• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a rotor head (1) for a wind energy system (2) with a rotor hub (6), with rotor blades (7) disposed thereon and with an adjusting device (20; 120; 220; 320) for adjusting pitch angles (8) for the rotor blades ( 7), wherein the adjusting device (20; 120; 220; 320) comprises a hydraulically drivable adjusting device (21; 221; 321) for changing the pitch angles (8) of the rotor blades (7), the adjusting device (20; 120; 220; 320) comprises an electrohydraulic drive (50; 250, 275; 350) for hydraulically driving the hydraulically drivable adjusting device (21; 221; 321) and / or for each rotor vane (7) an electromechanical driving device (36) for mechanically driving it hydraulically adjustable adjusting device (21; 221; 321), the driving devices (36, 50; 250, 275; 350) being arranged in the rotor hub (6).
    公开号:DK201200793A
    申请号:DKP201200793
    申请日:2012-12-14
    公开日:2013-06-17
    发明作者:Froehlich Udo；Doertoluk Ibrahim
    申请人:Bosch Gmbh Robert；
    IPC主号:
    专利说明:

    Description of the Invention The present invention relates to a rotor head for a wind power plant with a rotor hub, with rotor blades disposed thereon and with an adjustment end for adjusting pitch angles for the rotor blades, the adjustment device comprising a hydraulically drivable adjusting device for changing the pitch angle of the rotor blades.
    In addition, the invention relates to a wind energy egg having a tower device for providing a distance between a rotatable nacelle device and a support, with a rotor head rotatably mounted on the rotatable nacelle device.
    From the international patent application WQ 2QQ9 / 064264 A1, a wind energy system with variable adjustable rotor blades mounted on a rotor hub is known with respect to their pivot angle! The rotor hub is rotatably mounted on a nacelle in the wind energy system with a rotor shaft. For alteration and adjustment, respectively, an improved electrohydraulic alignment drive is proposed, whose main components are not located in the nacelle but in the rotor hub. The electro-hydraulic adjustment drive comprises an electric motor for operating a hydraulic pump and is moved by means of a hydraulic fluid in a hydraulic system connected to the hydraulic pump. The hydraulic line system comprises for each rotor vane a double-chamber hydraulic cylinder, by means of which the individual piichvinkei for each rotor vane can be set operationally dependent. The electro-hydraulic adjusting drive further comprises an emergency drive mechanism for, in an emergency, for example, in the event of a failure of the electric motor to drive the hydraulic pump, to be able to turn the rotor blades reliably at least to a neutral pitch angle position, in which the rotor blades are largely removed from the wind. To this end, the emergency drive mechanism comprises a high-pressure storage medium for storing a sufficient subset of high-pressure hydraulic fluid by means of which the individual dual-chamber hydraulic cylinders can be emergency operated. The high-pressure bearing is supplied by the electric motor-driven hydraulic pump before the wind-energy system is commissioned, ie before the rotor blades are turned, the wind.
    It is the object of the present invention to further develop wind energy eggs of the type mentioned in the introduction so that emergency operation on the one hand can be realized particularly compact, but on the other hand can be guaranteed extremely reliable.
    This task according to the invention is solved by a rotor head for a wind power plant with a rotor hub, with rotor blades mounted thereon and with a positioning device for adjusting pitch angles for the rotor blades, the adjustment device comprising a hydraulically drivable adjusting device for changing the pitch angle for rotor blades an electrohydraulic drive device for hydraulic operation of the hydraulic drivable adjustment device and for each rotor vane an electromechanical drive device for mechanically driving the hydraulically drivable adjusting device, the drive devices being arranged in the rotor hub.
    Since the electro-hydraulic drive as well as the electromechanical drive is arranged in the rotor head, in the present case, the advantages of both driving concepts according to the invention are provided in the smallest space within the rotor head.
    Particularly because of the present electro-hydraulic drive device, a substantially fully self-contained emergency drive device can be constructed, in a particularly simple manner, by means of which the adjusting devices for all rotor blades can be controlled centrally and jointly in the case of emergencies. It is readily apparent that, for these reasons alone, the emergency SOP drive device can be constructed very compact in design, so that it can also be placed within the rotor head without any problems.
    As a rule, an emergency purchase drive device of the type mentioned above can only be realized considerably more cumbersome, especially in the control technique, by means of the electric power mechanism in the safe driving direction.
