Flow spoiler control device and method and electronic operating module for adjusting a position of flow spoilers of a wind turbine together with the same

Abstract

The present invention relates to a flow spoiler control device (50) and to a method and an electronic operating module (9) for adjusting a position of flow spoilers (11) on blades (4) of a wind turbine (1), in particular a vertical-axis wind power plant, together with the same. In order to allow consistently reliable control along with long-term overload protection of the wind turbine (1) and reliable operation or at least shut-down of the wind turbine (1) itself in the event of a fault in individual components, the invention makes provision for a flow spoiler control device (50) to generate a substantially constant disruption force (FS) by way of at least a first drive unit (41) in order to move at least one of the flow spoilers (11) to a folded-open disruption position (S), in which it disrupts an air flow flowing from an inflow edge (12) up to an outflow edge (13) along an outer surface of the blade (4) and driving the wind turbine (1), and to leave the upward flow substantially unaffected by way of at least a second drive unit (42), with which a variable release force (FF), which counteracts the disruption force (FS), is generated in order to move the at least one flow spoiler (11) to a folded-closed release position (F), in which it is substantially flush with the outer surface.

Description

[0001] FLOW DISTANCE FLAP CONTROL DEVICE AS WELL AS METHOD AND ELECTRONIC OPERATING MODULE FOR ADJUSTING A POSITION OF FLOW DISTANCE FLAP OF A WIND TURBINE AND THE SAME

[0002] The present invention relates to a flow disturbance flap control device as well as a method and an electronic operating module for adjusting a position of flow disturbance flaps on blades of a wind turbine, in particular a vertical wind turbine, and the same.

[0003] State of the art

[0004] Damper control devices and methods for adjusting the position of dampers on the blades of wind turbines, such as vertical-axis wind turbines, are known from the prior art. Damper control devices serve to disrupt the airflow driving the vertical-axis wind turbines, resulting from the wind driving the blades and the rotation of the blades around a rotor axis of the wind turbine. This can prevent damage to the vertical-axis wind turbines, particularly at high wind speeds.

[0005] For example, EP 2 258 944 B1 discloses a control device for an aerodynamic brake comprising several components. It provides the simplest possible way to control the rotation of a wind turbine without wear using a brake that can be activated in failure situations without external control and bring the wind turbine to a standstill. A mass element is used to store mechanical energy, which can then be converted into aerodynamic braking.

[0006] CN 208534682 U discloses a vertical-axis wind turbine with a composite drag braking system, which allows the turbine's wind energy conversion system to start at low wind speeds and minimizes the influence of the respective wind direction. At excessive wind speeds, spoilers of the composite drag braking system are to be opened by centrifugal force to decelerate a rotor of the turbine.

[0007] EP 2 536 945 B1 relates to a control system for controlling the operation of a vertical axis wind turbine (VAWT) for generating power from an incoming fluid flow, comprising at least one flow-influencing arrangement associated with at least one blade of the VAWT. A control unit is connected to the flow-influencing arrangement, which comprises two flow-influencing units, each arranged on two opposite sides of the blade and operable to generate an inflow on the respective side of the blade, causing an increase in fluid flow momentum. The control unit is configured and operable to alternately activate the flow-influencing units in a predetermined time pattern, thus oscillating the inflow on the opposite sides of the blade.

[0008] JP 2011-27054 A describes a vertical-arc wind turbine whose blades open a flap with a weight element. If the blade rotates fast enough, the weight element pulls the flap away from the blade. At slower rotation, a spring element pulls the flap back toward the blade.

[0009] The disadvantage of prior art control devices and methods for adjusting the position of flow-influencing elements on wind turbine blades is that they do not allow for permanently reliable control of the wind turbine during normal operation, on the one hand, and their protection in the event of a potential overload at high wind speeds, on the other. Furthermore, the reliability of known control devices is unsatisfactory.

[0010] Description of the invention

[0011] The present invention is based on the object of at least mitigating, if not helping to eliminate, the disadvantages known from the prior art. In particular, the present invention is intended to enable consistently reliable control while simultaneously providing continuous overload protection for the wind turbine. Furthermore, the present invention is intended to enable reliable operation or at least shutdown of the wind turbine even in the event of a malfunction in individual components.

[0012] This object is achieved by a flow disturbance flap control device according to the invention in that it has a first drive unit which is designed to move at least one of the flow disturbance flaps into a deployed disturbance position by generating a substantially constant disturbance force, in which position it disrupts an air flow flowing from a leading edge to a trailing edge along an outer surface of the blades and driving the wind turbine, and at least one second drive unit which is designed to move the at least one flow disturbance flap into a folded-in release position with a variable release force counteracting the disturbance force, in which position it leaves the lift flow substantially unaffected, being largely aligned with the outer surface.In a method according to the invention, the object is achieved in that a substantially constant disturbing force is generated by means of a flow disturbance flap control device with at least one first drive unit in order to move at least one of the flow disturbance flaps into a deployed disturbing position in which it disrupts an air flow flowing from a leading edge to a trailing edge along an outer surface of the blades and driving the wind turbine, and with at least one second drive unit with which a variable release force counteracting the disturbing force is generated in order to move the at least one flow disturbance flap into a folded release position in which it leaves the lift flow substantially unaffected, being largely aligned with the outer surface.

[0013] With an electronic operating module for adjusting a position of flow disturbance flaps on blades of a wind turbine, the object is achieved in that the operating module is designed to carry out a method according to the invention.

[0014] In a wind turbine according to the invention, in particular a vertical wind turbine, the object is achieved by a flow disturbance flap control device according to the invention and / or an operating module according to the invention.

[0015] An advantage of the inventive solution over the prior art is that the first and second drive units can each contribute to the control and safety of the wind turbine by acting as agonists and antagonists, respectively. In other words, the release force seeks to move the spoiler into the release position, while the disturbance force seeks to move the spoiler into the disturbance position. The simultaneous, substantial constancy of the disturbance force creates a kind of inherent safety for the wind turbine in that, upon loss of the release force or in the event of a disturbance or failure of the second drive unit, the airflow spoilers are always moved into the disturbance position, thus decelerating the wind turbine or its rotor.Conversely, the release force generated by the second drive unit must first overcome the disturbance force generated by the first drive unit to move the flow disturbance flaps into the release position and thus enable proper operation of the wind turbine. Therefore, the inventive solution represents a way to simultaneously control and secure a wind turbine.

