WO2005012763A1 - Transmission destinee a une machine produisant de l'energie renouvelable - Google Patents

Transmission destinee a une machine produisant de l'energie renouvelable Download PDF

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Publication number
WO2005012763A1
WO2005012763A1 PCT/NZ2004/000175 NZ2004000175W WO2005012763A1 WO 2005012763 A1 WO2005012763 A1 WO 2005012763A1 NZ 2004000175 W NZ2004000175 W NZ 2004000175W WO 2005012763 A1 WO2005012763 A1 WO 2005012763A1
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WO
WIPO (PCT)
Prior art keywords
drive train
gear
shaft
sun gear
torque
Prior art date
Application number
PCT/NZ2004/000175
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English (en)
Inventor
Andrew Stephen Horsfall
Original Assignee
Andrew Stephen Horsfall
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Andrew Stephen Horsfall filed Critical Andrew Stephen Horsfall
Publication of WO2005012763A1 publication Critical patent/WO2005012763A1/fr

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Classifications

    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F16H3/724—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously using external powered electric machines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D15/00—Transmission of mechanical power
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D15/00—Transmission of mechanical power
    • F03D15/10—Transmission of mechanical power using gearing not limited to rotary motion, e.g. with oscillating or reciprocating members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F05B2210/00—Working fluid
    • F05B2210/16—Air or water being indistinctly used as working fluid, i.e. the machine can work equally with air or water without any modification
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • This invention relates to power generation from renewable resources such as wind energy, to devices that couple a generator to a windmill, and in particular this invention relates to coupling devices including an assembly of gears for adapting the generator to changing wind speeds.
  • Typical windmills are mounted on typically 60-80 m high towers, have two or three rotor blades (dia 30-50 m) that turn at a relatively slow rate between 20 and 50 revolutions per minute, a gearbox for raising the rate of angular motion of a shaft to drive an AC generator running at typically 1500 rpm coupled to an AC power grid operating at a constant frequency and typical windmills of this class are rated at from about 400 up to 1500 kilowatts. They are "computer-controlled”. Usually the blades are pitch controlled in order to match the variable speed of the wind to a fixed ratio of the constant speed of the rotor of the synchronous generator. The gearbox is required to reliably handle large torques and powers.
  • a fully variable, efficient gearbox has not been developed for use at this power level and there is still a need for better matching of the windmill rotation speed to wind speed in order that the maximum amount of energy can be extracted from the wind.
  • Some multi-speed gearboxes that allow more than one rotor speed are known, but those developed so far are expensive and complex.
  • a DC generator or variable-speed AC generator not restricted in rotation speed is known, but inversion into constant-frequency AC at the power levels involved is costly. Generators of the two-speed pole-changing type may be used, but they are also costly.
  • the invention to be described in this specification is generally suited to a wind turbine having a single speed gearbox coupled to a synchronous generator connected to a power utility grid.
  • the invention may have other applications.
  • a particular aspect of wind generation is coping with gusts, gales or hurricanes. Uncontrolled increases in wind speed beyond a design limit would result in stressing mechanical and electrical parts beyond their design limits, and would interfere with the stability of the AC grid fed from the generator. Therefore a torque limiting device is a preferred component of a windmill, at least as a short-term response to a gust of wind until either blade angle or entire windmill direction have been adjusted in order to cope with excessive wind speed. Unexpected gusts may be likely for windmills operated downwind from mountain ranges where rotors may cause gusts, or may occur during turbulent weather conditions such as cyclones, the passage of fronts, or in or near thunderstorms.
  • the present invention is relevant to high-power windmills that have an about constant-speed generator turning in synchrony with the frequency of an AC power utility grid that is being supplied. Windmills not having synchronous generators are electrically more complex and hence more expensive.
  • the means comprises the allowance of slip in a sun gear of a gear train in a secondary gear box in the event of a high torque.
  • the sun gear is coupled to a spur gear to which is coupled a hydraulic pump.
  • a pressure-responsive valve on the outlet of the pump is forced open by a torque apphed through the spur gear, the spur gear and hence the sun gear is stationary.
