Abstract:
A wind turbine power generating system, including a wind turbine connected to a speed-increasing gearbox having an output shaft. An electrical generator having an input shaft is also provided. A coupling interconnects the input and output shafts. The coupling includes a high torsional wind-up and/or displacement ability in parallel with a high frictional slip ability, such that during normal operation there is little or no frictional slippage and during a transient torque reversal the loads in the turbine drive system are decreased, thus decreasing the impact loads on the gearbox bearings.

Description:
CROSS-REFERENCE TO RELATED APPLICATION 
       [0001]    This application claims the benefit of pending U.S. provisional application Ser. No. 61/882,856, filed Sep. 26, 2013, by the same title, which is fully incorporated herein by reference. 
     
    
     TECHNICAL FIELD 
       [0002]    The invention herein relates to couplings interposed between wind turbines and electrical generators. Particularly, the invention relates to such a coupling configured to dissipate the adverse effects of torque reversals on gearbox bearings in a wind turbine generator system. 
       BACKGROUND ART 
       [0003]    Well over 100,000 megawatt and multi-megawatt wind turbines have been installed over the past decade, almost all using a similar drive system incorporating a gearbox as a speed increaser, positioned between the turbine blades and the generator. The gearboxes are designed for 20-year life, but typically need repair or replacement in 5 to 10 years or less. Axial cracking of gearbox bearings is becoming a major cost factor in the return on investment of wind farms. Impact loading during transient torque reversals has been recognized as a root cause of this damage. Recently research has shown that an unusual mode of bearing damage called White Etch Area (WEA) damage is causing the axial cracking of the bearings. WEA damage is actually a microscopic material alteration that creates super-hard inclusions like slivers just below the bearing raceway where cracks can initiate and grow. Severe and rapid microscopic plastic deformation is suspected as the cause of WEA damage. 
         [0004]    During a torque reversal, the load zone of the gearbox bearings suddenly shifts 180 degrees. The bearing rollers radially impact onto the raceway along with a simultaneous high axial load reversal from the helical gears. Both the magnitude and the rate of the impact loads and axial surface traction loads determine the potential for WEA plastic deformation in the bearing inner race. The higher the torsional natural frequency of the drive train&#39;s spring mass system, the greater the torque rate of change, and thus the higher the strain rate as the rollers impact the bearing inner race . As wind turbines have increased in size, the high strain rate during rapid bearing load zone reversals, along with high impact stress, appears to be exceeding a threshold where WEA damage is initiated in the bearing inner raceway. Once initiated the normal roller loading can cause axial cracking and bearing failures in as little as a year or two. 
         [0005]    In a wind turbine generator system, high inertia characterizes the entire system, from the turbine blades, main shaft, gearbox high-speed coupling and into the generator itself. Indeed, the highest inertia is typically at the opposite ends of the system—at the blades and the generator. On torque reversal, the high inertia of the system can significantly impact all of the system components, and particularly the gearbox. The asymmetric torque-limiting clutch system described in U.S. Patent Application Publication US 2012/045335 A1 describes a solution to this problem. An alternate solution contemplates increasing the torsional wind-up of the system (including certain of, blades, a main shaft, a gearbox, a high-speed shaft/coupling and a generator) which would lower the natural frequency. If this were done alone, it could cause other problems in the turbine drive system; such as resonant frequency issues in other parts of the turbine. For instance, it is known that the coupling spacer between the gearbox and the generator can have a problematic axial natural frequency that can cause spacer element resonance and destruction. Any changes to the system natural frequency during normal operation may necessitate a recertification of the turbine. 
         [0006]    Increasing the torsional wind-up must be done in a way that does not affect normal operation of the turbine. This could be accomplished with a high frictional slip ability in parallel with a high torsional wind-up and/or displacement ability. For example, if the frictional torque setting was at 40% of the rated turbine torque, there would be no slippage during normal operation between 20% and 100% of the rated turbine torque as apparent from  FIG. 1 . The only time the friction slippage would occur is when the drive system sees a total torque variation exceeding 80% of the rated turbine torque, for example for brief periods during startups and shutdowns. Significant slippage would only occur during rare system transient torque reversals exceeding the frictional slip setting. It is contemplated that the frictional torque setting should be such as to accommodate some small slippage during normal startup and shutdown operation to keep the friction surfaces clean and free of corrosion. 
