Underwater turbine

Abstract

The invention relates to an underwater turbine (1) having a rotor hub (2) which is connected to a rotor main shaft (6) for conjoint rotation and is designed to drive the rotor main shaft (6), wherein the rotor main shaft (6) extends in a nacelle (8) connected to the rotor hub (2) via the rotor main shaft (6) and there drives a generator (10) received therein, wherein the rotor hub (2) is furthermore designed to support at least one rotor blade (4), wherein the at least one rotor blade (4) is secured to a rotor blade shaft (204) and wherein the rotor blade shaft (204) is rotatably supported on the rotor hub (2) and has a first rotor-hub-side end (208), which projects into an interior of the rotor hub (2), and a second sea-side end (207) which can be secured to the respective rotor blade (4) for conjoint rotation, wherein in each case the rotor-hub-side end (208) of the rotor blade shafts (204) is designed to interact with a rotor blade adjustment arrangement (300) in order to rotate the at least one rotor blade shaft (204), wherein the rotor blade adjustment arrangement (300) furthermore has a translationally movable push rod (332) which has a first rotor-hub-side end (334) which is designed to project into the rotor hub (2) of the underwater turbine (1) and has at least one connection device (340) which is designed to be connectable to the rotor blade shaft (204) in such a manner that the translational movement of the push rod (332) is converted into a rotational movement of the at least one rotor blade shaft (204), and wherein the push rod (332) has a second nacelle-side end (336) which is designed to extend in the direction of the nacelle (8) of the underwater turbine (1), wherein the rotor blade adjustment arrangement (330) furthermore has a locking device (480) which is designed to fix the push rod (332) in at least one predefined translational position.

Description

[0001] Description

[0002] underwater turbine

[0003] Technical area

[0004] The present invention relates to an underwater turbine according to the preamble of claim 1.

[0005] Technical background

[0006] Underwater turbine rotor blades are typically attached to a rotor hub and can be mounted so they can rotate relative to the rotor hub. By rotating the rotor blades, the drive power can be varied. Furthermore, the rotor blade pitch system rotates the rotor blades in such a way that no torque is transferred from the rotor blades to the rotor hub, allowing the turbine to come to a complete standstill. In some designs, the blade pitch system is used to adapt to changing water flow directions without having to rotate the entire underwater turbine.

[0007] For this purpose, a drive unit is provided on the rotor blades or on the rotor blade shafts, which allows the rotor blades to be rotated.

[0008] However, such drive units are relatively bulky and therefore require a lot of installation space, which is not available, especially in smaller systems.

[0009] It is therefore an object of the present invention to provide a rotor hub arrangement which enables blade adjustment even in smaller underwater turbines.

[0010] Summary of the invention This object is achieved by an underwater turbine according to claim 1.

[0011] The following describes an underwater turbine comprising a rotor hub designed to drive a rotor main shaft. The rotor main shaft extends into a nacelle connected to the rotor hub via the rotor main shaft, where it drives a generator housed therein. The rotor main shaft can be non-rotatably attached to the rotor hub using fastening means, such as screws.

[0012] Furthermore, the rotor hub is designed to carry at least one rotor blade, wherein the rotor blade is fastened to a rotor blade shaft and wherein the rotor blade shaft is rotatably mounted on the rotor hub and has a first rotor hub-side end which projects into an interior of the rotor hub, and a second sea-side end which can be fastened in a rotationally fixed manner to the respective rotor blade, wherein the rotor hub-side end of the rotor blade shafts is in each case designed to cooperate with a rotor blade adjustment arrangement in order to rotate the at least one rotor blade shaft.

[0013] In order to provide a rotor blade adjustment arrangement even in smaller underwater turbines which have little installation space available, the rotor blade adjustment arrangement itself has a translationally movable push rod which has a first rotor hub-side end which is designed to protrude into the rotor hub of the underwater turbine and has at least one connecting device which is designed to be connectable to the rotor blade shaft in such a way that the translational movement of the push rod is converted into a rotational movement of the at least one rotor blade shaft, and wherein the push rod has a second nacelle-side end which is designed to extend in the direction of the nacelle of the underwater turbine.

[0014] In order to avoid having to expend unnecessary energy to hold the rotor blades in a certain position or to ensure, for example, in the event of a power failure or malfunction that the underwater turbine is automatically shut down, it is further proposed that the underwater turbine further comprise a locking device which is designed to fix the push rod in at least one predetermined translational position. This allows the rotor blades to be fixed in a certain position, for example a feathered position, in which no torque can be exerted on the rotor blades by the current. During maintenance work, or if, for example, a power supply for adjusting the rotor blades fails, it is advantageous if the entire underwater turbine is shut down. It is therefore particularly preferred to use a locking device which is pretensioned into the feathered position.