  • the hydraulic pump absorbs some of the excess torque by forcing compressed fluid through a restricted, closed circuit and through cooling means to return to the pump. Meanwhile the sun gear turns and the transfer ratio of the secondary gear box drops. At the same time, the blades tend to turn faster. Some of the excess torque is returned to the blades.
  • Makino et al (US 6720670 and US 6608397)) describe in very broad but not enabling terms a variable-ratio gear assembly (Figs lb to 3) for a wind machine in which there is a sensor responsive to output attached to the generator itself, and control means controlling the gear assembly to maintain the generator rotation speed relatively constant.
  • One detailed example employs toothed pinions and no control of gear ratio. Friction cones, which are not compatible with gear boxes for usefully high power levels, provide variable ratio.
  • this invention has the disadvantages (a) that the fate of any excess energy is unspecified, and (b) the generator must have experienced the excess load at least in part before it is sensed and action to compensate can begin.
  • OBJECT OBJECT
  • this invention provides a variable ratio drive train for a renewable- energy generating machine for coupling an electrical generator to a rotating source of power;
  • the drive train including a gearbox of the planetary type having a frame or housing and three gear sets: a sun gear, a plurality of planet gears, and an annular gear all held together in meshed alignment, and including an input drive shaft having when in use a first rate of rotation and an output drive shaft having when in use a second rate of rotation related to the first rate by a transfer ratio;
  • the input shaft being connected to a selected one of the gear sets;
  • the output shaft being connected to a selected either of the remaining gear sets, wherein the intermediate gear set, being that set not connected to either drive shaft, is at least partially externalised from the frame or housing and is brought into contact with externally controllable restraining means capable of affecting the rotation rate of the intermediate gear set with respect to the frame or housing so that the actual transfer ratio of the drive train may thereby be controlled during use.
  • the drive train or gear box is adapted for use within a sustainable energy plant such as a wind mill, wave, or tide plant, and is capable of transmitting the power typically collected by wind vanes or rotors to an electrical generator.
  • the drive train may operate in either of two modes of operation thereby serving as a dual ratio gearbox and the housing is capable of rotation with respect to an external support;
  • the gearbox includes as externally controllable restraining means a braking means mounted on the external support in functional apposition to an externalised surface attached to the intermediate gear set; wherein during a first mode of operation the braking means is inactive and the intermediate gear is allowed to rotate freely, thereby causing the input shaft to tend to spin faster than the output shaft so causing the one-way clutch to become engaged and thereby transmit power from the input shaft to the output shaft at a 1:1 transfer ratio without factional loss in the drive train; or wherein during a second mode of operation the brake is actuated thereby preventing movement of the intermediate gear set so that the planetary
  • the ratios provided are 1:1 and 1:1.5 (that is, a step-up from the input shaft to the output 100 shaft).
  • the sun gear serves as the intermediate gear set and bears an externalised concentric brake disk; the input shaft is coupled through an aperture in the sun gear directly to a mount for the planetary gears, and the output shaft is coupled to the annular gear, so that the drive train is adapted to serve as a dual transfer ratio 105 gearbox dependent on the status of the brake, and so that a power generating device may be more easily matched to a fluctuating supply of power.
  • the intermediate gear of the drive train is attached to an exteriorised concentric worm wheel; the framework of the drive train supporting a worm screw meshed with the worm wheel and mounted on a worm shaft rotatably mounted
  • the external support being provided with transducing means capable of sensing an axial load placed on the worm shaft by a torque from the concentric disk; the transducing means being connected to motor control means connected to a variable speed motor capable of causing the worm shaft to rotate hence causing the intermediate gear to rotate thereby causing a change of the ratio of the drive train, and so that
  • the drive train ratio in response to a sensed axial load the drive train ratio may be adjusted so that the axial load is held substantially constant thereby preventing the electrical generator attached to the output shaft of the drive train from experiencing an excessive torque.
  • Preferred transducing means include load cells, strain gauges (suitably mounted), and displacement transducers in combination with spring mounts.
  • the sensed axial load is used as an input to a negative feedback control loop in which the output comprises power to the variable speed motor drive and the sense of feedback is such that the control loop seeks to hold the axial load as sensed at no more than a predetermined threshold level.