         [0007]    If the high torsional wind-up is effected by a torsional spring, as contemplated in an embodiment of the invention, the torsional spring rate may be asymmetric so that the spring rate in reverse could be lower or near zero for a portion of the displacement. Any reverse torque events would slip at frictional resistance only of say 40% of normal turbine torque. The reverse angle of travel would need to be sufficient to absorb reverse transient wind-up energy of the drive system. This may require a torsional movement of 10 to 50 degrees or greater for typical turbines with generators operating at 1000 rpm or more. For turbines with lower generator operating speeds, the required torsional displacement would be lower, in the range of 1 to 5 degrees per 100 rpm. 
         [0008]    The typical coupling systems of existing wind turbines are designed with significant parallel, angular and axial shaft misalignment capability between the gearbox and the generator in order to accommodate the flexing of the lightweight base plate structure. These coupling systems typically have zero backlash and are torsionally very rigid with very little wind-up ability. The torsional characteristics are critically important to preventing resonant vibration problems in the drive system and turbine components. Some coupling systems are equipped with frictional torque limiters set at 150 to 200% of the rated turbine torque. They are intended to protect the coupling from the very high torque overloads such as generator short circuits. These torque limiters have proved to be ineffective in protecting the drive system and especially the gearbox from transient torque reversals whose impact loads on the gearbox bearings can dramatically shorten life. 
         [0009]    Coupling systems that utilize torsional wind-up in parallel with low frictional damping, such as Spaetgens Patent No. 2,909,911 and Lech Patent No. 4,5548,311, have been around for a long time. They are generally used on internal combustion engines. Their torsional wind-up ability is used to tune the natural frequencies of the system to be outside the operating range of the equipment. Their frictional damping component that is in parallel with the torsional wind-up is typically very small and is used to control clutch plate and gear rattle noise and damage during idling and shifting. These types of couplings generally are integrated with the engine clutch whose frictional slip setting is very high and is in series with the torsional wind-up ability, not in parallel. Lech is a good example. The frictional component that is in parallel has a very low frictional slip setting. 
         [0010]    A key to the present invention&#39;s success is a coupling system with a high torsional wind-up and/or displacement ability, along with a high frictional slip ability to dampen the system significantly only during a transient torque reversal event (see  FIG. 1 ). A typical turbine with a high speed generator operating at 1000 to 1800 rpm would require at least 10 degrees of reverse slippage with a torque setting of at least 10% of turbine rated torque. Ideally, the reverse slippage would exceed 20 degrees at 40% reverse torque. Nowhere in the prior art is there a drive system with such a combination of torsional displacement and/or wind-up with torsional frictional damping capable of taming high torque reversals. This is certainly not true for the uniquely challenging reversals of wind turbines. 
       SUMMARY OF THE INVENTION 
       [0011]    In light of the foregoing, it is a first aspect of the invention to provide an improved wind turbine coupling with an asymmetric torsional behavior in wind turbine drive systems to protect gearbox bearings from damage due to torsional reversals. 
         [0012]    Still a further aspect of the invention is the provision of a wind turbine coupling system having very little wind-up or torsional displacement during normal operation in the forward direction and yet having significant torsional wind-up and/or displacement in the reverse direction. 
         [0013]    Yet another aspect of the invention is the provision of a wind turbine coupling system that is readily adaptable to existing wind turbine couplings for enhanced operation and durability. 
         [0014]    Another aspect of the invention is the provision in a wind turbine coupling system of a frictional slip capability in parallel with torsional wind-up and/or displacement. 
         [0015]    Another aspect of the invention is the provision of a wind turbine coupling system having a frictional slip capability high enough that there is little or no slippage during normal operation. 
         [0016]    Yet a further aspect of this invention is the provision of a wind turbine coupling system with a small amount of frictional slippage during startup to full rated torque and shutdown. 
         [0017]    Another aspect of the invention is the provision of a wind turbine coupling having enough frictional slippage during a torque reversal to absorb the damaging energy of an impact load that might otherwise initiate axial cracking in gearbox bearings. 
         [0018]    Yet another aspect of the invention is the provision of a wind turbine coupling that automatically resets itself to the forward operational position upon restart of the turbine to full torque. 
         [0019]    Still a further aspect of the invention is the provision of a wind turbine coupling of a symmetrical design that is able to operate in an asymmetrical manner described above so that the device can be used for both clockwise and counter-clockwise forward direction of the wind turbine generator. 