    An emergency is, for example, caused by the failure of an electric drive motor for the adjusting device.
    In such an emergency, an adjustment of the pitch angle is no longer ensured on the basis of the engine power of an electric drive motor.
    On the other hand, in a normal operating condition, it is constructively easy to achieve a very precise pitch angle adjustment for the individual rotor blades by means of the electromechanical drive device. Preferably, very high reliability can be ensured in this way, in order to be able to relieve the rotor blades very quickly by adjusting their pitehwinki, especially in connection with critical winds.
    With the possibility of realizing a constant pressure system, the present tuning unit can be further operated significantly more energy efficiently. Also, the cost can be advantageously reduced.
    It should be understood that the number of rotor blades can be selected differently. In this connection it is also possible that the rotor head can only be fitted with a single rotor blade.
    The term "electro-hydraulic drive device" in the meaning of the invention describes a drive device for the hydraulically drivable adjusting device, which is distinguished by a hydraulic unit with a hydraulic pump, a hydraulic high-pressure sensor, a hydraulic-low-pressure sensor and a hydraulic line system ten! hydraulic connection of the aforementioned hydraulic unit components and icing the hydraulically drivable adjusting device, the hydraulic cooling system including hydraulic components such as valves and the like. The hydraulic pump is preferably driven by an electric motor.
    The term "electromechanical drive device" in the sense of the invention also describes a drive device for the hydraulically drivable adjusting device which is distinguished by a mechanical drive unit driven by an electric motor attached to it.
    The object of the invention is also solved by a wind energy system with a tower in the direction of providing a distance between a rotatable nacile arrangement and a substrate on which a rotor head and rotor head are rotatably mounted in accordance with one of the features described here.
    Such a wind power plant can be operated much more reliably and efficiently in comparison with known wind power plants. Furthermore, the construct is substantially simpler in design.
    If the hydraulically actuated adjusting device has a double cam cylinder or hydraulic motor, an adjustment of the pitch angle can be made in a very small space in terms of design.
    An exceptionally advantageous operation of the twin-chamber cylinder can be obtained when the electric drive device comprises a ball-driven drive device, which is mechanically mounted directly on a stern pelement, driven by an electric drive motor
    If the ball screw driver is mechanically directly functionally connected to a piston member of a double-chamber cylinder in the hydraulically drivable adjusting device, a direct mechanical connection between the electric drive motor and the hydraulically drivable adjusting device may be provided. Hereby an immediate and very precise adjustment of the pitch angle can be achieved.
    If the electro-hydraulic drive device has a hydraulic high-pressure sensor or a self-propelled additional electric motor, a particularly high emergency operating reliability can be achieved.
    It is to be understood that in the case of a self-propelled additional electric motor, this may be an AC motor connected to a public power grid. ideally, however, in the case of the self-propelled additional electric motor, it is a direct current electric motor, which is preferably supplied with electrical energy from an accumulator. This can also increase emergency operational security.
    According to a further aspect of the invention, the present invention is also solved by a rotor head for a wind energy egg having a rotor hub, with rotor blades mounted thereon, and with an adjusting device for adjusting pito angles for the rotor blades, wherein the adjusting device comprises a hydraulically drivable adjusting device. change the pitch of the rotor blades, the rotor head also being characterized in that the adjusting device comprises more than one electro-hydraulic drill winding, each of the electro-hydraulic drive devices being hydraulically connected with its own connections ten! the hydraulic drive bar adjustment unit.
    With the aid of an additional electro-hydraulic drive device, the electromechanical® drive device can advantageously be omitted as well. Yet, an unusual emergency operating device can be realized.
    Advantageously, the two electro-hydraulic drive devices with respect to the hydraulics are spatially spaced as far apart as possible and only hydraulically interconnected via the twin-chamber cylinder. In this way, a self-employed emergency operating device can be constructed well in terms of design.
    In addition, it is advantageous that one of the electro-hydraulic drive devices comprises a self-propelled additional electric motor, in particular a direct current motor, since it can still ensure the operation of a hydraulic pump even in the event of a power failure, in particular by a mains supply device for a wind energy hi. advantageously in connection with one of the electro-hydraulic drive devices, a hydraulic high-pressure bearing is omitted, whereby the constructive construction of the present filling device can be further reduced.
