WO2020135908A1 - Agencement d'éolienne et procédé associé - Google Patents

Agencement d'éolienne et procédé associé Download PDF

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Publication number
WO2020135908A1
WO2020135908A1 PCT/DK2019/050409 DK2019050409W WO2020135908A1 WO 2020135908 A1 WO2020135908 A1 WO 2020135908A1 DK 2019050409 W DK2019050409 W DK 2019050409W WO 2020135908 A1 WO2020135908 A1 WO 2020135908A1
Authority
WO
WIPO (PCT)
Prior art keywords
low
drive
speed shaft
wind turbine
rotor
Prior art date
Application number
PCT/DK2019/050409
Other languages
English (en)
Inventor
Joris KOFMAN
Dan Mølgaard MATHIASEN
Original Assignee
Vestas Wind Systems A/S
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 Vestas Wind Systems A/S filed Critical Vestas Wind Systems A/S
Publication of WO2020135908A1 publication Critical patent/WO2020135908A1/fr

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Classifications

    • 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
    • F03D13/00—Assembly, mounting or commissioning of wind motors; Arrangements specially adapted for transporting wind motor components
    • F03D13/10—Assembly of wind motors; Arrangements for erecting wind motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • F03D80/50—Maintenance or repair
    • 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
    • F05B2260/30—Retaining components in desired mutual position
    • F05B2260/31—Locking rotor in position
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • the present invention relates to a wind turbine arrangement and, in particular, to an arrangement for rotating a rotor of a wind turbine, for example during installation and/or decommissioning or maintenance of the wind turbine. Aspects of the invention relate to a wind turbine arrangement and to a method of rotating a rotor of the wind turbine arrangement.
  • Wind turbines for power generation are well known in the art.
  • a nacelle is mounted on a tower, with a rotor being mounted on the nacelle, and a plurality of blades being mounted on the rotor.
  • the rotor is mounted on a rotor shaft or ‘low-speed’ shaft which is supported in the nacelle by a shaft housing.
  • a gearbox is located in the nacelle, with the low-speed shaft being mounted to the gearbox to connect the gearbox to the rotor.
  • a generator is also located in the nacelle, and a‘high-speed’ shaft is mounted to the gearbox and connects the gearbox with the generator.
  • the rotor and blades are typically mounted to the nacelle after the tower has been positioned on-site and the nacelle has been mounted atop the tower.
  • the rotor includes a rotor hub which is mounted to the already-installed nacelle, and then each blade is installed successively to the rotor hub.
  • each blade is installed successively to the rotor hub.
  • the rotor hub must therefore be rotated through a predefined angle so that the second blade may be mounted to the rotor hub from the same direction. For example, for a wind turbine having three blades equally spaced in the angular direction the rotor hub must be rotated through an angle of 120° between mounting each successive blade.
  • rotation of the rotor hub during installation is initiated by a drive device or turner device which applies a drive torque to the high-speed shaft.
  • the resulting rotation of the high-speed shaft is transferred through the gearbox to cause rotation of the low- speed shaft and therefore of the rotor and rotor hub.
  • rotating the rotor in this manner is relatively simple as the rotor is balanced.
  • the rotor is unbalanced and the level of torque needed to rotate the rotor is relatively large and, in particular, significantly larger than during normal operation of the wind turbine when all of the blades are mounted to the rotor hub.
  • the torque required to rotate an unbalanced rotor may be higher than a maximum torque capacity of the gearbox. This can result in costly delays during installation of a wind turbine until there is a reduction in wind speed.
  • gearbox may be significantly‘over-dimensioned’ in relation to its dimensional requirements during normal operating conditions (for a balanced rotor), i.e. the gearbox is over-dimensioned for the vast majority of the wind turbine lifespan.
  • over-dimensioning increases the cost of the gearbox, which is already a particularly expensive component to manufacture and maintain.
  • a wind turbine arrangement comprising a rotor, a gearbox, a high-speed shaft connected to the gearbox, and a low-speed shaft coupling the rotor to the gearbox.