[0015] According to a preferred embodiment, the locking device comprises at least one adjustable locking element that interacts with the push rod or a component of the linear drive that moves the push rod translationally to fix the push rod in its translational position. Since the push rod extends through almost the entire underwater turbine, a locking device can be provided in many locations where installation space is available. Thus, a locking device can also be provided in compact underwater turbines.

[0016] It is particularly advantageous if the push rod has at least one recess on its outer surface, which is designed to interact with the locking element. This allows the locking element to act directly on the push rod.

[0017] According to a further preferred embodiment, a locking element of the at least one locking element is arranged on the rotor main shaft.

[0018] Alternatively or additionally, a locking element of the at least one locking element is arranged on a linear drive housing surrounding the linear drive or on the linear drive itself. Preferably, the linear drive housing is mounted in a rotationally fixed manner on the main rotor shaft.

[0019] Depending on the design of the underwater turbine, one or more locking elements can be provided, which can also be arranged at different locations. This allows for optimal use of the available installation space.

[0020] The non-rotatable connection of the linear drive housing to the main rotor shaft ensures that the force required to adjust the rotor blades can be supported directly on the main rotor shaft instead of on the nacelle. This eliminates the need to design the bearing units that support the main rotor shaft in the nacelle to absorb this force, which would be necessary if the linear drive were supported on the nacelle. This allows the bearing units of the main rotor shaft bearing to be smaller and optimized solely for the task of supporting the main rotor shafts.

[0021] According to a further preferred embodiment, the linear drive further comprises a piston that acts translationally on the push rod, having a rotor hub-side end with which it acts on the push rod, and a nacelle-side end that is subjected to force by the linear drive. Furthermore, the nacelle-side end of the push rod and the rotor hub-side end of the piston are accommodated in a push rod-piston connecting housing that is translationally displaceable within the linear drive housing.

[0022] This allows a particularly simple coupling between the push rod and the piston to be created, which enables the translational force of the piston to be directly applied to the push rod.

[0023] The linear drive is preferably a hydraulic or pneumatic linear drive, and the piston can be moved translationally by means of a hydraulic or pneumatic working fluid. This allows a large force to be exerted on the push rod, which can ensure adjustment of the rotor blades even against the high water pressure acting on the rotor blades.

[0024] In order to enable adjustment of the piston in a hydraulic or pneumatic linear drive, it is further preferred that the piston is accommodated in a piston housing which surrounds the piston and is designed to define at least a first working chamber for the piston, wherein when the first working chamber is acted upon by a working fluid, the piston acts on the push rod in such a way that the push rod can be moved from a first to a second position.

[0025] The first position can be a so-called feathered position of the rotor blades, i.e., the position in which no torque is transmitted by the rotor blades. In other words, the rotor blades are turned out of the flow. Preloading the rotor blades to the first position advantageously ensures that in the event of a power failure or a problem with the hydraulic or pneumatic linear drive, e.g., a pump malfunction, the underwater turbine is shut down, allowing maintenance or repair work to be carried out.

[0026] Furthermore, a return element, in particular a spring, can be provided on the piston, which is designed to preload the piston into the first position.

[0027] Alternatively or additionally, the piston housing is further designed to define a second working chamber, whereby when the second working chamber is pressurized with a working fluid, the piston can be moved into the first position. This also allows the rotor blades to be actively rotated from the second position to the first position. Furthermore, this dual action of the piston enables any intermediate position between the first and second positions to be actively controlled. The spring can also be viewed as a support element for returning to the first position.

[0028] Preferably, the piston is arranged in the piston housing in such a way that the piston essentially only performs a translational movement with respect to the piston housing.

[0029] According to a further preferred embodiment, the linear drive housing is non-rotatably connected to the main rotor shaft and at least partially surrounds the piston housing. The piston housing is non-rotatably supported in the nacelle, with a first rotationally decoupling bearing unit arranged between the linear drive housing and the piston housing. This enables relatively simple use of a hydraulic or pneumatic linear drive, since no rotary feedthrough for the hydraulic fluid or compressed air needs to be provided. Furthermore, with this configuration, the force exerted by the hydraulic or pneumatic drive can be supported on the main rotor shaft via the linear drive housing.