[0016] The inventive solution can be supplemented and further improved as desired by the following additional, individually advantageous embodiments. A person skilled in the art will readily recognize in the respective embodiments that device features of a flow spoiler control device according to the invention can each represent steps of a method according to the invention, and vice versa. According to a further embodiment, the first drive unit comprises at least one gas spring. The pressure of the gas spring can be continuously monitored. Thus, a pressure drop in the gas spring can trigger an alarm and thus call for maintenance or repair of the wind turbine.

[0017] According to a further embodiment, in an uncontrolled operating state of the wind turbine, the disturbance force is always greater than the release force. For example, an uncontrolled operating state can occur when corresponding control devices fail or when the wind turbine is idling. Since the disturbance force is always greater than the release force in such a state, the flow disturbance flaps are moved to the disturbance position, thus decelerating the rotor of the wind turbine.

[0018] According to a further embodiment, the release force in the release position is greater than or at least equal to the disruptive force. In other words, the release force applied by the first drive unit in the release position overcomes the disruptive force applied by the second drive unit or at least compensates for it. If this force is overcome, the at least one spoiler flap can, for example, rest against a stop limiting the release position, which makes it very easy to define the release position.

[0019] According to a further embodiment, it is provided that when changing from the fault position or an intermediate position to the release position from controlled operating states, the release force is greater than the disturbance force. In other words, the at least one flow disturbance flap can be set at different angles of attack with respect to the outer surface of the blade for the respective partial disturbance of the air flow flowing along the outer surface of the blades and driving the wind turbine. In a fixed setting position with the respective angle of attack, the disturbance force and the release force balance each other out. When the spoiler flap changes position towards the release position, the release force predominates over the disturbance force.This makes it surprisingly easy to provide a type of inherent safety because the release force must always exceed the disturbance force in order to reach the release position and, conversely, when the release force is removed, the predominant disturbance force always causes the flow disturbance flaps to move into the disturbance position.

[0020] According to a further embodiment, the airflow spoilers rest against a mechanical stop in the maximum fault position. The maximum fault position can be at an angle of attack of the airflow spoilers of substantially 90° with respect to the outer surface of the wing in order to achieve maximum disturbance of said airflow. The first drive unit can be designed such that it presses the spoilers into the maximum fault position before the first drive unit reaches its maximum deflection, which can be defined, for example, by a first deflection stop of the first drive unit. This prevents individual spoilers from no longer reaching the fault position, for example due to wear or malfunction of the first drive unit, such as signs of aging of the gas spring. This helps to further increase the operational reliability of an airflow spoiler control device according to the invention.

[0021] According to a further embodiment, the first drive unit provides the release force at least partially by generating hydraulic pressure via a hydraulic system. The hydraulic system can comprise an electrohydraulic drive module for generating hydraulic pressure. The electrohydraulic drive module can be electronically controlled very precisely and relatively easily by a corresponding electronic operating module.

[0022] According to a further embodiment, the hydraulic system comprises a single-acting hydraulic cylinder. This reduces the complexity and thus the susceptibility to failure of the hydraulic system. A self-contained, electrically driven hydraulic pump can be installed on the tower platform. By means of a rotary union, hydraulic oil or hydraulic fluid can be fed from the hydraulic pump on the tower platform through the hollow shaft of the turbine and a 3-way distributor, e.g. via support arms of the power blades, to the relevant hydraulic cylinders in the blades. Such a central pressure supply allows all flow spoilers to be controlled synchronously, thus avoiding unnecessary mechanical loads on the rotor structure that could be caused, for example, by uneven or different spoiler positions on different blades.In the event of a leak in the hydraulic system, the hydraulic pressure drops, causing the disturbance force to exceed the release force and therefore the spoilers to extend and ensure a safe operating condition of the turbine by automatically braking it.

[0023] According to a further embodiment, the hydraulic system comprises a bypass valve which, in an open position, reduces the hydraulic pressure to such an extent that the release force is less than the disturbance force. The bypass valve can be designed as an electromagnetic valve and arranged in an overflow channel. The overflow channel can connect a hydraulic cylinder to a hydraulic reservoir of the hydraulic system. The bypass valve can open the overflow channel, allowing hydraulic fluid to escape from the hydraulic cylinder and flow into the hydraulic reservoir, thereby reducing the hydraulic pressure in the hydraulic cylinder and thus reducing or eliminating the release force. The bypass valve thus helps to move the flow disturbance flaps into the disturbance position by reducing the hydraulic pressure.

[0024] According to a further embodiment, the bypass valve is open in its basic state (default). In other words, the bypass valve is designed as “normally open” (NO), e.g. in the form of a solenoid valve. As soon as the bypass valve is de-energized, it can open the overflow channel, allowing hydraulic fluid to escape from the hydraulic cylinder and flow into the hydraulic reservoir. This reduces the hydraulic pressure in the hydraulic cylinder and thus reduces or eliminates the release force. The bypass valve thus helps to provide an inherently safe flow disturbance valve control device according to the invention. In the event of load shedding, e.g. when no electrical power is available for control, such as in the event of malfunctions in the turbine’s electrical system, a lightning strike, or a power failure, the single-acting hydraulic cylinder can be actuated by the disturbance force orThe gas springs are pushed back, allowing the hydraulic oil to flow back into the reservoir through the solenoid valve. When the wind turbine is controlled by partially or fully extending the spoilers, the single-acting hydraulic cylinder can hold the spoilers at a selected position, directed against the airflow, against the force of the gas springs. The desired position of the hydraulic cylinder is fixed by the closed solenoid valve.

[0025] According to a further possibility for achieving the object according to the invention, it is provided that the at least one first drive unit and the at least one second drive unit are jointly connected to at least one of the airfoil spoilers in a force-transmitting manner via an airfoil spoiler control rod arrangement. Through the action of the airfoil spoiler control rod arrangement, the at least one first drive unit and the at least one second drive unit can be configured as antagonists, as already mentioned above. Thus, the airfoil spoiler control rod arrangement can assist in providing a way to simultaneously control and secure a wind turbine.