  • the wind turbine arrangement may include a first drive means configured to apply a first drive torque to the high-speed shaft so as to apply drive torque to the low-speed shaft through the gearbox.
  • the wind turbine arrangement may include a second drive means arranged between the rotor and the gearbox, and configured to apply a second drive torque to the low-speed shaft to cause rotation of the rotor.
  • the present invention is advantageous in that the applied drive torque or load to rotate the rotor is split into two contributions, i.e. two drive sources or paths.
  • a first contribution i.e. the first drive torque
  • a second contribution is provided by a second drive means or second turner tool towards the front of the drivetrain, specifically upstream of the gearbox. That is, the gearbox is not located in the drive torque path between the second drive means and the rotor.
  • the amount of drive torque applied to rotate the rotor is not limited to the torque capacity of the gearbox. This is particularly useful during installation or maintenance of the wind turbine when one or more wind turbine blades may be being attached to, or detached from, a rotor hub of the wind turbine rotor. When only some of the blades have been attached to the rotor hub, the rotor is ‘unbalanced’ and the amount of torque needed to rotate the rotor is significantly greater than during normal operation of the wind turbine. The amount of torque needed to rotate the rotor may be further increased in conditions of relatively high wind.
  • the present invention obviates the need for the gearbox to be‘over-dimensioned’ to be able to withstand an applied drive torque from a turner tool on the high-speed shaft to rotate an unbalanced rotor during a wind spike. This significantly reduces the cost of the gearbox as it does not have to withstand drive torques to rotate the rotor in these potentially one-off conditions in the life of the wind turbine.
  • the gearbox does not need to withstand the drive torque needed in such conditions because part of the drive torque, i.e. the second drive torque, being provided to the rotor is applied to the low-speed shaft by the second drive means, and so the second drive torque is not transferred through the gearbox.
  • the present invention allows single wind turbine blade installation or removal during conditions of wind speeds that are higher than is possible with prior art arrangements.
  • the present invention also allows installation of longer blades in a wider range of weather conditions than is possible with prior art arrangements.
  • the second drive torque may be greater than the first drive torque.
  • a sum of the first drive torque and the second drive torque may be greater than a maximum drive torque capacity of the gearbox.
  • the first drive torque may be less than or equal to the maximum drive torque capacity of the gearbox.
  • the maximum drive torque capacity of the gearbox may be less than a maximum operational drive torque of the wind turbine.
  • the second drive means may comprise a low-speed shaft control element associated with the low-speed shaft.
  • the second drive torque may be applied to the low-speed shaft control element to cause rotation of the low-speed shaft control element and the low- speed shaft.
  • the wind turbine arrangement may comprise locking means and the low-speed shaft control element may comprise a plurality of engagement formations.
  • the locking means may be movable between a locked position in which the locking means cooperates with the engagement formations to restrain movement of the low-speed shaft relative to a housing and/or a main frame of the wind turbine and an unlocked position in which the low-speed shaft control element is rotatable relative to the locking means.
  • the control element may be in the form of a rotor locking disc with the second drive means being attached to the locking disc.
  • the second drive means may be used to rotate the rotor into a position where the locking means may be moved to the locked position in case of failure of one or more drivetrain components such as the gearbox.
  • the second drive means may comprise a plurality of linear drives each movable between extended and retracted positions to cause rotation of the low-speed shaft control element.
  • the plurality of linear drives may each include a hydraulic cylinder. Hydraulic pressure may be applied to the hydraulic cylinders to cause the plurality of linear drives to move between the extended and retracted positions.
  • a method of rotating a rotor of a wind turbine arrangement comprising the rotor, a gearbox, a high-speed shaft connected to the gearbox, and a low-speed shaft coupling the rotor to the gearbox.
  • the method may comprise applying a first drive torque via first drive means to the high-speed shaft to apply a drive torque to the low-speed shaft through the gearbox.
