer system according to claim 1, wherein, described gear box casing suspends from described supporting structure.
3. dynamic transfer system according to claim 1, wherein, described planet carrier is included on the upwind and extends axially the truncated cone shape member that leaves from described planet carrier, and wherein said truncated cone shape member is strengthened described planet carrier, and torque load does not cause planet carrier to transmit with reversing.
4. dynamic transfer system according to claim 3, wherein, the tooth group relevant with described planet carrier is positioned on the described truncated cone shape member.
5. dynamic transfer system according to claim 1, wherein, the outstanding tooth group of the radially outward on the described coupling member with respect on the described coupling member radially inwardly outstanding tooth group axially locating in the contrary wind side.
6. dynamic transfer system according to claim 1, wherein, the tooth group on the described main shaft is radially positioned at the tooth group inside on the described planet carrier.
7. dynamic transfer system according to claim 1, wherein, the tooth group relevant with described main shaft comprises the member that can form interference fit with described main shaft.
8. dynamic transfer system according to claim 1, wherein, the outstanding tooth group of radially outward has coronal contour in the axial direction, described radially inwardly outstanding tooth group have straight substantially profile.
9. according to claim 3 or 4 described dynamic transfer systems, wherein, described gear-box comprises nonrotational support unit, wherein said nonrotational support unit comprises that axis along the longitudinal is positioned at single track and is arranged to provides the bearing of supporting to arrange that described gear-box does not have other bearings between described track and described truncated cone shape member on planet carrier between planet carrier zone and nonrotational support unit.
10. dynamic transfer system according to claim 9, wherein, described single track is in the radial and axial extension part office in planet carrier zone.
11. dynamic transfer system according to claim 9, wherein, described bearing is arranged the nonrotational motion that is arranged between the described truncated cone shape member of at least part of restriction and the described nonrotational support unit.
12. dynamic transfer system according to claim 11, wherein, described nonrotational motion is one or more in relative radial motion, motion to axial and the relative tilt motion between input shaft and the described non-rotatable member.
13. dynamic transfer system according to claim 9, wherein, described bearing is arranged and is comprised the biconial roller bearing.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB1212578.7A GB2504072B (en) | 2012-07-16 | 2012-07-16 | Contra-rotating transmission |
| GB1212578.7 | 2012-09-28 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203114536U true CN203114536U (en) | 2013-08-07 |
Family
ID=46799646
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2012206799813U Expired - Fee Related CN203114536U (en) | 2012-07-16 | 2012-12-05 | Power transmission system for wind turbine |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN203114536U (en) |
| GB (1) | GB2504072B (en) |
| WO (1) | WO2014013237A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104769319A (en) * | 2012-09-28 | 2015-07-08 | 诺迈士科技有限公司 | Power gearing system for a wind turbine |
| CN114585810A (en) * | 2019-10-23 | 2022-06-03 | 维斯塔斯风力***有限公司 | Assembling or disassembling gear assemblies of wind turbines |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103850882B (en) * | 2014-03-25 | 2016-04-20 | 上海电机学院 | A kind of wind generating unit and electricity-generating method thereof |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE737886C (en) * | 1939-11-15 | 1943-07-28 | Wilhelm Stoeckicht Dipl Ing | Helical planetary gear |
| GB696653A (en) * | 1949-12-16 | 1953-09-02 | Lucien Romani | Improvements in or relating to torque governors for a windmill |
| DE2558093A1 (en) * | 1975-12-19 | 1977-06-23 | Mannesmann Ag | PLANETARY GEAR |
| GB2136084B (en) * | 1983-03-01 | 1986-03-12 | Northern Eng Ind | Toothed gearing |
| SU1401201A1 (en) * | 1986-03-17 | 1988-06-07 | В.И.Козаренко | Screw gearing |
| KR960007401B1 (en) * | 1994-06-27 | 1996-05-31 | 신찬 | Multi-unit rotor blade system integrated wind turbine |
| US8264096B2 (en) * | 2009-03-05 | 2012-09-11 | Tarfin Micu | Drive system for use with flowing fluids having gears to support counter-rotative turbines |
| KR101205329B1 (en) * | 2010-06-11 | 2012-11-28 | 신익 | Wind Power Generator Having Triple Rotors Integrated System |
-
2012
- 2012-07-16 GB GB1212578.7A patent/GB2504072B/en not_active Expired - Fee Related
- 2012-12-05 CN CN2012206799813U patent/CN203114536U/en not_active Expired - Fee Related
-
2013
- 2013-07-15 WO PCT/GB2013/051891 patent/WO2014013237A1/en active Application Filing
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104769319A (en) * | 2012-09-28 | 2015-07-08 | 诺迈士科技有限公司 | Power gearing system for a wind turbine |
| CN104769319B (en) * | 2012-09-28 | 2017-06-13 | 诺迈士科技有限公司 | For the power gear Transmission system of wind turbine |
| CN114585810A (en) * | 2019-10-23 | 2022-06-03 | 维斯塔斯风力***有限公司 | Assembling or disassembling gear assemblies of wind turbines |
| CN114585810B (en) * | 2019-10-23 | 2024-05-24 | 维斯塔斯风力***有限公司 | Assembling or disassembling a gear assembly of a wind turbine |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2014013237A1 (en) | 2014-01-23 |
| GB201212578D0 (en) | 2012-08-29 |
| GB2504072A (en) | 2014-01-22 |
| GB2504072B (en) | 2014-08-13 |
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| CF01 | Termination of patent right due to non-payment of annual fee |