[0026] According to a further embodiment, the flow disturbance flap control rod arrangement comprises a rocker arm that is rotatably mounted about a rocker bearing point arranged between a first lever end and a second lever end of the rocker arm, wherein the first drive unit is connected to the first lever end in a force-transmitting manner, and the second drive unit is connected to the second lever end in a force-transmitting manner. The rocker arm represents a surprisingly simple solution for setting up the first drive unit and the second drive unit as antagonists. Therefore, the rocker arm can assist in providing simultaneous control and protection of a wind turbine in a relatively simple manner according to the invention.

[0027] According to a further embodiment, the rocker bearing point is arranged on a shaft rotation axis of a transmission shaft, which connects the rocker arm to a transmission rod for transmitting the disruptive force and / or the release force to the at least one flow disturbance flap in a torque-transmitting manner. The transmission rod can, for example, be designed as an intermediate rod arranged between the rocker arm and a control rod attached to the flow disturbance flap. Thus, either the first or the second drive unit can act directly on the rocker arm or the transmission rod to provide disruptive or release force. The transmission rod can thus help to design the first drive unit and the second drive unit as antagonists according to the invention.

[0028] According to a further embodiment, the at least one flow disturbance flap is designed to be movable in parallel pivoting manner between the release position and the fault position via a parallel pivoting device. For this purpose, the at least one flow disturbance flap can be held at at least two parallel pivot points or connected to the parallel pivoting device. The parallel pivoting device can comprise at least two pivot levers on which the at least two parallel pivot points can be arranged. In this way, the at least one flow disturbance flap can be moved with a parallel pivot. The at least one flow disturbance flap can essentially always extend parallel to a longitudinal axis of the wing and can be moved back and forth between the release position and the fault positions with a translational movement component, for example in or against the longitudinal direction.For this purpose, a transmission rod of the airfoil spoiler control rod arrangement can be connected to the drive unit in a torque-transmitting manner. The connection can be established via the rocker arm and / or a bell crank. The bell crank can be designed as a rocker arm and / or connected to the rocker arm in a force-transmitting manner, for example by coupling the rocker arm to the bell crank via an intermediate joint. Thus, the at least one airfoil spoiler can be pushed virtually transversely into and out of the airflow flowing along the outer surface of the wing. This helps to minimize the disturbing and release forces required to actuate the at least one airfoil spoiler. As a result, the components involved in the force transmission, as well as the at least one airfoil spoiler itself, can be provided with relatively little material and operated in an energy-efficient manner.

[0029] According to a further embodiment, at least two airfoil spoilers arranged on opposite side surfaces of the blades are each connected to the rocker arm via a control rod in a force-transmitting manner. In this way, airfoil spoilers arranged on the two opposite wing surfaces can be actuated synchronously with an airfoil spoiler control rod arrangement according to the invention. This allows for particularly effective control and protection of a wind turbine.

[0030] According to a further embodiment, a first control linkage is designed as a single piece with a first control rod, and a second control linkage is designed as a two-piece with a further control rod and the intermediate rod, the further control rod and the intermediate rod being connected to one another in series. The intermediate rod and control rod can be connected to one another in an articulated manner. The control rod of the first control linkage can be connected to the first lever end in a movement-transmitting manner. The intermediate rod, which is connected to the rocker arm in a torque-transmitting manner, can connect the rocker bearing point to the control rod of the second control linkage in a movement-transmitting manner. The first control linkage and the second control linkage thus serve to drive the first drive unit orThe second drive unit is designed to act as an antagonist and simultaneously connect it to the two airfoil spoilers located on opposite sides of the blade, transmitting power. This approach allows for highly effective control and safety of the wind turbine with the aid of synchronously operated airfoil spoilers located on both sides of its blades.

[0031] According to a further embodiment, the length of the intermediate rod essentially corresponds to the length of the distance between the rocker bearing point and the second lever end. The length of the intermediate rod can essentially correspond to the length of the distance between the rocker bearing point and the second lever end. The rocker bearing point can be arranged centrally between the lever ends. This allows the disturbing force and the release force to be mechanically balanced. In this way, the first drive unit and the second drive unit can have a substantially equal force ratio or be of the same dimensions.

[0032] According to a further embodiment of a method according to the invention, it can be provided that a rotor speed of the wind turbine is controlled using the at least one flow disturbance flap as an actuator. A nominal speed of the wind turbine can be used as the target value for the control. Thus, the power of the wind turbine can be limited relatively easily with the aid of the at least one disturbance flap to a nominal power corresponding to the nominal speed, which is particularly helpful for using the wind turbine at wind speeds above the nominal wind speed of the wind turbine.

[0033] According to a further embodiment of a method according to the invention, the disturbing force can be an elastic force stored in the first drive unit, and the release force can be a force generated by the second drive unit during controlled operation of the wind turbine. The elasticity of the disturbing force combined with simultaneous control of the release force helps to apply it appropriately in the event of any fluctuations in wind speed, in order to limit the rotor speed of the wind turbine accordingly with the shortest possible reaction time or to decelerate the rotor. This minimizes any latencies in the control and security of the wind turbine.

[0034] Short description of the characters

[0035] Embodiments of the present invention are described with reference to the figures listed below: They show:

[0036] Fig. 1 is a schematic front view of a wind turbine according to the invention;

[0037] Fig. 2 is a schematic perspective view of an uncovered blade segment of the wind turbine shown in Fig. 1, including flow spoilers in a maximum fault position;

[0038] Fig. 3 is a schematic side view of the wing segment shown in;

[0039] Fig. 4 is a schematic detailed view of the wing segment shown in Figs. 2 and 3 with a flow disturbance flap in the release position;

[0040] Fig. 5 is a schematic perspective view of a drive train according to the invention for the flow disturbance flaps of the wind turbine shown in Fig. 1;

[0041] Fig. 6 is a schematic representation of a flow disturbance flap control device according to the invention including a drive module with flow disturbance flaps in a maximum fault position;

[0042] Fig. 7 is a schematic representation of a flow disturbance flap control device according to the invention including a drive module with flow disturbance flaps in an intermediate fault position;

[0043] Fig. 8 is a schematic representation of a flow disturbance flap control device according to the invention including a drive module with flow disturbance flaps in a release position; and

[0044] Fig. 9 is a schematic cross-sectional view of a wing with a flow spoiler control device according to the invention including a parallel pivoting device with flow spoilers in a maximum fault position.

[0045] Fig. 10 is a schematic longitudinal sectional view of a wing with a flow spoiler control device according to the invention including a parallel pivoting device with flow spoilers in a maximum fault position.