  • the method may comprise applying a second drive torque via second drive means to the low-speed shaft to cause rotation of the rotor.
  • the first and second drive torques may be applied substantially simultaneously.
  • the method may include controlling the amount of applied first and second drive torques to rotate the low-speed shaft to a predetermined angular position.
  • the wind turbine arrangement may comprise locking means for restraining rotation of the low-speed shaft relative to a housing and/or a main frame of the wind turbine arrangement.
  • the method may comprise actuating the locking means to an unlocked position in which the low-speed shaft is rotatable relative to a housing and/or a main frame prior to applying the first and second drive torques.
  • the method may include receiving sensor output data indicative of a position of the locking means, and may include confirming that the locking means is in the unlocked position in dependence on the received sensor output data prior to applying the first and second torques.
  • the method may be performed as part of a process to install one or more wind turbine blades to a rotor hub of the rotor of the wind turbine arrangement.
  • the method may also be performed as part of a maintenance process to remove one or more of the wind turbine blades from the rotor hub.
  • Figure 1 is a diagram illustrating a front view of a wind turbine arrangement according to an aspect of the invention
  • Figure 2 is a schematic plan view of a drivetrain of the wind turbine arrangement of Figure 1 , the drivetrain including a high-speed shaft drive and a low-speed shaft drive for rotating a rotor of the wind turbine arrangement;
  • Figures 3a-d show various views of the low-speed drive of Figure 2;
  • Figure 4 shows a perspective view of part of a component part of the low-speed drive of Figure 2;
  • Figure 5 shows the steps of a method of rotating the rotor of the wind turbine arrangement of Figure 1 ;
  • Figures 6a-g show various configurations of the low-speed shaft drive of Figure 2.
  • FIG. 1 shows a wind turbine arrangement 10, or simply a wind turbine, according to an embodiment of the invention.
  • the arrangement 10 includes a tower 12, a nacelle 14 rotatably coupled to the top of the tower 12 by a yaw system, a rotor including a rotor hub 16 mounted to the nacelle 14 and a plurality of wind turbine rotor blades 18 coupled to the rotor hub 16.
  • the nacelle 14 and rotor blades 18 are turned and directed into the wind direction by the yaw system.
  • the nacelle 14 houses generating components (not shown) of the wind turbine, including the generator, gearbox, drivetrain and brake assembly, as well as convertor equipment for converting the kinetic energy of the wind into electrical energy for provision to the grid.
  • the wind turbine is shown in its fully- installed form suitable for operation; in particular, the rotor 16 is mounted on the nacelle 14 and each of the blades 18 are mounted on the rotor and rotor hub 16.
  • FIG. 2 shows a schematic plan view of a drivetrain 20 located in the nacelle 14 of the wind turbine 10.
  • the rotor 16 is coupled to a generator 22 for harnessing the captured wind energy.
  • the rotor 16 is coupled to the generator 22 via a gearbox 24 and two rotatable shafts 26, 28.
  • the rotor 16 is connected to the gearbox 24 via a so-called‘low-speed’ shaft 26 (also referred to as a rotor shaft, driveshaft or main shaft), and the gearbox is then connected to the generator 22 via a so-called‘high speed’ shaft 28.
  • the rotor 16 is connected to the low-speed shaft 26 such that rotation of the low-speed shaft 26 causes rotation of the rotor 16.
  • the wind turbine includes two drive or turner devices 30, 32.
  • a first (or high-speed) drive device 30 is positioned between the generator 22 and the gearbox 24, in particular along or adjacent to the high-speed shaft 28.
  • the high-speed drive device 30 is arranged to apply drive torque to the high-speed shaft 30 so as to cause rotation of the high-speed shaft 30. This causes rotation of the low-speed shaft 26 through the gearbox 24, and therefore rotation of the rotor 16.
  • the high-speed drive device 30 may be any suitable drive device.
  • the high-speed drive device 30 is a rotary drive device including a plurality of hydraulic motors.
  • a second (or low-speed) drive device 32 is positioned between the rotor 16 and the gearbox 24, in particular along or adjacent to the low-speed shaft 26.