  • the 125 variable speed motor drive is not energised, while if the sensed axial load is greater than the predetermined threshold level, the variable speed motor drive is energised in proportion.
  • the invention provides a windmill having an electrical generator and equipped with a drive train as described previously in this section, wherein the 130 drive train protects the generator from excess torque; the excess torque being returned to the blades as a result of an instantaneous change in the ratio of the drive train.
  • the invention provides a windmill having an electrical generator and equipped with a drive train as described previously in this section, wherein the drive train is capable of being quickly changed from a first ratio to a 135 second ratio so that the windmill can be operated in a manner matched to the available wind.
  • the intermediate gear of the drive train is a modified, slideable sun gear capable of being forced, in a first mode, to a first position towards one end of a shaft; in which position the sun gear is locked to an externally rotatable wheel thereby
  • the slideable sun gear is capable in a second mode of being forced into a second position away from one end of the shaft; in which second position teeth included about the periphery of the sun gear cause the sun gear to become locked to the planet gears and hence the drive train becomes locked in a transfer ratio of 1:1, so
  • the drive train can operate in more than one mode. More particularly, the slideable sun gear when in the first position towards one end of a shaft is locked to a separately rotatable worm wheel thereby forming a composite sun gear and drivable worm capable of being rotated by an external, torque-responsive motive source, conferring a torque limiting property on the drive train and when in the 150 second position the sun gear is locked by means of a second annular set of gear teeth included about the periphery of the sun gear about both sides of the planet gears hence locking the drive train in a transfer ratio of 1:1, so that the same drive train can operate as either a torque-limited gearbox having a selected transfer ratio or as a direct transfer gearbox.
  • the drive train or gear box may be provided as an accessory capable of being used within an existing windmill design.
  • the drive train or gear box may be provided as part of or in conjunction with an AC generator assembly suitable for use with a sustainable energy plant so that the generator simulates a two-speed generator even though, in use, the rotor of the generator itself turns at a
  • the dual-speed drive train or gear box may be constructed within or upon an existing gearbox suitable for use with a sustainable energy plant so that the existing gearbox assumes a dual-speed function hence rendering any associated generator more effective.
  • Fig 1 is a longitudinal sectional view of the gearbox portion of example 1, a torque-limiting 170 device.
  • Fig 2 is a diagram showing a front elevation view of example 1.
  • Fig 3 is a diagram showing a longitudinal section of example 2.
  • Fig 4 is a diagram showing a perspective view of example 2.
  • Fig 5 is a diagram showing a perspective view of example 3 in a first mode.
  • Fig 6 is a diagram showing example 3 in a second mode.
  • Fig 7 shows the transfer functions of a prior art gearbox and several Examples.
  • the Examples relate to a planetary gear type coupling for use in power-generating windmills at power levels of typically up to 0.5 to 1.5 MW. Wind power as available is to be collected
  • Fig 7 shows example transfer functions.
  • the Y axis 701 shows generator power output and a design maximum level at the dotted line 703.
  • Axis 702 shows several wind power inputs.
  • Curve 704/705 is a prior-art curve in which the windmill control system reacts slowly to overload by yawing the windmill or changing the pitch
  • Example 1 Torque limiter as in Fig 7, lines 709-710. Operation is along line 709, but if a sudden gust of wind takes the input power over a threshold the torque limiter has immediate
  • Example 2 Speed changer as in Fig 7, two slopes of lines 706, 707, 708/A. The windmill is operative over a wider range of wind speeds. If the sun gear is held stationary the transfer 195 function follows the slope of line 707/708 ; otherwise the function is on the slope of 706 corresponding to a 1:1 transfer ratio coupling.
  • Example 3 Ratios as for example 2; alternative slopes of lines 706 or the mode suited to a higher wind speed 707, and entering the solid horizontal portion 708A if the torque limiter comes into effect.
  • the device In the low speed mode the device is a 1:1 coupler with low losses and 200 in the example described the torque limiter is not active in that mode.
  • EXAMPLE 1 This type of torque-limiting gearbox is adapted for use in conjunction with a windmill for generating electric power for distribution by an AC power utility grid.