         [0020]    The foregoing and other aspects of various embodiments of the invention, taken separately or in combination, are achieved by the improvement in a wind turbine power generating system comprising a wind turbine connected to a speed-increasing gearbox having a high-speed output shaft and an electrical generator having an input shaft, the improvement comprising: a coupling system interconnecting said output and input shafts, said coupling system having a portion of its torque path split between at least one of a torsional wind-up and displacement component along with a torsional dampening component. The torsional dampening component may be a frictional slip component set in the forward direction to at least 10% of the rated turbine torque. Similarly, the frictional slip setting in the reverse driving direction may be equal to at least 10% of the rated turbine torque. The torsional rotational displacement movement in a reverse direction may be taken from the group of at least 10 degrees or greater for turbines with generators operating at 1000 rpm or more, and for turbines with lower generated speeds in the range of 1 to 5 degrees per 100 rpm. A zero backlash connection may be provided between a pressure plate and endplate in the coupling system. 
         [0021]    In a preferred embodiment of the invention for generator speeds exceeding 1000 rpm, the parallel wind-up and frictional slip are located on the generator shaft and an adapter plate is provided to fit the existing flexible coupling of the turbine for ease and safety of retrofitting. According to the invention, a portion of the rotational movement is frictional slip without torsional wind-up in forward or reverse and wherein the frictional slip-only portion is at least 10 degrees. It is contemplated that a hard stop is provided after a threshold of torque in a forward direction is exceeded, and that threshold is contemplated at above 120% of rated turbine torque. 
         [0022]    The torsional movement of the coupling system has an asymmetric action during operation such that the only time a deadband is engaged is during a torque reversal exceeding a frictional slip threshold. It is particularly preferred that the asymmetric action occurs automatically and a frictional slip setting is greater than 20% of the rated turbine torque, but less than 100% thereof. The design of the frictional slip and wind-up elements are preferably symmetric to allow for use on wind turbines that have gearbox designs that may drive the generator in either clockwise or counterclockwise direction in normal forward rotation. 
         [0023]    In operation, the coupling system is symmetrical in design and yet asymmetric in its response to torque reversals with a prolonged slip ability in either direction of shaft rotation, and the slip torque setting is high enough to only occur during transient torsional events that would typically include torque reversals and transient torque events. The torsional movement during normal startups and shutdowns is normally less than 10 degrees for generator speeds exceeding 1000 rpm, while the torsional movement during transient torque reversals exceeds 10 degrees. While a torsional spring is preferred for the wind-up action, it is also contemplated that the torsional spring may be replaced with an elastomeric material in shear, an elastomeric material in compression, metal springs in compression, metal springs in bending, and gas springs. In any event, it is desired that the same torsional wind-up components provide wind-up in both forward and reverse directions. 
         [0024]    The invention also contemplates a method of providing torsional damping in a wind turbine drive system to reduce the magnitude and rapidity of torque reversals, and mitigate the resulting damaging impact loads on drive system components, comprising: detecting a drive system torque reversal exceeding a first preset threshold; dissipating torsional wind-up energy in the drive system while maintaining said reverse torque at said first preset threshold; detecting a positive torque exceeding a second preset threshold; and returning the turbine drive system to forward operation. The drive system operates in a forward direction producing electric power without affecting the system&#39;s basic forward torsional characteristics, while providing torsional damping in a reverse direction, and the referenced first threshold is set at less than 100% of the turbine torque at a power rating of the generator. Again, the torque reversal detection and dissipation of torsional wind-up is achieved automatically with frictional slipping, which effectively reduces the magnitude of reverse torque and slows the rate of the torque reversal magnitude increase. 
         [0025]    In certain embodiments of the invention, the first and second preset thresholds are the same and the frictional slipping action is provided in parallel with torsional springs that deflect during normal forward operation such that the torque load and the turbine generator drive system is shared by both frictional slippage and spring deflection. The frictional slippage provides a hysteresis damping to a winding up and unwinding of the drive system components, the torsional springs preferably having a zero torque load deadband for at least a portion of a torsional displacement movement during a torque reversal and wherein additional reverse torsional deflection spring action occurs at an end of the deadband movement. There is provided an additional reverse torsional spring action that is symmetric to the forward torsional spring action, thus achieving bidirectional operation of the unit. 
         [0026]    The invention also contemplates a method of retrofitting a wind turbine generator with torsional damping to reduce the magnitude and rapidity of torque reversals, comprising: removing the coupling hub on the generator shaft; installing a new coupling hub allowing the wind turbine generator drive system to operate in the forward direction producing electric power without affecting the system&#39;s basic forward torsional characteristics while providing torsional damping in the reverse direction by detecting a drive system torque reversal exceeding a preset threshold, dissipating torsional wind-up energy in the system while maintaining said reverse torque at said preset threshold, detecting a positive torque, and returning the turbine drive system to the forward operation; and selecting and installing an adapter plate to mate an existing coupling spacer. 