  • the low-speed drive device 32 is arranged to apply drive torque to the low-speed shaft 26 so as to cause rotation of the low-speed shaft 26 and therefore the rotor 16.
  • Figures 3a-d show various views of the low-speed drive device 32 of the described embodiment.
  • Figures 3a-d show the low-speed shaft 26 and a housing or casing 34 of a bearing of the low-speed shaft 26 with the low-speed drive device 32 adjacent the low-speed shaft housing 34 and engaging with the low-speed shaft 26.
  • a rotatable locking disc 36 completely surrounds the low-speed shaft 26 and is adjacent to the low-speed shaft 26.
  • the locking disc 36 is generally of annular shape and receives the low-speed shaft 26 therethrough in a relatively tight fit so that rotation of the locking disc 36 causes rotation of the low-speed shaft. That is, the locking disc 36 has an aperture 37 that receives the low-speed shaft 26.
  • the locking disc or plate 36 is located adjacent to the rotor and rotor hub 16.
  • the low-speed shaft 26 and the locking disc 36 are rotatable relative to the shaft housing 34, but such rotation of the low-speed shaft 26 and the locking disc 36 may be restrained or restricted, i.e. the low-speed shaft 26 and the locking disc 36 may be locked relative to the housing 34.
  • rotation of the locking disc 36 relative to the housing 34 may be restricted by locking means including locking pins 40 attached to, or part of, the housing 34.
  • locking pins 40 attached to, or part of, the housing 34.
  • the outer edge or periphery 38 of the locking disc 36 has a number of equally-spaced holes or recesses 42 or, more generally, engagement formations 42.
  • the locking pins 40 are adjacent to the periphery of the locking disc 36 and may engage with the engagement formations 42 to lock the locking disc 36 relative to the shaft or bearing housing 34.
  • the locking pins 40 are movable between unlocked and locked positions. In the unlocked position, the locking pins 40 are retracted away from the locking disc 36. As such, the locking pins 40 do not engage or cooperate with the engagement formations 42 of the locking disc 36 and therefore do not restrict rotation of the locking disc 36 relative to the housing 34. In the locked position, each of the locking pins 40 is lined up with, and received in, a corresponding engagement formation 42 of the locking disc 36. The locking pins 40 are fixed relative to the shaft housing 34 when in the locked position, and the locking pins 42 engage or cooperate with the engagement formations 42 of the locking disc 36 to restrict or prevent rotation of the locking disc 36 (and therefore the low- speed shaft 26).
  • the locking disc 36 is also referred to as a control element as it controls relative rotation between the low-speed shaft 26 and the housing 34.
  • each drive element 38, 39 is generally arc-shaped having two arc-shaped side walls 44a, 44b and connected at one end by an end wall 44c.
  • the side walls 44a, 44b and end wall 44c define a gap 45 for receiving part of the edge of the locking disc 36.
  • the drive elements 38, 39 also each include two circular flange portions 46a, 46b extending from one of the side walls 44a and two holes or apertures 48a, 48b through the side walls 44a, 44b and the circular flange portions 46a, 46b.
  • the drive elements 38, 39 also each include corresponding pins 50a, 50b that may be extended into, or retracted from, the holes 48a, 48b.
  • the drive element holes 48a, 48b are of similar dimensions to the engagement formations 42 of the locking disc 36, and the drive elements 38, 39 receive the edge of the locking disc 36 therebetween.
  • the drive element pins 50a, 50b are movable between engaged and disengaged positions. In particular, in the disengaged position the drive element pins 50a, 50b are retracted from the drive element holes 48a, 48b and also the engagement formations 42 of the locking disc 36. That is, in the disengaged position the drive element pins 50a, 50b do not cooperate with, and are distant from, the engagement formations 42 such that relative movement of the drive elements 38, 39 and the locking disc 36 is permitted.