  • the gearbox is a stand-alone regulating device by which we mean that excess torque or power is
  • the gearbox includes a sun, planets and annulus (orbital) type of gearing but the sun is modified so that it may be forcibly rotated, hence making the gearbox variable.
  • a longitudinal section 100 shows the layout of a preferred embodiment. This gearbox is rated for about 0.5 to 1.5 MW operation with adequate safety margins. Dimensions of a realistic working prototype provide that the disk 103
  • the input shaft 102 is rigidly connected with a planet carrier comprising disk 106 carrying a number (preferably 3, 4 or 5) of planet pinion
  • gears 105 These pinions may be mounted on Hicks-style cantilevered axles 112 for improved load sharing, as is known in the art.
  • the input shaft is supported by bearings 111 within the output shaft. More bearings Ilia are provided between the input shaft 102 and the sun gear 113, according to standard practice.
  • the pinions 105 are always engaged with both the annulus gear 108 and the sun gear 113.
  • the sun gear 225 is also rigidly connected with a externalised radial disk 103, provided at its periphery with a worm thread (see Figs 5 or 6) engaged with a worm screw 201 (see Fig 2) mounted from a supporting frame. Oil seals 109 and 110 are shown, but other covers, lubrication means, etc (according to standard practice) are not shown in this illustrative example.
  • Fig 2 shows some special aspects of this invention not included in Fig 1 from one end.
  • Fig 2 is a face view of the input shaft 102 surrounded by the disk 103 carrying a peripheral worm thread 104. Rotation (if any) of the disk will be in a clockwise direction.
  • a worm screw 201 rigidly supported on shaft 201A is constantly engaged with the thread 104. The worm screw on its shaft is firmly held by means of thrust
  • Sensing means capable of locally detecting the torque apphed by the edge of disk 103 against the worm screw is provided.
  • One version of sensing means comprises allowing and sensing a small amount of movement in an axial direction in relation to a housing
  • Bearing 213 is supported by a pre-loaded (biased) compression spring 209 in compression (optionally to a controllable amount by adjustment of confinement) against a frame or housing 210. If a large torque is apphed to the input shaft 102, the worm tends to be moved (to the right) against the compression spring 209, the strength and loading of which is set so that applied torques of less than the
  • a worm gear is preferred because of its non-reversibility by which we mean that it is difficult to force a worm screw to turn in a step-up mode by turning the worm itself.
  • Other forms of gear can be used.
  • Locking may also be caused to occur within the motor 206 itself, such as by application of a steady magnetic field in an AC motor.
  • a load cell is used to support the thrust bearing 213 and is placed between bearing 213 and frame or housing 210.
  • Typical load cells 255 employ strain gauges to measure bending of internal beams and exhibit a quite small displacement when maximally loaded.
  • the load cell output signal is passed to a control box implementing a proportional/integral servo drive that causes the motor 206 (supported on frame 207) to turn proportionally to torque, once the torque signal exceeds a predetermined threshold.
  • the motor causes the worm to be driven so that the disk 103 is made to rotate in the direction that will cause the effective torque as sensed to be reduced.
  • the geared coupling 204 and 205 permits a positive rotational drive to be maintained to the worm even if worm screw displacement occurs. Rotation of the worm causes the sun gear 113 to rotate, causing the effective ratio of the planetary gear box to change so
  • Torque limiting can be combined with a pre-existing variable speed mode of operation.
  • the worm can rotate at a set rate and then speed up if excess torque is detected.
  • Increased angular momentum in the turbine blades a result of the extra energy collected from the gust may be recovered by returning the ratio of the gearbox towards
  • transducer 208 controller 200
  • worm drive motor 206, coupling 204/205
  • spring 209 comprises a feedback controlled regulator of torque applied to the worm screw by the shaft, always endeavouring to maintain the torque at no more than a certain value and so that axial
  • the output shaft 101 is driven from the input shaft 102 through the orbital gears.
  • the sun gear is stationary, being locked in place by friction at the sliding interface between the stationary worm 201 and the worm thread 103.
  • the example prototype gearbox has a 1:1 ratio.
  • This mode corresponds to line 709 in Fig 7.