[0046] Fig. 11 is a schematic cross-sectional view of a wing with a flow spoiler control device according to the invention including a parallel pivoting device with flow spoilers in a release position.

[0047] Fig. 12 is a schematic longitudinal sectional view of a wing with a flow spoiler control device according to the invention including a parallel pivoting device with flow spoilers in a release position.

[0048] Fig. 13 is a schematic plan view of a wind turbine according to the invention in operation including the electronic operating module.

[0049] Ways to implement the invention

[0050] Embodiments of the present invention are described in detail below with reference to the accompanying figures. It will be readily apparent, clear, and unambiguous for a person skilled in the art that the figures show only possible embodiments in which individual features or groups of features, as set forth above, can be combined or omitted as desired according to specific requirements.

[0051] Fig. 1 shows a schematic front view of a wind turbine 1 according to the invention, which extends along a lateral direction X, a transverse direction Y, and a vertical direction Z, which together define a Cartesian coordinate system. The wind turbine 1 comprises a tower 2 supporting a rotor 3 rotatable about a vertical rotation axis R3. The rotor 3 comprises blades 4, a rotor arm 5, and a rotor hub 6 mounted on the tower 2 for rotation about the rotation axis R3, to which the blades 4 are rigidly attached via two of the rotor arms 5 each.

[0052] Furthermore, the wind turbine 1 has a supply and control device 7, which comprises an energy conversion module 8 and an electronic operating module 9, which are connected to each other and to the rotor 3 via lines 10 and can be integrated into the tower 2 and / or arranged separately therefrom. The energy conversion module 8 can comprise at least one generator (not shown) for generating electrical current from wind power provided by the rotor 3. The electronic operating module 9 contains all the measuring and control devices required for operating the wind turbine 1 or is connected thereto via the lines 10.

[0053] Fig. 2 shows a schematic perspective view of an uncovered segment of one of the blades 4 of the wind turbine 1 shown in Fig. 1, including flow disturbance flaps 11 in a maximum disturbance position S max, wherein the coordinate system shown refers to the right wing 4 shown in Fig. 1 for the sake of simplicity and clarity. The wing 4 extends in the transverse direction Y from a leading edge 12 to a trailing edge 13 and comprises a plurality of ribs 14 arranged one above the other and spaced from one another in the height direction Z, each of which comprises a front rib segment 15 facing the leading edge 12, a middle rib segment 16 and a rear rib segment 17 facing the trailing edge 13.

[0054] The ribs 14 are connected to one another via a leading edge 18 forming the leading edge 12, a trailing edge 19 forming the trailing edge 13, a front spar 20 extending between the front rib segments 15 and the middle rib segments 16, and a rear spar 21 extending between the middle rib segment 16 and the rear rib segment 17. Furthermore, connecting strips 22 are provided on both sides in the outer region of the front rib segment 15, the middle rib segment 16, and the rear rib segment 17, which connect the ribs 14 to one another.

[0055] Fig. 3 shows a schematic side view of the segment of the wing 4 shown in Fig. 2. Here, it is clear that a mushroom-shaped recess is formed in the central rib segment 16, which serves as a flow disturbance flap control device receptacle 23. At the end of a stem of the mushroom shape, a fastening region 24 is provided, which is formed from a plurality of fastening openings 25 surrounding said end in a semicircle, whereby the end is designed as a shaft receiving section 26. The flow disturbance flap control device receptacle 23, in particular its shaft receiving section 26, serves to receive or fasten a flow disturbance flap control device according to the invention (see Fig. 5).

[0056] Fig. 4 shows a schematic detailed view of the wing segment shown in Figs. 2 and 3 with one of the airfoil spoilers 11 in a release position F, in which the airfoil spoiler 11 is substantially aligned with an outer skin (not shown here) of the wing 4. The airfoil spoiler 11 is attached to the front spar 20 via a hinge 27, wherein an inner tab 28 of the hinge 27 is attached to the spar 20 and an outer tab 29 of the hinge 27 carries the airfoil spoiler 11, while a hinge joint body 30 connects the inner tab 28 and the outer tab 29 to one another. The spar 20 is designed in profile, at least in a section facing the outer skin of the wing 4, like a T-beam with a corresponding T-profile at least on one side, wherein a web 31 of the T-profile is arranged between the front rib segment 15 and the middle rib segment 16 and a belt 32 of the T-profile carries the inner tab 28 of the hinge 27.

[0057] Fig. 4 further illustrates that the flow disturbance flap 11 has a fastening section 33 and a disturbance section 34. The fastening section 33 is designed to complement the outer tab 29 of the hinge 27, with the outer tab 29 and the fastening section 33 being aligned with one another such that they jointly form a flow disturbance surface 35, while an end of the flow disturbance flap 11 facing the hinge 27 ends in the region of the hinge joint body 30 or rests there. On a side opposite the flow disturbance surface 32, a nose-shaped stop 36 is formed on an end of the flow disturbance flap 11 pointing away from the hinge 27.

[0058] A length of the stop 36, measured vertically from the disturbance section 34 of the flow disturbance flap 35, is dimensioned such that the flow disturbance flap 11 rests against an outer skin of the wing 4 in the release position F, wherein the flow disturbance flap 11 and the belt 32 including the hinge 27 are arranged substantially within a flow influencing means 37 which is formed in the front rib segment 15 and the middle rib segment 26 in order to leave the lift flow substantially unaffected in the release position F. Furthermore, a connecting strip recess 38 is provided in which the connecting strip 22 is arranged such that it also leaves the lift flow substantially unaffected. In the present exemplary embodiment, the connecting strip is shaped as an S-profile in cross section. Fig. 5 shows a schematic perspective view of a drive train 39 according to the invention for the flow disturbance flaps 11 of the wind turbine 1 shown in Fig. 1.The drive train 39 is part of a flow disturbance flap control device 40 according to the invention, which comprises a first drive unit 41 and a second drive unit 42 for driving a transmission shaft 43 of the drive train 39. The transmission shaft 43 is composed of three shaft segments 43a, 43b, 43c, each of which is connected to one another via a sliding piece 44 and at least one Hardy disk 45 and is mounted in a shaft bracket 46, which is held mounted in the mounting area 24 of the shaft receiving section 26 by means of the mounting openings 25.