    In this context, it is particularly advantageous in this context that one of the electro-hydraulic drive devices merely comprises a hydraulic impression sensor.
    When the electro-hydraulic drive device comprises a hydraulic motor unit with a hydraulic motor, with a fixed-egg yeast device for determining a rotor vane axis! and with a gear device, the hydraulically drivable adjusting device can advantageously be equipped with a hydraulic motor,
    Other advantages of the present invention are to be seen in that a pressure generation relative to the hydraulically drivable adjusting device does not have to take place further in a nacelle device, whereby a corresponding passage of hydraulic lines between the nacelle device and the rotor hub can be undone. In this way, significant movements of ice in the dead zone in the transition zone between the nacelle device and the rotor hub are eliminated, so that a corresponding maintenance and repair cost and associated costs can be significantly reduced. In addition, the amount of hydraulic fluid required by the present compact design is also reduced, thereby further reducing costs.
    Further advantages, objects and features of the present invention are explained by means of the accompanying drawings and the following description, by way of example, showing and describing a wind power plant and then various adjusting devices for adjusting pite hooks for rotor blades. The drawing shows; FIG. 1 is a schematic view of a wind energy egg having a rotor head according to the invention, comprising one of the adjusting devices shown in the following figures; Fig. 2 is a schematic diagram of a first adjustable device which is applicable to the rotor head of Fig. 1 with an electromechanical drive device according to the invention and with a hydraulic emergency drive device comprising a hydraulic high-pressure bearing; FIG. 3 is a schematic of a further view of the rotor head of FIG. 1 an adjustable device according to the invention useful with an electromechanical drive device and with an electro-hydraulic emergency drive device comprising a self-propelled emergency drive motor; FIG. 4 schematically shows an alternative to the rotor head of FIG. 1 applicable adjusting device according to the invention with an electro-hydraulic drive device and with a hydraulic emergency drive device comprising a hydraulic high-pressure bearing; and FIG. 5 schematically shows a further rotor head in FIG. 1, an adjustable device according to the invention, usable with an electro-hydraulic drive device and with a hydraulic emergency drive device comprising a hydraulic high-pressure bearing.
    The FIG. Rotor head 1 according to the invention is arranged on a wind power plant 2, which comprises a tower device 3, on which a nacelle device 5 rotatably mounted on a vertical axis 4 of the wind power plant 2 is mounted on the upper side of the tower device. as read-page or page-page runners. The transmission device 5 may also possibly be designed as a machine housing (not explicitly provided here).
    With its rotor hub 6, the rotor head 1 is pivotally mounted with the aid of a rotor shaft, which is not shown in detail here. The rotor hub 6 carries three rotor blades (here, for example, only with reference thread), which with respect to their pitch angle 8 are each rotatable. Conquered on rotor hub 6 around a pitch angle axis 9. For this, in the rotor head 1 and 1 respectively. located in the rotor hub 6 one of the adjusting devices 20 (see FIG. 2), 120 (see FIG. 3), 220 (see FIG. 4) or 320 {see FIG. 5), whereby the wind energy system 2 is substantially improved in conjunction with known wind energy eggs.
    Pen as shown in FIG. 2 as the first embodiment, setting adjustment 20, comprises a hydraulically drivable adjustment tube 21 formed as a double-chamber cylinder 22. A double housing 22 comprises a cylinder housing 23 with a longitudinal axis 24 displaceably mounted in a cylinder housing 25. The cylinder piston 25 comprises a piston rod 28 with a partition 27 which subdivides one of the hydraulic volumes formed by the cylinder housing 23 into a first hydraulic chamber 23 and a second hydraulic chamber 29, the size of the individual hydraulic chambers 28 and 29 being adjustable depending on the position of the cylinder piston 25. relative to the cylinder housing 23. At its first end 30, the cylinder piston 25 is functionally concentric to one of the rotor blades 7, such that a translational movement of the cylinder piston 25 along the longitudinal extension 24 causes a rotational adjustment movement of the rotor blade 7, whereby the pivot wing of the rotor blade 7 ka n changes.
    In this first embodiment, the adjusting device 20 as the main drive device 35 in the hydraulically driven adjusting device 21 comprises an electromechanical drive device 36 for mechanically driving the hydraulically drivable adjusting device 21. The electromechanical drive device 36 is characterized by an electric drive motor 37 and a ball-driven drive device 38. a coupling device 39 is interconnected.