  • the sun gear 103 is caused to rum as a result of the worm screw 201 being driven by the motor 206 in response to an excessive apphed torque, so altering the transfer ratio of the gear box and having the effect of holding 310 excess kinetic energy from a gust of wind as a blade speed increase rather than causing overload damage to any part of the windmill.
  • the resulting increase in efficiency depends on the variability of the wind itself.
  • This mode corresponds to line 710 in Fig 7.
  • this invention may have its own control 315 means although a power source for the motor is required.
  • Windmills with synchronous generators are constant-speed machines and the computer in control may not have means to measure the blade rotation rate.
  • Existing windmill control systems usually include means to either change the pitch of the propellor blades or yaw the windmill when the excess 320 speed has risen to an undesirable amount, having regard to blade strength for example, and these may be retained.
  • EXAMPLE 2 This invention relates to a type of dual-speed gearbox intended to extend the operating range of a windmill used for generating power of the order of 0.5 MW for connection to a power
  • This Example is intended to be placed between the step-up gearbox and the generator itself, where it extends the capability of the windmill to operate effectively in a range of wind speeds.
  • One ratio is 1:1.
  • the other ratio is typically a step-up of 1:1.5.
  • the gearbox includes a sun planets and annulus (orbital) type of gearing.
  • a longitudinal section 300 shows a preferred embodiment. The entire assembly may rotate during use,
  • Rotational energy from the existing windmill gearbox (not shown) drives the input shaft 302 and is coupled from the gearbox to the generator by output shaft 301.
  • At the termination of the input shaft there is a rigid connection 311 with the planet gear carrier 313.
  • the invention includes a one-way
  • the planet carrier has a number (preferably 3, 4 or 5) of pinion gears assembled on to it, such as pinion 314 (a void is shown on the lower side where a planet gear may be placed). Pinions 314 may
  • pinions 314 are always engaged with an inner sun gear 308 which is rigidly connected with a radial brake disk 304 and being directly connected to neither the input nor the output shaft is called an intermediate gear.
  • the sun gear may rotate
  • a brake mechanism 315 for either holding or releasing the disk 303 follows conventional disk brake design as is well known in the art.
  • Bearings 310 and 307, and an oil seal 306 are provided in order to allow relative rotation.
  • These pinions 314 are also always engaged with an outer annular ring gear 309, which is rigidly connected to the output shaft 301.
  • another oil seal 305 closes
  • the output shaft is driven directly at a 1:1 ratio through the oneway clutch 312 by the input shaft 302.
  • the brake 304/315 is off, so that the effect of rotation of the planet carrier is to cause the sun gear and the attached disk 303 to spin freely.
  • the gearbox 355 acts as a 1:1 coupling with no losses.
  • the sun gear 308 is locked by means of the brake 315 clamping upon the braking surface 304 of disk 303.
  • the planet carrier causes the annular ring 309 to rotate in the same direction as the input shaft but at a faster rate (1.5 times the input shaft rate, in this Example), so that the one-way clutch 312 placed between the input and
  • 360 output shafts is allowed to freewheel or overrun and is decoupled.
  • the speed change is effected by locking or unlocking the brake on disk 303. This action can be carried out by an actuator (not shown) working the brake mechanism in response to a command from a controlling digital processor (not shown).
  • One design has the gear box stepping up the rotation of the output shaft by preferably 1.5 times for use when winds are light.
  • the generator speed is allowed to stabilise before the generator is reconnected to the grid.
  • the invention allows rotor rotation speeds during power generation of either 36 rpm or 48 rpm.
  • a suitable one-way clutch should be optimised for long life at the typical power levels used. Because the speed changes are effected while the blades are not turning, the one-way clutch does not need to absorb a great deal of impact energy at the time of becoming engaged. In the absence of torque limiting means, the power transfer relationship (Fig 7) lies along line 706, or line 707 including the dashed portion.
  • EXAMPLE 3 This may be regarded as a variant of Example 1.
  • the planetary gearbox of this invention may also be used so as provide a useful constant or alterable change of rotational speed, if that was required for any other reason. It has the advantage that the torque limiting feature may stay in effect even if the primary mode of operation is as a
  • the hardware is modified by including means to determine the rate of rotation of the motor driving the worm screw and to report that rate to the windmill operating computer.