     
    
     
       DESCRIPTION OF DRAWINGS 
         [0027]    For a complete understanding of the various aspects, structures and operation of the invention, reference should be made to the following detailed description and accompanying drawings wherein: 
           [0028]      FIG. 1  is a functional schematic of a wind turbine coupling system between the gearbox and the generator particularly adapted as a retrofit for existing coupling systems; 
           [0029]      FIG. 2  is a graph of drive coupling torque as a percent of rated torque vs. angle of displacement for the present invention compared to the torsional rigidity of the typical existing coupling hub it replaces, indicated by the vertical dot-dash line, during normal operation; 
           [0030]      FIG. 3  is the same torque vs. angle of displacement graph as in  FIG. 2 , but shows the torque and displacement during a torque reversal and restart of the turbine, the torsional rigidity and zero backlash of existing coupling systems being shown with the dot-dash line; 
           [0031]      FIG. 4  is the same torque vs. angle of displacement graph as in  FIGS. 2 and 3 , but if the turbine were turning in the opposite direction of forward rotation, e.g. counter-clockwise vs. clockwise, demonstrating a symmetric design with asymmetric behavior; 
           [0032]      FIG. 5  is a cross-sectional view of the coupling adapted for implementation of the system; 
           [0033]      FIG. 6  is a cross sectional view of the coupling showing one of the compression springs that provides the torsional deflection; 
           [0034]      FIG. 7  is a sectional view of a coupling of the invention showing the compression springs for the torsional deflection, along with the slots for the torque bolts in the friction plate, and the Bellville springs for controlling the force on the friction elements; 
           [0035]      FIG. 8  is a view of the input hub showing the holes for the torque bolts and the slots to allow rotational travel of torsional wind-up compression springs without compression, along with the ends of the spring slots that provide for compression of the torsional wind-up springs at each end of travel; 
           [0036]      FIG. 9  is a view of the end plate showing the torque bolt holes, along with slots for movement and compression of the torsional wind-up springs and recesses for a Bellville spring; 
           [0037]      FIG. 10  shows the friction plate with bonded friction material and openings for the compression-type spring that is used for the torsional wind-up, along with slots to allow the torque bolts to displace rotationally relative to the friction plate; and 
           [0038]      FIG. 11  is the pressure plate that fits into the endplate with zero backlash drive to transfer the torque between the two. 
       
    
    
     DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS 
       [0039]    Referring now to the drawings, and more particularly  FIG. 1 , it can be seen that a wind turbine coupling system between the gearbox output shaft and generator input shaft made in accordance with the prior art is designated generally by the numeral  10 . The system includes a gearbox  12  coupled to the generator  19  by a spacer coupling  14 . The instant invention  16  replaces the existing coupling hub on the generator shaft and adapts to the spacer of the existing coupling system. The drawing illustratively shows a frictional slip capability  17  in parallel with a torsional deflection and/or displacement capability  18 . 
         [0040]    With reference to  FIG. 2 , an appreciation can be obtained as to the torsional behavior of an existing wind turbine coupling hub compared to the torsional behavior of a preferred embodiment of the invention. The existing coupling hubs are characterized by torsional rigidity and zero backlash with virtually no useful torsional wind-up or angular displacement as shown with the near-vertical dot-dash line. In contradistinction, the preferred embodiment has a useful level of torsional wind-up (torque increasing with angular displacement) and/or some significant torsional displacement. In parallel with the torsional wind-up and/or displacement is a frictional slip capability preferably set to allow some slight torsional displacement during startup and shutdown. A slip setting of 40% of rated turbine torque is shown to allow this slight frictional slippage during startup and shutdown and thus keeping the frictional interface in optimum condition.  FIG. 2  also shows a potential for large angular displacement, but it does not become active until a torque reversal, as shown in  FIG. 3 . Those skilled in the art can appreciate that a frictional slip setting that was much greater than 50% of rated turbine torque could prevent slippage in the forward direction. It could still function in the torsional reversal mode, which is a rare event in typical modern turbines and thus the friction interface would have to be well protected from corrosion and other frictional interface changes that could cause stick/slip behavior or an undesirable increase in its static torque slip release setting. 