    The ball screw drive device 38 has a threaded rod 40 driven by the electric drive motor 37. The threaded rod 40 is pivotally mounted in a housing 42 for the ball screw drive 38. The housing 42 further houses two guide rods 43, 44 on which a drive hub 40 is mounted. 45 for the ball screw driver 38 is translationally guided, the drive hub 45 by means of the threaded rod 40 being translational. displaceable and this in the direction of the longitudinal axis 24 of the double-chamber cylinder 22. On the drive hub 45 is provided a fastening flange 46, to which again a connecting link 47 is attached, which is also connected at a second end 48 to the cylinder stern 25.
    Preferably, the hydraulic actuator adjusting device 21, by means of the electromechanical actuator 38, can be designed in a simple and particularly accurate manner.
    In addition to the electromechanical drive device 36, the adjusting device 20 further comprises an electro-hydraulic drive device 50 for hydraulically driving the hydraulically drivable adjustment device 21. The electro-hydraulic drive device 50 comprises a hydraulic line system 51, which with a first hydraulic line section 52 is connected to a first chamber connection 53 the first hydraulic chamber 28 of the double chamber cylinder 22.
    In addition, the hydraulic sealing system 51, by means of a second hydraulic sealing section 54, is connected to another chamber connection 55 to the second hydraulic chamber 29 in the double chamber cylinder 22.
    Further, the hydraulic boiler system comprises 51 and 51 respectively. the electro-hydraulic drive device 50 is a hydraulic pump 56, which is driven by a hydraulic pump in the drive motor 57.
    In addition, the hydraulic line system has 51 and 1 respectively. the electro-hydraulic drive device SO over a hydraulic high pressure bearing 58 and a hydraulic pressure bearing 59.
    between the hydraulic pump 56 and the hydraulic high pressure bearing 58, a first non-return valve 60 is arranged, while an additional conical valve 61 is arranged between the hydraulic pressure bearing 59 and the second hydraulic discharge section 54.
    Between the hydraulic high-pressure bearings 58 and the first hydraulic seal section 52, a directional control valve 62 is further arranged.
    Before commissioning the wind power system 2, the hydraulic high-pressure bearing 58 is charged by means of the hydraulic pump 56. In this way, the directional valve 62 is in the position 62A, in which a hydraulic fluid coming in the direction from the hydraulic pump 56 cannot pass the directional valve 62. The hydraulic pump 56 hereby sucks up further hydraulic fluid from the hydraulic pressure bearing 59 and pumps this to the hydraulic high pressure storage unit 58. in the hydraulic high-pressure storage 58, the hydraulic pump drive motor 57 is switched off. The high-pressure hydraulic fluid remains essentially in the hydraulic high-pressure storage 58 since an avoidance is prevented by the check valve 60 on one side and on the other side by the directional control valve 62.
    In this mode of operation, the normal drive of the wind power system 2 can be accommodated, at which the rotor blades 7 are driven to an appropriate pitch angle 8. This is done by means of the electromechanical diaphragm unit 36, which drives the hydraulically drivable adjusting device 21, which comprises the double chamber cylinder 22, and moves the displaceably-mounted cylinder piston 25 along the longitudinal axis 24 in the direction of exit 63. Thus, the hydraulic fluid flows from the second hydraulic chamber 20 via the second hydraulic chamber section 54, the directional control valve 62 and the first hydraulic seal section 52 into the first hydraulic chamber 28, preventing the outflow connection of the check valve 61 the hydraulic fluid from the second hydraulic link section 54 in the direction of the hydraulic impression bearing 59. A run-in of the cylinder piston 25 occurs in the reverse order, an emergency now occurs, for example, that the electric drive motor 37 becomes powerless and the main drive device 35 with its own ctromechanical drive device 36 is no longer operational, the adjusting device 20 switches to an emergency fluid drive 1, which activates the electro-hydraulic drive 51 as an emergency fluid drive device 65. hydraulic section 52 and the first camber connection 53 flow ten! the first hydraulic chamber 28 in the double chamber cylinder 22, whereby the cylinder piston 25 is moved in the exit direction 63. Hereby the hydraulic fluid from the second cylinder chamber 29 is via the second chamber connection 55 and the second hydraulic seal section 54 and via the check valve 61 displaced to the hydraulic impression spring cylinder 59. 25 has run out completely. The double chamber cylinder 22 remains in this position since the first hydraulic chamber 28 is completely hydraulically separated from the second hydraulic chamber 29. Thus, the force effect of the double chamber cylinder 22 is maintained in accordance with the hydraulic pressure of the hydraulic high pressure bearing 56.