  • a suitable rotation transducer (not shown, but well known to workers in the relevant art) is mounted on the motor shaft (or internal 400 motor properties may be used, or the disk 103 may include a device for monitoring its rate of rotation.
  • the controller 211 may have a capability to inherently determine the motor speed to a sufficient accuracy. It might be a form of synchronous or stepping motor.
  • the motor 206 In use, if the operating computer determines that a different rate of blade rotation to 405 that provided when the sun gear is stationary is desired, the motor 206 is driven through controller 211 at a speed that has the effect of causing the disk attached to the sun gear to rotate at a desired rate, to give this gearbox the desired ratio. Again, the power requirements of motor 216 are low in comparison with the power being transmitted through the drive train (including 102 to 101).
  • any indication of displacement of shaft 201 A through transducer 208 is permitted to add to the motor rotation speed, so that even if the invention is running in this third mode it retains the torque limiting function described above.
  • EXAMPLE 4 This is a combination of Example 1 and Example 2.
  • Fig 5 shows this Example in a first mode; 415 the sun gear coupling 507 is engaged with the worm gear 502.
  • the input shaft 503 at left is rigidly coupled to the annulus gear 505 which is always meshed with the planet spur gears 506, 506' and these gears are also always meshed with the sun gear 507 which is the intermediate gear.
  • the planet gears are on a carrier which is part of the output shaft 504.
  • the rotational velocity of the sun gear may be altered (in this mode) by rotation of the externally 420 fixed worm screw 501 working against the worm gear 502.
  • the sun gear 507 must have been moved axially along the output shaft 504 so that dog teeth 509 on the side face of the sun gear have meshed with complementary dog teeth 508 on the side face of the worm gear.
  • the device acts as a 1:X transfer ratio with active torque control (as previously described for Example 1). The value of X depends on gear diameters and typically
  • the annulus turns the planet gears which use the sun gear as a reference, which might be moved by action of the worm 501.
  • the second mode shown in Fig 6, is activated by sliding the sun gear away from the worm gear by means of an actuator arm (not shown) ending with a roller miing in a circumferential groove 512. (This groove and actuator were not shown in Fig 5, and other means known in the
  • gears of a planetary group other than the sun gear serve as the exter- 440 nalised controllable member of the planetary gearbox.
  • a controllable disk is connected to the annulus gear with the drive applied to the sun gear, and the output taken from the planetary gears. (These versions are not illustrated).
  • the worm gear of Figs 1, 2, 5 and 6 may be exposed to too much torque. Solutions to that problem include forced lubrication of the bronze screw, making the diameter of the steel worm 445 as large as is feasible, and inserting further planetary gears that increase the relative rotation rate of the worm perhaps by a 4:1 ratio.
  • Variations of gear tooth configuration may reduce noise and wear, as is known in the art. If the gear box of Example 2 was used in a mode wherein the brake was used to cause a 450 change in rotation rate for a change of ratio during power transmission, the brake acting on the disk 103 would need to be substantial and dissipate a significant amount of heat, and wear would occur. This mode is possible though presently believed to be "not preferable”. There is another propellor brake in most windmills. This type of operation may suit some types of windmill control and management.
  • this gearbox can be sold as a retro-fit option or as an accessory, while it may be incorporated within or upon the housing of a generator and sold as part of the generator itself, thereby creating a cheaper and simpler kind of two-speed generator than an electrically implemented version or alternatively sold as a torque-protected generator.
  • this gearbox is incorporated within and sold as part of an existing "main" 460 gearbox, which thereby becomes a more versatile kind of gearbox than was previously available..
  • this invention does not dump some excess energy within a heat sink; it returns all of the excess energy to the blades as rotational momentum and may recover the blade energy after a gust or allow it to be dissipated as drag on the blades.
  • the invention uses existing, slower-to-act alterations to operating mode (such as 475 blade feathering (change of pitch) or windmill yawing) to bring the blade rotation speed down again, if the excess wind turns out to be steady.
  • the operating cost to efficiency of the torque limiting invention is small; the motor if in use may use 0.02% of the power developed under load.
  • the insertion cost is also small; at sub- torque limiting speeds the related losses are only those of a standard orbital gear transmission.