  • the drive elements 38, 39 are arranged relative to the locking disc 36 such that the engagement formations 42 are adjacent to the drive element holes 48a, 48b, and the drive element pins 50a, 50b are inserted into, or received through, the engagement formations 42 of the locking disc 36. That is, in the engaged position the drive element pins 50a, 50b cooperate with the engagement formations 42 such that relative movement of the drive elements 38, 39 and the locking disc 36 is not permitted. Specifically, in the engaged position movement of the drive elements 38, 39 causes rotation of the locking disc 36.
  • the drive element pins 50a, 50b may be more generally referred to as engaging means, and the engaging means is movable between the engaged and disengaged positions using hydraulic power as will be described further below.
  • the low-speed drive device 32 also includes four linear drives 52a, 52b, 52c, 52d, in particular hydraulic linear drives each including a hydraulic cylinder 54a, 54b, 54c, 54d and piston 56a, 56b, 56c, 56d.
  • the hydraulic pressure in the hydraulic cylinders 54a, 54b, 54c, 54d may be adjusted so as to cause linear movement of the pistons 56a, 56b, 56c, 56d relative to the cylinders 54a, 54b, 54c, 54d.
  • each cylinder has a rod end and a cap end.
  • the pistons 56a, 56b, 56c, 56d are extended by applying pressure and flow in the cap-end chamber and by connecting the rod-end chamber to a hydraulic pressure tank.
  • the pistons 56a, 56b, 56c, 56d are retracted by applying pressure and flow in the rod-end chamber and by connecting the cap-end chamber to a hydraulic pressure tank.
  • the four linear drives 52a, 52b, 52c, 52d are identical.
  • Two of the linear drives 52a, 52b are associated with one of the drive elements 38, and the other two of the linear drives 52c, 52d are associated with the other drive element 39. Focussing firstly on the first drive element 38 and the first pair of linear drives 52a, 52b, a first one of the linear drives 52a is rotatably fixed or attached at one end to the shaft housing 34 or main frame of the wind turbine 10, and rotatably fixed or attached at the other end to one of the circular flange portions 46a of the drive element 38.
  • a second of the linear drives 52b is rotatably fixed or attached at one end to the shaft housing 34 or main frame of the wind turbine 10, and rotatably fixed or attached at the other end to the other of the circular flange portions 46b of the drive element 38.
  • the hydraulic cylinder 54a of the first linear drive 52a is attached to the housing 34 at an opposite side of the locking disc 36 from which the hydraulic cylinder 54b of the second linear drive 52a is attached to the housing 34.
  • the piston 56a of the first linear drive 52a is attached to the first circular flange portion 46a and the distal end of the piston 46a is shaped to engage with and receive the first circular flange portion 46a.
  • the piston 56b of the second linear drive 52b is shaped in a corresponding manner to engage with the other circular flange portion 46b.
  • the other drive element 39 and the other pair of linear drives 52c, 52d are arranged in a similar manner to the first drive element 38 and the first pair of linear drives 52a, 52b.
  • one of the other pair of linear drives referred to as the third linear drive 52c
  • the remaining linear drive referred to as the fourth linear drive 52d
  • the first and fourth linear drives 52a, 52d are rotatable relative to the housing 34 along a common, first rotation axis 58
  • the second and third linear drives 52b, 52c are rotatable relative to the housing 34 along a common, second rotation axis 60.
  • the first and second axes 58, 60 are located on opposite sides of the locking disc 36.
  • the fourth linear drive 52d when the third linear drive 52c is in the extended position, the fourth linear drive 52d is in the retracted position.
  • the first and third linear drives 52a, 52c are generally on opposite sides of the locking disc 36: when the first linear drive 52a is in the extended position, the third linear drive 52c is also in the extended position; and, when the first linear drive 52a is in the retracted position, the third linear drive 52c is also in the retracted position.
  • the second and fourth linear drives 52b, 52d are generally on opposite sides of the locking disc 36: when the second linear drive 52b is in the extended position, the fourth linear drive 52d is also in the extended position; and, when the second linear drive 52b is in the retracted position, the fourth linear drive 52d is also in the retracted position.