[0059] Fig. 5 further shows that the drive train 39 extends through the wing 4 essentially transversely to the ribs 14 or parallel to the vertical direction Z. Intermediate rods 47 in the form of drive levers for driving at least one of the flow disturbance flaps are connected to the transmission shaft 43 in a torque-transmitting manner. In particular, three intermediate rods are provided per shaft segment 43a-c.

[0060] Fig. 6 shows a schematic representation of a flow disturbance flap control device 50 according to the invention together with a drive module 51 and with the flow disturbance flaps 11 in the maximum fault position S ma x. The drive module 51 comprises the first drive unit 41 and the second drive unit 42. A spoiler control rod assembly 52 of the spoiler control device 50 mechanically connects the drive module 51 to the spoilers 11.

[0061] The first drive unit 41 is designed as a gas pressure spring and comprises a gas cylinder 53 with a gas piston 54, which has a gas piston plate 55 slidably received in the gas cylinder 53 essentially perpendicular to the rotational axis C43 of the transmission shaft 43, and a gas piston rod 56 attached thereto. A gas pressure PG of a gas prevailing in the gas cylinder 53 constantly acts on the gas piston plate 55 and seeks to push it toward the flow spoiler control rod assembly 52 with a corresponding disturbing force Fs, which also runs essentially perpendicular to the rotational axis C43 of the transmission shaft 43. The gas piston rod 56 transmits the disturbing force Fs to the flow spoiler control rod assembly 52 with the aid of a first force transmission means 57.

[0062] The second drive unit 42 is designed as a hydraulic system and comprises a hydraulic pump 60, a pressure relief valve 61, a check valve 62, a hydraulic cylinder 63, an electrically controlled solenoid valve 64, and a hydraulic reservoir 65, which are connected to one another via respective hydraulic lines 66 carrying hydraulic fluid. The hydraulic pump 60 and the solenoid valve 64 are each connected to the supply and control device 7 via lines 10. The lines 10 are designed here as power lines that supply drive or control current to the hydraulic pump 60 and the solenoid valve 64, respectively.

[0063] During operation of the wind turbine, the hydraulic pump 60 generates a hydraulic pressure by means of hydraulic fluid drawn from the hydraulic reservoir 65, which is limited by the pressure relief valve 61. Thus, a hydraulic pressure P H. The hydraulic cylinder 63 accommodates a hydraulic piston 67 with a hydraulic piston plate 68, which is also movable essentially perpendicular to the rotational axis C43 of the transmission shaft 43 and to which a hydraulic piston rod 69 is attached. The hydraulic pressure PH prevailing in the hydraulic cylinder 63 acts on the hydraulic piston plate 68 as a function of the output of the hydraulic pump 60 and the position of the solenoid valve 64 and attempts to push it toward the flow spoiler control rod arrangement 52 with a release force FF, which is also essentially perpendicular to the rotational axis C43 of the transmission shaft 43. The hydraulic piston rod 69 transmits the disturbance force FF to the flow spoiler control rod arrangement 52 with the aid of a second force transmission means 70.

[0064] The flow disturbance flap control rod assembly 52 comprises a rocker arm 80 with a first arm end 81, which is force-transmittingly connected to the first force-transmitting means 57, and with a second arm end 82, which is force-transmittingly connected to the second force-transmitting means 70. The rocker arm 80 is rotatably mounted at a rocker bearing point 82 between the first arm end 81 and a second arm end 82. Thus, the first drive unit 41 is force-transmittingly connected to the first arm end 81, and the second drive unit 42 is force-transmittingly connected to the second arm end 82.

[0065] The rocker bearing point 82 is arranged substantially on the rotational axis C43 of the transmission shaft 43. At least two of the flow disturbance flaps 11 are arranged on opposite side surfaces of the wings 4 and are connected to the rocker arm 80 in a force-transmitting manner via a first control linkage 85 and a second control linkage 86, respectively. The first of the control linkages 85 comprises at least one first control rod 87. The second control linkage 86 comprises at least one second control rod 88 and at least one of the intermediate rods 47.

[0066] The first control linkage 85 is connected to the first lever end 81 via a first intermediate joint 89 for transmitting the disturbance force Fs. The second control rod 88 and the intermediate rod 47 are connected to one another via a second intermediate joint 90 for transmitting the release force FF. The intermediate rod 47 is connected to the rocker arm 80 in a torque-transmitting manner by means of the transmission shaft 43. The first control rod 87 is connected to at least one of the flow disturbance flaps 11 via a first control joint 91, and the second control rod 88 is connected to at least one other of the flow disturbance flaps 11 via a second control joint 92.

[0067] A length of the intermediate rod measured between the rocker bearing point 83 and the second intermediate joint 89 essentially corresponds to the length of the distance between the rocker bearing point 83 and the second lever end 82. The rocker bearing point 83 is arranged essentially centrally between the lever ends 81, 82. Thus, the disturbing force Fs and / or the release force FF are transmitted to the flow disturbance flaps 11 by means of the rocker lever 80 in a substantially oppositely symmetrical manner, whereby the first drive unit 41 and the second drive unit 52 act antagonistically on the position of the flow disturbance flaps 11, or the disturbing force Fs and the release force FF act in opposite directions.

[0068] In the maximum fault position S shown in Fig. 6 ma x the disturbance force Fs is greater than the release force FF at least until the maximum disturbance position S max is reached. For this period, the gas pressure PG must therefore be essentially constant or at least large enough for the disturbance force Fs to exceed the release force FF. For this purpose, the power of the hydraulic pump 60 can be reduced accordingly and / or the solenoid valve 64 can be opened sufficiently so that the hydraulic pressure PH drops sufficiently. Advantageously, the solenoid valve 64 is designed as a bypass valve in the hydraulic line 66 leading to the hydraulic reservoir 65 in the "normally open" version, so that the hydraulic pressure PH drops sufficiently when the current in the line 10 supplying the solenoid valve 64 is correspondingly reduced or eliminated, for example in the event of a power failure, whereby the flow disturbance flaps 11 then automatically move to the maximum disturbance position S ma x can be moved.

[0069] Fig. 7 shows a schematic representation of the flow disturbance flap control device 50 including the drive module 51 with the flow disturbance flaps 11 in an intermediate fault position Sz as a further possible fault position S in addition to the maximum fault position S ma x. In the intermediate fault position Sz, the flow disturbance flaps 11 are positioned at an angle between the release position F and the maximum fault position S according to the respective requirements. ma x. To maintain the intermediate disturbance position Sz, the disturbance force Fs and the release force FF must balance each other or be balanced such that the flow disturbance flaps 11 assume a desired angle of attack, for which purpose the power of the hydraulic pump 60 and / or the position of the solenoid valve 64 can be regulated accordingly.