         [0041]      FIG. 3  shows the behavior of the preferred embodiment during a torque reversal exceeding the frictional torque setting threshold. It shows the effect of providing a large amount of angular displacement or backlash in conjunction with the torsional wind-up ability that is acting in parallel with the frictional slip ability. Torque reversals are known to cause load zone reversals on the gearbox bearings that result in the rollers impacting on the bearing raceways. This can lead to cracking and failing of the bearing races. By designing in a significant angular displacement, the frictional slippage can absorb most or all of the impact energy that could cause bearing damage. Most torque reversals occur during severe stopping events.  FIG. 3  shows that upon restarting the turbine, a preferred embodiment automatically slips back into normal operation when the forward torque in the system exceeds the frictional slip threshold. The preferred embodiment also has a torsional wind-up ability at the end of the reverse angular displacement. This provides cushioning in case the amount of angular displacement designed is not enough to fully absorb the torque reversal energy. Some hard stops may also be designed in to limit the torsional wind-up and protect the torsional wind-up springs from damage. 
         [0042]      FIG. 4  shows another reason to provide the torsional wind-up ability in Reverse—the symmetry of the design.  FIG. 4  is again the same  FIGS. 2 and 3 , but shows another advantage of designing the torsional wind-up ability into the reverse direction—the design becoming symmetrical so that the unit can operate the same whether the normal direction of rotation of the generator shaft is clockwise or counterclockwise. This eliminates the need to manufacture and stock two different units for the same size wind turbine that has different directions of rotation at the generator. 
         [0043]    Referring now to  FIG. 5 , an appreciation of the invention can be obtained from a sectional view that shows the details of the preferred embodiment. Adapter  20  connects the coupling spacer  14  to the input hub  22 . Torque bolts  24  clamp the endplate  26  to the input hub  22  with spacing controlled by the bolt spacers  25 . The endplate  26  retains the Belleville springs  32  that provide the necessary force on the pressure plate  28  against the friction material  30  to control the slip torque setting. The friction material is affixed to the friction plate  34 , which is fixed to the output hub  40  with bolts  38 . Bearing  36  maintains concentricity of the input to the output. A “shrink disc” shaft locking device  42  clamps the output to the generator shaft. 
         [0044]      FIG. 6  is a sectional view similar to  FIG. 5  that shows one of a plurality of compression springs  50  that provides a means for torsional wind-up.  FIG. 7  is a sectional end view showing one of the compression springs  50  compressed in the normal operating position with the torque bolts  24  near the end of travel in the slots  52  in frictional plate  34 . The slot ends provide a hard stop against the torque bolts to protect the compression springs from being overstressed. A plurality of Belleville springs  32  is also shown. These provide the necessary axial force for the characteristic slip torque on the friction surfaces  30 . 
         [0045]      FIG. 8  shows the details of the input hub  22  with holes  58  to accommodate the torque bolts  24 . Slots  54  provide clearance for the compression springs  50  to allow rotational movement between the input and the output when the frictional torque threshold set by the Belleville springs  32  is exceeded. Slot ends  56  contact the compression springs  50  at the extremes of the angular displacement to provide the desired torsional wind-up capabilities at each end of the torsional displacement. 
         [0046]      FIG. 9  is a view of the endplate  26  showing slots  60  matching the slots  54  for the rotational movement relative to the compression springs. Similar slot ends are also shown. Recesses  62  for the Belleville springs are also shown. 
         [0047]      FIG. 10  is a view of the friction plate  34  showing slots  66  for relative movement of the torque bolts and openings  68  for containing the compression springs  50 . 
         [0048]      FIG. 11  is a view of the pressure plate  28  with tabs  70  shown as a means of carrying the torque to the endplate. 
         [0049]    It is contemplated that various embodiments will typically have a combination of torsional wind-up and torsional displacement that will exceed  10  degrees and preferably be on the order of 20 to 60 degrees or greater for typical turbines with generators operating at 1000 rpm or more. For turbines with lower generator speeds, the required torsional displacement would be lower, in the range of 1 to 5 degrees per 100 rpm. 
         [0050]    It is also contemplated that various embodiments will typically have a frictional torque setting exceeding 10% of the turbine torque so that normal turbine torque fluctuations do not cause unnecessary slippage and wear. The frictional torque setting would preferably be in the range of 20 to 50%, but could also be in excess of 50%. The most preferred setting would be 30 to 45% so as to provide a slight amount of slippage during normal startup and shutdown. That keeps the friction interface at its optimum performance during the rare torque reversal events that can damage the bearings. 
         [0051]    Thus, it can be seen that the various aspects of the invention have been achieved by the structure presented and described above. While in accordance with the patent statutes, only the best known and preferred embodiment of the invention has been presented and described in detail, the invention is not limited thereto or thereby. 
         [0052]    Accordingly, for an appreciation of the true scope and breadth of the invention, reference should be made to the following claims.