  • FIG. 5 shows the steps of a method 70 of mounting the blades 18 to the rotor hub 16 of the wind turbine 10 using the high-speed drive 30 and the low-speed drive 32.
  • the blades 18 are to be mounted to the rotor hub 16 once the wind turbine tower 12, nacelle 14, and rotor and rotor hub 16 have already been installed.
  • each of the three blades 18 are to be mounted one at a time and from generally the same direction to aid ease of installation.
  • the rotor 16 must therefore be rotated through generally 120° between mounting each of the blades 18 to the hub.
  • the rotor is rotated so that the rotor hub 16 is at the appropriate angular position to receive the first of the blades 18.
  • Both the high-speed drive 30 and the low-speed drive 32 are used to rotate the rotor 16.
  • the high-speed drive 30 is arranged to apply drive torque to the high-speed shaft 28 and, substantially simultaneously, the low- speed drive 32 is arranged to apply drive torque to the low-speed shaft 26.
  • FIG. 6a shows an initial state of the low-speed drive 32 in which the locking pins 40 are in the locked position and the drive element pins 50a, 50b of both drive elements 38, 39 are in the disengaged position. It is also seen that the four linear drives 52a, 52b, 52c, 52d are in an initial or reset position whereby the first and third linear drives 52a, 52c are in the extended position, and the second and fourth linear drives 52b, 52d are in the retracted position.
  • step 72 the drive element pins 50a, 50b are actuated using hydraulic power to move from the disengaged position to the engaged position, i.e. the pins 50a, 50b are now inserted into, and cooperate with the engagement formations 42 of the locking disc 36.
  • This configuration of the low-speed drive 32 is illustrated in Figure 6b.
  • the locking pins 40 are actuated to move from the locked position to the unlocked position, i.e. the locking pins 40 no longer cooperate with the engagement formations 42 of the locking disc 36.
  • the wind turbine 10 includes sensors, for example inductive proximity sensors, to ensure that the locking pins 40 have been fully retracted from the engagement formations 42 before proceeding to the next step. This configuration of the low-speed drive 32 is illustrated in Figure 6c.
  • the high-speed drive 30 is controlled to apply drive torque to the high-speed shaft 28 and, substantially simultaneously, the low-speed drive 32 is controlled to apply drive torque to the low-speed shaft 26.
  • pressure in the hydraulic cylinders 54a, 54b, 54c, 54d must be applied.
  • the pistons 56a, 56c apply a linear‘pulling’ force to the drive elements 38, 39, respectively, and the pistons 56b, 56d apply a linear‘pushing’ force to the drive elements 38, 39, respectively. That is, the first and third linear drives 52a, 52c move from their extended to the retracted positions, and the second and fourth linear drives 52b, 52d move from their retracted to extended positions.
  • this causes the drive elements 38, 39 to apply a force to the locking disc 36 via the interaction or cooperation between the drive element pins 50a, 50b and the engagement formations 42.
  • the drive elements 38, 39 move and so the locking disc 36 and the low-speed shaft 26 begin to rotate.
  • the drive elements 38, 39 convert the linear drive torque of the linear drives 52a, 52b, 52c, 52d to be converted into rotational drive torque of the locking disc 36.
  • the low-speed shaft 26 and rotor 16 are rotated until the rotor hub is in the appropriate position to accept or receive the first of the blades 18.
  • the drive elements 38, 39 (or drive shoes or callipers remain on the locking disc 36 during rotation of the locking disc 36).
  • the pressure in each of the cylinders is monitored by pressure sensors, and the pressure and flow is controlled so that the desired amount of rotation of the locking disc 36 is achieved.
  • This configuration of the low-speed drive 32 is illustrated in Figure 6d.
  • the locking disc 36 is rotated to a position in which engagement formations 42 of the locking disc 36 line up with, and are adjacent to, the locking pins 40.