  • the invention is inherently quick to respond to an excess torque; responses within 1 second are feasible.
  • the invention is a stand-alone, self-regulating device, needing perhaps 1 KW of electric power for the torque limiter function (when active).
  • Self-regulation is a useful fail-safe property.
  • the technology is like that already used in windmill power trains (gearboxes, electromechanical 485 actuators, and active control. Mechanics and engineers do not need training in new fields. The capital cost is small and lower than alternatives.
  • the invention may be scaled up or down for use in applications other than propellor-driven wind generation.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
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  • Wind Motors (AREA)

Abstract

La technologie d'un engrenage planétaire protège les générateurs synchrones des moulinets utilisant un limiteur de couple dans lequel un engrenage (103) est servo-pivoté par un pignon à vis sans fin (201) même si un couple de rafales de vent excessif est détecté au niveau de la vis (201). Le coefficient de transfert est immédiatement modifié et la puissance excédante est réaffectée à des pales de moulinets rotatives. De la même manière, une boîte d'engrenage à deux vitesses est construite par freinage réversible de la roue solaire (303 figure 3), si elle n'est pas freinée, un embrayage à roue libre (312) verrouille les arbres de sortie (320) et d'entrée (302) entre eux et si elle est freinée, l'ensemble d'embrayage planétaire (314, 308, 309) applique une vitesse rotationnelle augmentée sur l'embrayage (312) lequel surproduit. Ces deux fonctions peuvent être combinées.
PCT/NZ2004/000175 2003-08-05 2004-08-05 Transmission destinee a une machine produisant de l'energie renouvelable WO2005012763A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
NZ527410 2003-08-05
NZ52741003 2003-08-05
NZ52775003 2003-08-22
NZ527750 2003-08-22

Publications (1)

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WO2005012763A1 true WO2005012763A1 (fr) 2005-02-10

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Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1775465A2 (fr) 2005-10-13 2007-04-18 General Electric Company Dispositif pour l'entraînement d'une première partie d'une éolienne par rapport à une deuxième partie de l'éolienne
ITBO20090436A1 (it) * 2009-07-07 2011-01-08 Bonfiglioli Riduttori Spa Riduttore vite senza fine-gruppo corona combinato con un riduttore epicicloidale multistadio per la generazione di energia eolica
EP2366988A1 (fr) * 2010-03-19 2011-09-21 Winergy AG Procédé et dispositif de détection de couple dans un engrenage au moyen d'un capteur de vibrations
ES2370713A1 (es) * 2008-04-10 2011-12-22 M. Torres Olvega Industrial, S.L. Transmisión de accionamiento entre el eje motriz y el generador eléctrico de un aerogenerador.
WO2012023994A1 (fr) * 2010-08-18 2012-02-23 Ebo Group, Inc. Système d'embrayage à limitation de couple pour éolienne
EP2500143A1 (fr) * 2009-11-10 2012-09-19 Makita Corporation Outil électrique
ES2403557A1 (es) * 2011-11-10 2013-05-20 Rafael LASTRA GÓMEZ Amortiguador-limitador de par para aerogeneradores.
US20140090945A1 (en) * 2012-10-03 2014-04-03 Jtekt Corporation Power generation device
US8845471B2 (en) 2013-01-23 2014-09-30 General Electric Company Variable input synchronous output drivetrain for wind turbine
WO2015019998A1 (fr) * 2013-08-05 2015-02-12 株式会社ジェイテクト Dispositif de générateur d'énergie éolienne et dispositif de transmission de rotation utilisé dans celui-ci
US9035476B2 (en) 2011-09-12 2015-05-19 Jtekt Corporation Power generating device
US9054560B2 (en) 2012-04-19 2015-06-09 Jtekt Corporation Power generating apparatus
CN105221691A (zh) * 2015-09-24 2016-01-06 安徽钟南人防工程防护设备有限公司 一种用于风机传动的涡轮传动装置
CN105443748A (zh) * 2015-12-28 2016-03-30 南京高速齿轮制造有限公司 偏航、变桨齿轮箱的输入端

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Publication number Priority date Publication date Assignee Title
US3529493A (en) * 1968-10-29 1970-09-22 Peter Egli Power transmission
US5015898A (en) * 1987-09-09 1991-05-14 Heinz Frey Continuously variable drive
US4995861A (en) * 1988-12-23 1991-02-26 Mannesman Aktiengesellschaft Mechanical shiftable three speed planetary transmission
US4973295A (en) * 1989-03-31 1990-11-27 Gabrielle Reng-Yi Wu Lee Stepless variable ratio transmission
FR2672361A1 (fr) * 1991-01-31 1992-08-07 Brondet Henry Reducteur-variateur de vitesse.