    The FIG. 3, as shown in the second embodiment, further adjustment device 120 has substantially the same structure as adjustment device 20 in FIG. 2. Here, only the differences from the first embodiment of FIG. 2. explained, in order to avoid repetition.
    Here, the electromechanical drive device 36 also drives the hydraulically drivable adjusting device 21, with the cylinder piston 25 being moved in the run-out direction 63 and the hydraulic fluid thereby flowing from the second hydraulic chamber 29 via the second chamber connection 55 and the second hydraulic pump section 54 to the hydraulic pump 56 in the hydraulic pump 56. and the third mechanically connected DC electric motor 170 is set in motion. The hydraulic fluid flows further from the hydraulic pump 56 via a second hydraulic section 171, a directional control valve 62, a check valve 60, and via the first hydraulic section 52 and the first hydraulic chamber closure 53 into the first hydraulic chamber 28. Hereby, an electric energy storage 172 can at least be heated up.
    In connection with the check valves 61 and 173, the hydraulic pressure bearing 59 ensures that the hydraulic fluid in the hydraulic line system 51 is biased by a slight overpressure, thereby preventing a lack of hydraulic fluid at the hydraulic pump 56, for example due to a cavity.
    Upon entry of the cylinder piston 25 towards the direction of exit 63, the hydraulic fluid flows from the first hydraulic chamber 28 via the first chamber closure 53, the directional control file 62, the additional hydraulic section 171, the hydraulic pump 56, the second hydraulic chamber section 54 and the second hydraulic chamber section 54 and the second hydraulic chamber section 54.
    In an emergency operating state, for example by powerless electric drive motor 37, the DC electric motor 170 driven by the electric energy storage device 172 so that the hydraulic pump 56 sucks hydraulic fluid from the second hydraulic chamber 29 and presses it through the first check valve 60 into the first hydraulic chamber 28 into the first hydraulic chamber 28. If this connection is coupled to its purchase statement 82B, the double chamber cylinder 22 is driven in this connection! it has reached its final destination. Hereby, the double-chamber hydraulic cylinder 22 retains its occupied position, since the first hydraulic chamber 28 is hydraulically sealed by means of the first check valve 60 and the directional control file 62.
    In this second embodiment, a direct current electric motor 170 is provided. Alternatively, this can also be designed as alternating current flow motor.
    In the embodiment shown in FIG. 4 as adjusting device 220 shown in the third embodiment, instead of an electromechanical drive device 36 (see Figures 1 and 2), an additional electrohydraulic drive device 275 is provided as the main new device 235 for a hydraulically drivable adjusting device 221 for adjusting pitch angle 8.
    The hydraulically drivable adjusting housing 221 is again configured as a double chambered hydraulic unit 222. The double chambered hydraulic cylinder 222 comprises a cylinder housing 223 in which a digit head support is provided. 225 is displaceably mounted along the longitudinal direction 224 of the double-chamber hydraulic cylinder 222. With the cylinder piston 225 also a partition 227 is displaceable, which subdivides a volume enclosed by the cylinder housing 223 into a first hydraulic chamber 228 and a second hydraulic chamber 229.
    As an emergency drive device 265, there is also an additional electro-hydraulic drive 250, the latter being further characterized by a hydraulic wiring system 251 for hydraulically connecting a hydraulic high pressure bearing 258, a hydraulic low pressure bearing 259, a hydraulic pump drive motor 257, a single pump 257 and a hydraulic pump 257. a directional control valve 262; The hydraulic line system 251 is hydraulically connected to a first hydraulic connection section 252 to a first hydraulic connection 253 to the first hydraulic chamber 228, and a second hydraulic connection section 254 is hydraulically connected to a second hydraulic connection 255 to the second hydraulic chamber 229.
    The additional electro-hydraulic drive 275 comprises an additional hydraulic clamping system 276 which is connected to a further first hydraulic connection 277 to the first hydraulic chamber 228. In addition, the second hydraulic seal system 276 is hydraulically connected to the second hydraulic chamber 229 by a further second hydraulic connection. drive device 275 an additional hydraulic pressure sensor 279, an additional hydraulic pump 280 driven by an additional hydraulic pump drive motor 281, an additional first non-return valve 282, a second second non-return valve 283 and a further third non-return valve 284 as well as an additional rectifier control valve 285.