  • the locking pins 40 are actuated using hydraulic power to move from the unlocked position to the locked position so as to restrain movement of the locking disc 36 and low-speed shaft 26 relative to the housing 34.
  • the inductive sensors are used to ensure that the locking pins 40 are fully inserted into the engagement formations 42 prior to initiating the next step of the rotation cycle process.
  • This configuration of the low- speed drive 32 is illustrated in Figure 6e, and the first of the blades may then be mounted to the rotor hub 16.
  • the rotor 16 In order for the second of the blades 18 to be mounted the rotor 16 must be rotated through an angle of 120° so that the rotor hub is in the appropriate position to receive the second of the blades 18.
  • the drive element pins 50a, 50b are moved from the engaged to the disengaged position so as to allow movement of the drive elements 38, 39 relative to the locking disc 36.
  • This configuration of the low- speed drive 32 is illustrated in Figure 6f.
  • the linear drives 52a, 52b, 52c, 52d are configured to return to their initial or reset positions by controlling the hydraulic pressure such that the first and third linear drives 52a, 52c move to their extended positions, and the second and fourth linear drives 52b, 52d move to their retracted positions.
  • This configuration is illustrated in Figure 6g, and it is noted that this‘reset’ position returns the low-speed drive 32 to the configuration illustrated in Figure 6a. Rotation of the rotor 16 to the appropriate position for the rotor hub to receive the second of the blades 18 is therefore effected by repeating steps 72 to 80.
  • the high-speed drive 30 and the low-speed drive 32 are actuated substantially simultaneously to cause rotation of the rotor 16.
  • the drive torque needed to cause rotation of the rotor may be provided by a combination of the high- and low-speed drives 30, 32, i.e. the required drive torque is split between the highl and low-speed drives 30, 32.
  • the torque split may be chosen to include any suitable combination of contributions from the two drives 30, 32.
  • the drive torque provided by the high-speed drive 30 is limited to be no greater than a maximum level of drive torque that the gearbox 24 may withstand, i.e. a drive torque capacity, without causing failure of the gearbox 24.
  • the drive torque capacity of the gearbox 24 may be less than the level of drive torque required to cause rotation of the rotor 16.
  • the low-speed drive 32 may therefore be used to make up the deficit in drive torque being provided to the rotor 16.
  • the total drive torque being provided by the high- and low-speed drives 30, 32 is greater than the maximum torque capacity of the gearbox 24.
  • a maximum operational drive torque of the wind turbine 10 i.e. a maximum level of drive torque that may be needed to rotate the (unbalanced or balanced) rotor 16 during the lifetime of the wind turbine 10, perhaps in relatively extreme weather conditions, e.g. high winds, is greater than the maximum torque capacity of the gearbox 24.
  • the high-speed drive 30 drives the high-speed shaft 28 close to the limit that the gearbox 24 may withstand.
  • the maximum drive torque that the high-speed drive 30 may provide is equal to the maximum torque capacity of the gearbox 24. It may be that the high-speed drive 30 provides the majority of the drive torque needed to rotate the rotor 16, with the low-speed drive 32 making up the shortfall, i.e. the sum of the drive torque being provided by the high- and low-speed drives 30, 32 is greater than the drive torque capacity of the gearbox 24.
  • the low-speed drive 32 needs to, or is chosen to, provide the majority of the drive torque to rotate the rotor 16, i.e. where the drive torque provided by the low- speed drive 32 is greater than that provided by the high-speed drive 30.
  • the low-speed drive 32 it is possible for the low-speed drive 32 to provide greater levels of drive torque to the drivetrain 20 than the high-speed drive 30.
  • the torque split between the high- and low-speed drives 30, 32 depends on the total torque required, and how much torque may be transferred through the gearbox 24.
  • the low-speed drive 32 may also be used to limit the torque transferred through the gearbox 24 in the event of a wind spike.
  • One or both of the drive elements 38, 39 and the locking pins 40 will always be engaged, and so can assist in dissipating torque that may otherwise be transferred through the gearbox 24 in the case of such an event.