[0070] Fig. 8 shows a schematic representation of the flow disturbance flap control device 50 including the drive module 51 with flow disturbance flaps 11 in the release position F. To achieve this, the release force FF is greater than the disturbance force Fs at least until all disturbance positions S have been passed. For this period, the hydraulic pressure PH must therefore be essentially at least large enough for the release force FF to exceed the disturbance force Fs. For this purpose, the output of the hydraulic pump 60 can be increased accordingly, with the solenoid valve 64 being closed.

[0071] Fig. 9 shows a schematic cross-sectional view of a wing 4 with a flow spoiler control device 50 according to the invention together with a parallel pivoting device 100 with flow spoiler flaps 11 in the maximum fault position S max. For example, the parallel pivot device 100 comprises at least one pivot axis 101 and at least one pivot bearing 102, which holds the at least one pivot axis 101 rotatably movable about a pivot axis of rotation C i. The pivot bearing 102 can, for example, be fastened and / or formed on the front spar 20. At least one pivot lever 103 can be held rotatably movable about the pivot axis of rotation C i in a pivot point 104 on the pivot axis 101 and can be connected at an actuating joint 105 to a flow disturbance flap control rod arrangement 152 for actuating the at least one flow disturbance flap 11, which can extend along the height direction Z through a flow disturbance flap recess 137 formed in the rib.

[0072] The at least one flow disturbance flap 11 can be held at at least two parallel pivot points 106, which can be arranged, for example, at each end of a pivot lever 103. The at least one flow disturbance flap 11 can be designed like a T-profile. For this purpose, the at least one flow disturbance flap 11 can have a web section 110 and a band section 111. The web section 110 can extend in cross-section essentially parallel to the height direction Z and can be connected to the pivot levers 103 at the at least two parallel pivot points 106. In cross-section, the band section 111 can extend essentially parallel to the transverse direction Y and thus have a part pointing towards the leading edge 12 and a part pointing towards the trailing edge 13. The part pointing towards the leading edge 12 can be longer in cross-section than the part pointing towards the trailing edge 13.In this way, by obstructing the flow, a dynamic pressure on the side 11 facing the leading edge 12 and / or by promoting a flow separation on the side of the at least one airfoil spoiler 11 facing the trailing edge 13, a negative pressure can be increased and thus the efficiency of the at least one airfoil spoiler 11 can be improved. Fig. 10 shows a schematic longitudinal sectional view of the wing 4 with the airfoil spoiler control device 50 together with the parallel pivoting device 100 with airfoil spoilers 11 in the maximum fault position S. max. A pivoting contour 112 can be formed on the at least one airfoil spoiler 11 to enable it to pivot out of the airfoil spoiler recess 137 along a pivot plane that can extend substantially parallel to the lateral direction X and the vertical direction Z. The pivot levers 103 can be designed as double pivot levers such that they each have two lever ends, each with a parallel pivot point 106, in order to be able to simultaneously actuate at least two airfoil spoilers 11 arranged on opposite sides of the wing 4. At least one of the pivot levers 106 is connected to the airfoil spoiler control rod arrangement 152 via the actuating joint 105.The flow disturbance flap control rod arrangement 152 may comprise at least one transmission rod 153, which may be connected via a respective actuating joint 105 to both or, to avoid mechanical over-determination, to one of the at least two pivot levers 106 in the actuating joint 105 power transmission.

[0073] The at least one transmission rod 153 can extend through the wing 4 essentially parallel to the vertical direction Z and can be connected to the drive module 51 via a deflection lever 180 (see Figs. 6 to 8). The deflection lever 180 can have a first lever end 181, a second lever end 182, and a deflection bearing point in which it is mounted on the wing 4 so as to be rotatable and movable about a deflection axis Ci83. For example, the first lever end 181 is connected to the transmission rod 153 via a first intermediate joint 189, and the second lever end 182 is connected to the drive module 51 via a second intermediate joint 190.

[0074] The disturbing force Fs and the release force FF can be introduced into the second lever end 182 via the second intermediate joint 190, essentially opposite to or in the height direction Z. The second lever end 182 can be in the maximum disturbing position S ma x by the disturbing force Fs counterclockwise around the deflection axis Ci83 in the direction of the at least one flow disturbance flap 11. Thus, the first lever end 181 exerts a pull on the transmission rod 153 via the first lever joint 189, which can rotate the pivot levers 103 via at least one actuating joint 105, for example, also counterclockwise around their respective pivot axis of rotation C i in such a way that they move the at least two flow disturbance flaps 11 attached to them, for example, synchronously with one another, out of the respective flow disturbance flap recess 137 into the maximum disturbance position S max can be swiveled. In the maximum locking position S ma x, the pivot levers 103 can, for example, be perpendicular to the longitudinal direction X and / or to the transmission rod 153.

[0075] Fig. 11 shows a schematic cross-sectional view of the blade 4 with the airfoil control device 50 together with the parallel pivoting device 100 with airfoils 11 in the release position F. The airfoils 11 are pivoted completely out of the airfoil recesses 137. The band section 111 of the airfoils 11 can end essentially flush with an outer skin of the blade 4. Thus, the airfoils 11 or their band sections 111 can close the airfoil recesses 137. This helps to provide a relatively undisturbed blade profile with as few as possible or even no flow obstructions, such as any gaps in the outer surface of the blade 4 and / or elements protruding therefrom, whereby the efficiency of the wind turbine 1 can be further improved.

[0076] Fig. 12 shows a schematic longitudinal sectional view of the wing 4 with the airfoil control device 50 according to the invention, including the parallel pivoting device 100 with airfoils in the release position F. In the maximum release position F, the second lever end 182 can be rotated clockwise around the deflection axis Ci83 in the direction away from the at least one airfoil 11 by the release force FF. Thus, the first lever end 181 exerts pressure on the transmission rod 153 via the first lever joint 189, which can rotate the pivot levers 103, for example, also clockwise about their respective pivot rotational axis C i via at least one actuating joint 105, such that they can pivot the at least two airfoils 11 attached to them, for example, synchronously with one another out of the respective airfoil recess 137 into the release position F.In the release position F, the pivot levers 103 can, for example, be aligned at an acute angle to the longitudinal direction X and / or to the transmission rod 153.