EP0635639A1 (fr) * 1993-07-21 1995-01-25 Ashot Ashkelon Industries Ltd. Transmission pour éoliènne
EP0822355A2 (fr) * 1996-07-29 1998-02-04 de Jong, Maud Transmission à variation de vitesse continue
JPH10246173A (ja) * 1997-03-03 1998-09-14 Mitsubishi Heavy Ind Ltd 遊星増速機
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Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1775465B1 (fr) * 2005-10-13 2015-09-30 General Electric Company Dispositif pour l'entraînement d'une première partie d'une éolienne par rapport à une deuxième partie de l'éolienne
EP1775465A2 (fr) 2005-10-13 2007-04-18 General Electric Company Dispositif pour l'entraînement d'une première partie d'une éolienne par rapport à une deuxième partie de l'éolienne
ES2370713A1 (es) * 2008-04-10 2011-12-22 M. Torres Olvega Industrial, S.L. Transmisión de accionamiento entre el eje motriz y el generador eléctrico de un aerogenerador.
ITBO20090436A1 (it) * 2009-07-07 2011-01-08 Bonfiglioli Riduttori Spa Riduttore vite senza fine-gruppo corona combinato con un riduttore epicicloidale multistadio per la generazione di energia eolica
EP2500143A1 (fr) * 2009-11-10 2012-09-19 Makita Corporation Outil électrique
EP2500143A4 (fr) * 2009-11-10 2013-10-23 Makita Corp Outil électrique
EP2366988A1 (fr) * 2010-03-19 2011-09-21 Winergy AG Procédé et dispositif de détection de couple dans un engrenage au moyen d'un capteur de vibrations
US8621940B2 (en) 2010-03-19 2014-01-07 Siemens Aktiengesellschaft Method for detecting torque in a transmission, measuring device and control program
WO2012023994A1 (fr) * 2010-08-18 2012-02-23 Ebo Group, Inc. Système d'embrayage à limitation de couple pour éolienne
US8932017B2 (en) 2010-08-18 2015-01-13 Ebo Group, Inc. Wind turbine torque limiting clutch system
US9322395B2 (en) 2011-09-12 2016-04-26 Jtekt Corporation Power generating device
US9035476B2 (en) 2011-09-12 2015-05-19 Jtekt Corporation Power generating device
ES2403557A1 (es) * 2011-11-10 2013-05-20 Rafael LASTRA GÓMEZ Amortiguador-limitador de par para aerogeneradores.
US9054560B2 (en) 2012-04-19 2015-06-09 Jtekt Corporation Power generating apparatus
US9097295B2 (en) * 2012-10-03 2015-08-04 Jtekt Corporation Power generation device
US20140090945A1 (en) * 2012-10-03 2014-04-03 Jtekt Corporation Power generation device
US8845471B2 (en) 2013-01-23 2014-09-30 General Electric Company Variable input synchronous output drivetrain for wind turbine
WO2015019998A1 (fr) * 2013-08-05 2015-02-12 株式会社ジェイテクト Dispositif de générateur d'énergie éolienne et dispositif de transmission de rotation utilisé dans celui-ci
CN105221691A (zh) * 2015-09-24 2016-01-06 安徽钟南人防工程防护设备有限公司 一种用于风机传动的涡轮传动装置
CN105443748A (zh) * 2015-12-28 2016-03-30 南京高速齿轮制造有限公司 偏航、变桨齿轮箱的输入端
CN105443748B (zh) * 2015-12-28 2017-08-25 南京高速齿轮制造有限公司 偏航、变桨齿轮箱的输入端

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