  • the holes or engagement formations 42 along the periphery of the locking disc 36 are partial holes or open holes located at the very edge of the locking disc 36; however, in different embodiments, the engagement formations may be completely enclosed and/or may be located at any suitable location of the locking disc, for example, radially inwards relative to the engagement formations of the described embodiment, and/or may be of any suitable size or shape.
  • the drive elements 38, 39 are each formed in a single piece, i.e. two hydraulic pistons are connected to a single drive element having two pins for engaging with the locking disc.
  • each of the drive elements may be in two pieces so that one hydraulic piston is connected to one drive element piece having one pin for engaging with the locking disc, and another hydraulic piston is connected to another drive element piece having another pin for engaging with the locking disc. The two pieces of the drive element may then be positioned adjacent each other at the periphery of the locking disc.
  • each of the two drive elements 38, 39 has two pins 50a, 50b, i.e. a total of four pins 50a, 50b, and each of the four hydraulic pistons 56a, 56b, 56c, 56d is associated with a different one of the pins 50a, 50b.
  • each drive element may only include one pin for engaging with the locking disc, with two hydraulic pistons being associated with the same pin.
  • the engaging means is movable between the engaged and disengaged positions using hydraulic power; however, in different embodiments different means of power may be used to cause such movement, for example electric power.
  • different means of power may be used to cause such movement, for example electric power.
  • the use of electric power may be advantageous in that the power means may be more suited for positioning in a relatively tight space.

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Wind Motors (AREA)

Abstract

La présente invention concerne une éolienne comportant un rotor et une boîte de vitesses. L'éolienne comporte également un arbre à grande vitesse relié à la boîte de vitesses, et un arbre à faible vitesse ou un arbre de rotor destiné à accoupler le rotor à la boîte de vitesses. Un premier outil tourneur applique un premier couple d'entraînement à l'arbre à grande vitesse, afin d'appliquer un couple d'entraînement à l'arbre à faible vitesse par l'intermédiaire de la boîte de vitesses. Un second outil tourneur, entre le rotor et la boîte de vitesses, applique un second couple d'entraînement à l'arbre à faible vitesse, afin de provoquer la rotation du rotor.
PCT/DK2019/050409 2018-12-28 2019-12-18 Agencement d'éolienne et procédé associé WO2020135908A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DKPA201870868 2018-12-28
DKPA201870868 2018-12-28

Publications (1)

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WO2020135908A1 true WO2020135908A1 (fr) 2020-07-02

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060196288A1 (en) * 2004-11-18 2006-09-07 Rainer Aust Turning device
US20120133147A1 (en) * 2011-10-11 2012-05-31 Mitsubishi Heavy Industries, Ltd. Turning device for wind turbine rotor and wind turbine generator including the same
KR101346178B1 (ko) * 2012-06-22 2013-12-31 삼성중공업 주식회사 풍력발전기용 로터 회전장치
US20150308467A1 (en) * 2012-12-10 2015-10-29 Senvion Se Turn Drive for a Wind Turbine, and Method for Rotating the Rotor Shaft of a Wind Turbine
EP3385535A1 (fr) * 2017-04-07 2018-10-10 Adwen GmbH Système de verrouillage de rotor

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060196288A1 (en) * 2004-11-18 2006-09-07 Rainer Aust Turning device
US20120133147A1 (en) * 2011-10-11 2012-05-31 Mitsubishi Heavy Industries, Ltd. Turning device for wind turbine rotor and wind turbine generator including the same
KR101346178B1 (ko) * 2012-06-22 2013-12-31 삼성중공업 주식회사 풍력발전기용 로터 회전장치
US20150308467A1 (en) * 2012-12-10 2015-10-29 Senvion Se Turn Drive for a Wind Turbine, and Method for Rotating the Rotor Shaft of a Wind Turbine
EP3385535A1 (fr) * 2017-04-07 2018-10-10 Adwen GmbH Système de verrouillage de rotor

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