[0077] Fig. 13 shows a schematic plan view of the wind turbine 1 in operation including the electronic operating module 9. For the sake of simplicity, the wind direction corresponds, for example, to the lateral direction X. A rotation of the rotor 3 about the rotation axis R3 is measured with a rotation angle α by corresponding sensors (not shown) connected to the operating module 9 in a signal-transmitting manner. With additional sensors, the wind speed v, wind direction and / or power output of the wind turbine or rotor can also be measured. Depending on the wind speed, four operating modes of the wind turbine 1 result with the respective position of the airflow spoilers 11, namely a power generation mode at wind speeds v below a nominal wind speed v rthe wind turbine 1 , a power generation mode at wind speeds above the rated wind speed v r , an idle mode and a standstill mode.

[0078] In power generation mode at wind speeds v below the rated wind speed v r the wind speed v is above a cut-in wind speed Vj n of the wind turbine 1. The rotation speed of the rotor 3 is controlled to achieve maximum power. For this purpose, the airflow spoilers 11 are usually in the release position F.

[0079] In power generation mode at wind speeds v below the rated wind speed v r the wind speed v is above the cut-in wind speed Vj nand still below a shutdown wind speed Vout of wind turbine 1. The rotation speed of rotor 3 is limited to a nominal rotation speed, and thus the power output of wind turbine 1 is limited to its nominal power. For this purpose, the airflow spoilers 11 are generally set to a fault position S depending on the respective circumstances or control requirements.

[0080] In idle mode, either the wind speed v can be less than the cut-in wind speed Vj n or greater than the cut-off wind speed v ou t. The rotation speed of the rotor 3 adjusts itself depending on the wind speed. The airflow spoilers 11 are in the maximum fault position S ma x.

[0081] In standstill mode, any wind speed can prevail down to a maximum design wind speed Vmaint of the wind turbine. The rotor 3 is stationary, for example, due to the activation of a mechanical brake (not shown). The airflow spoilers 11 are in the maximum fault position S ma x.

[0082] Deviations from the embodiments described above are possible within the scope of the inventive concept. Thus, a wind turbine 1 according to the invention can have any desired design of tower 2 and rotor 3 with a number of blades 4, rotor arms 5, rotor hubs 6, supply and control devices 7, energy conversion modules 8, electronic operating modules 9 with corresponding lines 10, flow disturbance flaps 11, leading edges 12, trailing edges 13, ribs 14, front rib segments 15, middle rib segments 16, rear rib segments 17, leading edges 18, trailing edges 19, front spars 20, rear spars 21, connecting strips 22, flow disturbance flap control device receptacles 23, fastening areas 24, fastening openings 25, shaft receiving sections 26, hinges 27, inner tabs 28, outer tabs 29, hinge joint bodies 30, webs 31, Belts 32, fastening sections 33, interference sections 34,Flow disturbance surfaces 35, stops 36, flow disturbance flap recesses 37, connecting bar recesses 38, drive trains 39, flow disturbance flap control devices 40, first drive units 41, second drive units 42, transmission shafts 43 with rotation axes C43, shaft segments 43a-c, sliding pieces 44, Hardy discs 45, shaft brackets 46, intermediate rods 47, flow disturbance flap control devices 50, drive modules 51, flow disturbance flap control rod assemblies 52, gas cylinders 53, gas pistons 54, gas piston plates 55, gas piston rods 56, first power transmission means 57, hydraulic pumps 60, pressure relief valves 61, check valves 62, hydraulic cylinders 63, solenoid valves 64, hydraulic tanks 65, hydraulic lines 66, Hydraulic piston 67, hydraulic piston plate 68, hydraulic piston rods 69, second power transmission means 70, rocker arms 80, first lever ends 81, second lever ends 82, rocker bearing points 83, first control rods 85,second control linkage 86, first control rods 87, second control rods 88, first intermediate joints 89, second intermediate joints 90, first adjusting joints 91, second adjusting joints 92, parallel pivot devices 100, pivot axes 101 with pivot axes C101, pivot bearings 102, pivot levers 103, pivot pivot points 104, actuating joints 105, parallel pivot points 106, web sections 110, band sections 111, pivot contours 112, flow spoiler cutouts 137, flow spoiler control rod assemblies 152, transmission rods 153, reversing levers 180, first lever ends 181, second lever ends 182, deflection bearing points 183 with deflection axes C183, first intermediate joints 189 and / or second intermediate joints 190, which can be designed according to the respective requirements to be dependent on a wind speed v, switch-on wind speed Vj, n , design wind speed v ma int, cut-off wind speed v out and / or nominal wind speed v r required disturbance forces Fs, release forces FF, gas pressures PG hydraulic pressures P H , fault positions S, maximum fault positions S ma x and / or intermediate fault positions Sz ready or to be set. List of reference symbols

[0083] 1 wind turbine 33 mounting section

[0084] 2 Tower 34 Stör section

[0085] 3 Rotor 35 Flow disturbance surface

[0086] 4 wings 36 stop

[0087] 5 Rotor arm 37 Flow spoiler recess

[0088] 6 Rotor hub 38 Connecting bar recess

[0089] 7 Supply and 39 drive train

[0090] Control device 40 flow spoiler control

[0091] 8 Energy conversion module setup

[0092] 9 electronic operating module 41 first drive unit / gas spring

[0093] 10 Line 42 second drive unit / hydraulic

[0094] 11 Flow disturbance flap system

[0095] 12 Leading edge 43 Transmission shaft

[0096] 13 Trailing edge 43a-c shaft segment

[0097] 14 Rib 44 Sliding piece

[0098] 15 anterior rib segment 45 Hardy disc

[0099] 16 middle rib segment 46 shaft bracket

[0100] 17 rear rib segment 47 intermediate rod (drive lever)