    Thus, in connection with the main drive device 235 and the emergency drive device 265, there are two essentially independent electro-hydraulic drive devices 250 and 275.
    Prior to commissioning a 220 equipped wind energy egg 2 (sefig. 1) in operation in the downstream direction, the hydraulic high-pressure bearing 258 in the emergency drive device 265 is charged by the hydraulic pump 256. The directional control valve 262 is in that connection in a first directional control valve position 262A, the hydraulic pump 256 sucks from the hydraulic low-pressure bearing 259 the required hydraulic fluid and pumps it into the hydraulic high-pressure fluid storage 258. since an unintended avoidance of the hydraulic fluid therefrom is prevented by the first check file 260 and the directional control valve 262 located in the first directional control valve 262A,
    For an extension of the cylinder piston 225 in the run-out direction 263, the additional hydraulic pump driver 281 in the main drive device 235 is now activated, whereby the additional hydraulic pump 280 carries the hydraulic fluid via the additional directional control valve 285 and the second check valve cylinder 282 into the first hydraulic cylinder 222. In this way, hydraulic fluid also flows from the second hydraulic chamber 229 via the additional second hydraulic fluid outlet 278 to the additional hydraulic pump 280. The operation of the additional hydraulic fluid pressure carrier 279 and the second and third non-return valves 283 and 284 ensure that there is always a minimum pressure in the additional hydraulic conduit system 276, whereby a many! on hydraulic fluid, for example, due to cavitation, especially at the additional hydraulic pump 280, is avoided.
    For a run-in of the cylinder piston 225, the additional hydraulic pump 280 rotates in the opposite direction of rotation, whereby the hydraulic fluid is now actively fed to the second hydraulic pressure chamber 229, whereby hydraulic fluid flows from the first hydraulic chamber 228 via the further first hydraulic injection 277 via the further directional control 28. the additional hydraulic pump 280.
    In a state of emergency operation, for example, when the hydraulic pump drive motors 257 and 281 are powerless and not operational, the directional acid valve 262 is in a directional control valve 262B, in which the hydraulic fluid can flow from the hydraulic high-pressure carrier 26 through the sieve 26 through the directional storage 25 and via the first hydraulic seal section 252 into the first hydraulic chamber 228. Thereby the eyeliner piston 225 moves in the direction of exit 263 and hydraulic fluid is displaced out of the second hydraulic chamber 229 via the directional control valve 262 to the hydraulic low pressure storage 259. This process takes place until the cylinder piston 225 is fully extended. Cylinder piston 225 remains in this fully extended position as the two hydraulic chambers 228 and 229 are completely spaced apart. For the most part, the power effect of the double-chamber hydraulic cylinder 222, similar to that of hydraulic high-pressure bearing 258, remains hydraulic pressure, lasting respectively. at least long enough.
    In the FIG. 5, as the fourth embodiment example! shown further to the rotor head 1 of FIG. In adjusting device 320, an electro-hydraulic drive 350 is provided, in connection with which the hydraulically drivable adjusting device 321 is this time alternatively realized by a hydraulic rotary unit 390 with a hydraulic motor 391, with a rotor blade shaft fastening device 392 for fixing a rotor shaft 39 and 7 gear assembly 394.
    The electro-hydraulic drive 350 further comprises a hydraulic wiring system 351, electric hydraulic high pressure bearing 358, one hydraulic clamp pressure bearing 359, one hydraulic pump drive 357 driven hydraulic pump 356, a first check valve 360, a second check valve 361 and a third check valve 384. in 362, another directional control valve 364.
    Before a wind energy egg 2 equipped with the setting device 320 (see Fig. 1) takes up its operation, the hydraulic high pressure bearing 358 is charged. Hereby, the roiarvingeak.se !·· fixing device 392 is still active, so that an unintentional rotation of the rotor blade 7 is excluded, thereby resting the roering ring against its stop (not shown here). For charging the hydraulic high-pressure storage 358, a hydraulic fluid, via the hydraulic pump 356, is pumped into the hydraulic high-pressure storage 358 via the first check valve 360. The first directional control valve 362 is in this connection in its first directional control position 362A.
    In a normal operating condition of the adjusting device 320, the hydraulic pump 356 transports the hydraulic fluid via the first directional control valve 362 to the hydraulic motor 391, thereby rotating and thereby rotating the rotor vane 7. For this purpose, the first directional control valve 362 is still in the first purge control valve position 362A. The hydraulic fluid flowing out of the hydraulic motor 391 flows back to the hydraulic pump 356 via the conduit sections 395 and 396.
    In an emergency drift state, for example, when the hydraulic pump motor 357 is powerless and not operational, the directional control valve 362 is in a directional control valve position 362B and the second directional control valve 364 in another grease control valve 388B.
    The hydraulic fluid now flows from the hydraulic high pressure bearing 358 via the additional partial section 397 and via the first directional control valve 362 to the hydraulic motor 391, whereby the rotor vane 7 can be turned to an emergency running position. Upon reaching the emergency run position, the rotor blade shaft shaft assembly 392 is closed so that the rotor shaft 393 is fixed.
    By a suitable hydraulic coupling of additional hydraulic motor units 390 for additional rotor blades 7, an advantageous redundant arrangement may be provided.
    Advantageously, control of the above-described exemplary embodiments can also be provided with a wireless energy and signal transmission, so that a contactless electrical power transmission, especially from the nacelle insert 5 to the rotor hub 5, is advantageously rendered redundant.
    It is to be understood that, in connection with the above-described exemplary embodiments, these are merely first embodiments of the rotor head according to the invention. In so far as the embodiment of the invention does not limit itself to these embodiments! sese ksem pie r.
    All of the features set out in the application annexes are considered to be essential to the invention if they are individually or in combination new to the prior art.
    Here is a rotary head 2 rotor head 2 wind power plant 3 tower unit 4 vertical axis 5 nacelle bearing 6 rotor hub 7 rotor blades 8 pitch angle 9 pltch angle axis 20 enclosing device 21 hydraulically drivable adjusting device 22 double-chamber cylinder 23 cylinder housing 27 piston shaft 27 long axis 25 cyber housing u! in chamber 30 first end 35 main drive 36 electromechanical drive 37 electric drive motor 38 thread drive or thread drive (it could also be a planetary roller drive or a trapezoidal drive) 39 clutch 40 thread rod 41 bearing 42 housing 43 first guide rod 44 second guide rod 45 drive hub 46 48 second end 50 electric hydraulic drive 51 hydraulic ed sewing system m 52 first hydraulic section 53 first chamber connection 54 second hydraulic section 55 second chamber connection 56 hydraulic pump 57 hydraulic pump drive motor 58 hydraulic high pressure storage 59 hydraulic pressure layer
    60 first check valve
    61 second contraventi! 62 directional control valve 62A first directional latch valve 62B second tire control valve 63 exit direction 65 emergency power drive 170 direct current electric motor 171 double hydraulic section 22 piston rod 227 partition 228 first hydraulic chamber 229 second hydraulic chamber 235 main drive 250 electric hydraulic drive 251 hydraulic drive system 252 first hydraulic line section 253 first chamber connection 254 second hydraulic line section 255 second chamber connection 258 hydraulic pump drive 257 hydraulic pump 257 hydraulic pump 257 hydraulic pump 257 hydraulic pump 257 hydraulic pump 257 hydraulic pump 257 hydraulic pump 257 hydraulic pump 257 hydraulic pump 257 hydraulic pump 257
    262 retn i ng ssty fox ti I
    262A first directional control valve position 262B second directional control valve position 263 exit direction 265 emergency fluid drive device 275 additional electro-hydraulic drive device 276 additional hydraulic line system 277 additional first hydraulic connection 278 additional second hydraulic pivot 289 additional hydraulic throttle driver 280 additional hydraulic pump bearing 280 further hydraulic pump 283 additional second check valve 284 additional third check valve
    285 Additional Directional Revenue I
    320 indstiliingsindretning 321 hydraulically drivable adjustment device 350 eiektrohydraulisk driving device 351, the hydraulic conduit system 358, hydraulic pump 357 hydraulikpumpedrivmotor 358 hydraulic high pressure storage 359 hydraulic low pressure takes 360 first valve 361 second valve 362, directional control valve 362a first reiningsstyreventiistifiing 362b second directional control valve position 364 Andert directional control valve 364B second retningsstyreventiJstifling 384 third check valve 390 hydraulikmotorenbed 391 hydrauiikmotor 392 roiorvingeakselfastlæggelsesindreining 393 rotorvlngeaksel 394 gearbox 395 subcontractor section 396 second subcontractor section 397 additional subcontractor
    权利要求:
    Claims (10)
    [1]
    A rotor head (1) for a wind energy egg (2) with a rotor hub (6), with rotor blades (7) disposed thereon and with an adjustment direction (20; 120; 220; 320} for adjusting pite angles (8) for the rotor blades (7), wherein the adjusting device (20; 120; 220; 320} comprises a hydraulically drivable adjusting device (21; 221; 321}) to change the angle of rotation (8) of the rotor blades (7), characterized in that the adjusting device (20 ; 120; 220; 320} comprises an electro-hydraulic drive (50; 250, 275; 350) for hydraulically driving the hydraulically drivable adjusting device (21; 221; 321} for each rotor vane (7) an electromechanical driving device (36) for mechanically driving the hydraulically drivable adjusting device (21; 221; 321), wherein the driving devices (36, 50; 250, 275; 350) are arranged in the rotor hub (6).