[0101] 18 Nosing strip 50 Flow spoiler control

[0102] 19 End bar device

[0103] 20 front spar 51 drive module

[0104] 21 behind spar 52 spoiler control rods

[0105] 22 connecting strip arrangement

[0106] 23 Flow spoiler flaps 53 Gas cylinder control device holder 54 Gas piston

[0107] 24 Mounting area 55 Gas piston plate

[0108] 25 Mounting holes 56 Gas piston rod

[0109] 26 Shaft receiving section 57 first power transmission means

[0110] 27 Hinge 60 Hydraulic pump

[0111] 28 inner tab 61 pressure relief valve

[0112] 29 outer tab 62 check valve

[0113] 30 hinge joint bodies 63 hydraulic cylinders

[0114] 31 Bridge 64 Solenoid valve / bypass valve

[0115] 32 Belt 65 Hydraulic tank Hydraulic line 189 First intermediate joint

[0116] Hydraulic piston 190 second intermediate joint

[0117] Hydraulic piston plate

[0118] Hydraulic piston rod v Wind speed second power transmission means vin Switch-on wind speed

[0119] Rocker lever Vmaint Design wind speed first lever end Vout Cut-off wind speed second lever end v r Nominal wind speed

[0120] Rocker bearing point first control rod C43 Rotation axis second control rod Ci83 Deflection axis first control rod C101 Pivot rotation axis second control rod F Release position first intermediate joint Fs Disturbance force second intermediate joint FF Release force first control joint PG Gas pressure second control joint PH Hydraulic pressure

[0121] Parallel swivel device R3 rotation axis

[0122] Swivel axis S Fault position

[0123] Swivel bearing Smax maximum fault position

[0124] Swing lever Sz intermediate locking position

[0125] Pivot point X Side direction

[0126] Actuating joint Y transverse direction

[0127] Parallel pivot point Z height direction

[0128] Web section a rotation angle

[0129] Band section

[0130] Swing-out contour

[0131] Flow spoiler recess

[0132] Flow spoiler control rod arrangement

[0133] transmission rod

[0134] Bell crank first lever end second lever end

[0135] Deflection bearing point

Claims

Patent claims 1. A flow disturbance flap control device (50) for adjusting a position of flow disturbance flaps (11) on blades (4) of a wind turbine (1), in particular a vertical wind turbine, comprising at least one first drive unit (41) which is designed to move at least one of the flow disturbance flaps (11) into a deployed, disrupted position (S) by generating a substantially constant disruptive force (Fs), in which position it disrupts an air flow flowing from a leading edge (12) to a trailing edge (13) along an outer surface of the blades (4) and driving the wind turbine (1), and comprising at least one second drive unit (42) which is designed to move the at least one flow disturbance flap (11) into a retracted, released position (F) with a variable release force (FF) counteracting the disruptive force (Fs), in which position it leaves the lift flow substantially unaffected, being largely aligned with the outer surface.

2. Flow disturbance flap control device (50) according to claim 1, characterized in that in an uncontrolled operating state of the wind turbine (1) the disturbance force (Fs) is always greater than the release force (FF).

3. Flow disturbance flap control device (50) according to claim 1 or 2, characterized in that, in the case of changes from the disturbance position (S, S ma x) or an intermediate fault position (S, Sz) into the release position (F) the release force (FF) is greater than the fault force (Fs).

4. Flow disturbance flap control device (50) according to at least one of claims 1 to 3, characterized in that the second drive unit (42) provides the release force (FF) at least partially by generating a hydraulic pressure (PH) via a hydraulic system.

5. Flow disturbance flap control device (50) according to claim 4, characterized in that the hydraulic system comprises a bypass valve (64) which, in an open position, reduces the hydraulic pressure (PH) to such an extent that the release force (FF) is less than the disturbance force (Fs).

6. Flow disturbance flap control device (50) according to claim 4 or 5, characterized in that the one bypass valve (64) is open in its basic state.

7. Flow disturbance flap control device (50) according to at least one of claims 1 to 6, characterized in that the at least one first drive unit (41) and the at least one second drive unit (42) are jointly connected to at least one of the flow disturbance flaps (11) in a force-transmitting manner via a flow disturbance flap control rod arrangement (52).

8. Flow disturbance flap control device (50) according to claim 7, characterized in that the flow disturbance flap control rod arrangement (52) comprises a rocker lever (80) which is rotatably mounted about a rocker bearing point (83) arranged between a first lever end (81) and a second lever end (82) of the rocker lever (80), wherein the first drive unit (41) is connected to the first lever end (81) in a force-transmitting manner and the second drive unit (42) is connected to the second lever end (82) in a force-transmitting manner.

9. Flow disturbance flap control device (50) according to claim 8, characterized in that the rocker bearing point (83) is arranged lying on a shaft rotation axis (C43) of a transmission shaft (43) which connects the rocker arm (80) to an intermediate rod (47) for transmitting the disturbance force (Fs) and / or the release force (FF) to the at least one flow disturbance flap (11) in a torque-transmitting manner.

10. Flow disturbance flap control device (50) according to at least one of claims 1 to 9, characterized in that the at least one flow disturbance flap (11) is designed to be movable in parallel pivoting manner between the release position (F) and the fault position (S) via a parallel pivoting device (100).

11. Method for adjusting a position of airflow disturbance flaps (11) on blades (4) of a wind turbine (1), in particular vertical wind turbine, wherein by means of an airflow disturbance flap control device (50) with at least one first drive unit (41) a substantially constant disturbing force (Fs) is generated in order to move at least one of the airflow disturbance flaps (11) into a deployed disturbing position (S), in which it disrupts an airflow flowing from a leading edge (12) to a trailing edge (13) along an outer surface of the blades (4) and driving the wind turbine (1), and with at least one second drive unit (42) with which a variable release force (FF) counteracting the disturbing force (Fs) is generated in order to move the at least one airflow disturbance flap (11) into a folded-in release position (F), in which it largely aligns with the outer surface, the lift flow in essentially unaffected.

12. Method according to claim 11, characterized in that a rotor speed of the wind turbine (1) is controlled with the at least one spoiler flap (F) as an actuator.

13. The method according to claim 11 or 12, characterized in that the disturbance force (Fs) is an elastic force stored in the first drive unit (41) and the release force (FF) is a force generated by the second drive unit (42) in a controlled operation of the wind turbine (1).

14. Electronic operating module (9) for adjusting a position of flow disturbance flaps (11) on blades (4) of a wind turbine (1), in particular a vertical wind turbine, characterized in that the electronic operating module (9) is designed to carry out a method according to one of claims 11 to 13.

15. Wind turbine (1), in particular a vertical wind turbine, characterized by a flow disturbance flap control device (50) according to at least one of claims 1 to 11 and / or by an electronic operating module (9) according to claim 14.

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