    [2]
    Rotor head (1) according to claim 1, characterized in that the hydraulically actuable adjusting device (21; 221; 321) comprises a double-chamber cylinder (22; 222} or a hydraulic motor (391).
    [3]
    Rotor head (1) according to claim 1 or 2, characterized in that the electromechanical drive device {36} comprises a thread drive device (38) driven by means of an electric drive motor (37) directly mechanically mounted on a piston member! (25) in the hydraulic drive adjusting device (21).
    [4]
    Rotor head (1) according to claim 3, characterized in that the threaded drive device (38) is mechanically directly functionally connected to a sealing element (25) in a double chamber cylinder (22) in the hydraulically driven adjusting device (21).
    [5]
    Rotor head .. (- 1) according to any one of claims 1 to 4, characterized in that the electro-hydraulic drive device (50; 250 350) comprises a hydraulic high-pressure bearing (58; 258; 358) after a self-propelled additional electric motor, a DC electric motor (170).
    [6]
    Rotor head (1) according to any one of claims 1 or 2, characterized in that the adjusting device (20; 120; 220; 320) comprises more than one electro-hydraulic drive device (50; 250, 275; 350), each of the electro-hydraulic drive devices. (50; 250, 275; 350) with its own connections (53, 55; 253, 255, 277, 278) are hydraulically connected to the hydraulically drivable adjusting device (21; 221; 321).
    [7]
    7. Head (.. 1) according to claim 6. characterized in that one (50) of the electro-hydraulic drive means (50; 250, 275; 350) comprises a self-propelled additional electric motor, in particular a direct current electric motor (170).
    [8]
    Rotor head (1) according to any one of claims 1 to 4, characterized in that one (50; 275) of the electro-hydraulic drive housings (50; 250, 275; 350) merely comprises a hydraulic impression bearing (59; 279).
    [9]
    Rotor head (1) according to claim 1 or 2, characterized in that the electro-hydraulic drive device (320) comprises a hydraulic engine unit (390) with a hydraulic motor (391) with a locking device (392) for determining a rotor blade shaft (3939) gear assembly (394).
    [10]
    A wind energy system with a tower device (3) for providing a distance between a rotatable nacile device (5) and a support, rotatably mounted on the rotatable nacile device (5), characterized by a rotor head (1) according to any of the preceding claims.
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    同族专利:
    公开号 | 公开日
    DE102011121524A1|2013-06-20|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    BRPI0722189A2|2007-11-09|2014-04-08|Moog Inc|WIND TURBINE|DE102014013570A1|2014-09-18|2016-03-24|Conveni Gmbh|Stellsystem, wind turbine and method for aligning and / or tracking a nacelle and / or a rotor blade|
    法律状态:
    2015-07-20| PHB| Application deemed withdrawn due to non-payment or other reasons|Effective date: 20141231 |
    优先权:
    申请号 | 申请日 | 专利标题
    DE102011121524A|DE102011121524A1|2011-12-16|2011-12-16|Rotor head structure for wind-power plant, has electro-hydraulic drive device and electromechanical drive unit to hydraulically and mechanically drive hydraulically driven adjusting device changing angle of incidence at rotor blades|
    DE102011121524|2011-12-16|
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