[0030] According to a further advantageous embodiment, the piston is non-rotatably connected to the push rod-piston connecting housing, and the nacelle-side end of the push rod is rotatably mounted in the push rod-piston connecting housing by means of a second rotationally decoupling bearing unit. This means that the push rod-piston connecting housing itself is only translationally movable and essentially does not rotate, since the piston itself is only translationally movable.

[0031] Alternatively, the nacelle-side end of the push rod can be non-rotatably connected to the push rod-piston connecting housing, in which case the piston is rotatably mounted in the push rod-piston connecting housing by means of a second rotationally decoupling bearing unit. This means that the push rod-piston connecting housing itself rotates together with the push rod, while the piston remains stationary.

[0032] Both designs allow for direct force transmission between the push rod and the piston, while simultaneously allowing the use of a piston that can only be moved in a translational manner.

[0033] If the nacelle-side end of the push rod is connected to the push rod-piston connecting housing in a rotationally fixed manner, and the piston is rotatably mounted in the push rod-piston connecting housing by means of a second rotationally decoupling bearing unit, it is advantageous if the locking device has at least one blocking element that interacts with the push rod-piston connecting housing. Since the linear drive housing and thus also the push rod-piston connecting housing are accommodated in the nacelle, they are relatively easily accessible, so that the locking device can be integrated into the underwater turbine without requiring additional installation space. The action of the blocking element on the push rod-piston connecting housing can directly prevent the push rod-piston connecting housing and thus the push rod from translational movement.

[0034] If, however, the rotor hub end of the piston is connected to the push rod-piston connecting housing in a rotationally fixed manner, and the nacelle end of the push rod is rotatably mounted in the push rod-piston connecting housing by means of a second rotationally decoupling bearing unit, it is advantageous if the locking device on the linear drive is arranged, for example, on a piston housing that defines at least one working space for the piston and has at least one locking element that interacts with the piston. If a locking element were to act between a rotating linear drive housing and a rotationally fixed piston, the locking device would have to be designed such that it locks reliably even under shear loads.

[0035] According to a further preferred embodiment, the locking device is designed to fix the push rod at several translational positions.

[0036] As mentioned above, one of the translational positions can be the feathering position of the rotor blades. It is particularly preferred if the locking device and / or the linear drive device is designed such that, in the event of a malfunction or power failure, the locking device fixes the push rod in its first position, which corresponds to the feathering position of the rotor blades.

[0037] Furthermore, it is preferred if a second translational fixing position of the push rod corresponds to a rotor blade position that enables maximum rotational force transfer from the flow to the rotor blade. This ensures that the rotor blades remain rotated against the flow, even when the rotor blade adjustment assembly is not actively supplied with power. This enables particularly energy-efficient operation of the underwater turbine.

[0038] Alternatively or additionally, it can also be provided that a third translational fixing position of the push rod of a rotor blade position is provided, which enables a defined, reduced rotational force transmission of the flow to the rotor blade. This can, for example, put the underwater turbine into emergency operation, in which electricity is produced, but no excessive load occurs on the rotor blades. This can be the case, for example, in the case of an excessively increased water flow caused by a storm. It is particularly advantageous if the reduced

[0039] Rotational force transmission 50% to 90%, in particular 60% to 80%, preferably 70%, corresponds to a maximum rotational force transmission of the flow to the rotor blade.

[0040] According to a further preferred embodiment, the locking device has at least one locking element that can be actuated by a hydraulic or electromechanical actuator. This allows the locking element to be easily moved into and released from a locking position. It can also be advantageous if the locking element is preloaded into its locking position, for example, by means of a spring element.

[0041] Further advantages and advantageous embodiments are set forth in the description, the drawings, and the claims. In particular, the combinations of features set forth in the description and the drawings are purely exemplary, so the features may also be present individually or in other combinations.

[0042] Short character description

[0043] The invention will be described in more detail below with reference to exemplary embodiments illustrated in the drawings. The exemplary embodiments and the combinations shown in the exemplary embodiments are purely exemplary and are not intended to define the scope of the invention. This scope is defined solely by the appended claims.

[0044] There show: Fig. 1 to Fig. 23: schematic sectional views of various different preferred embodiments for an underwater turbine.

[0045] Detailed description of the invention

[0046] In the following, identical or functionally equivalent elements are identified by the same reference symbols.

[0047] Figure 1 shows a schematic sectional view of an underwater turbine 1. The underwater turbine 1 comprises, as its main components, a rotor hub 2, which is designed to mount and support rotor blades 4, and a rotor main shaft 6 which is rigidly connected to the rotor hub 2 and extends into a nacelle 8 in which a generator 10 for generating electricity is accommodated. The rotor main shaft 6 can be fastened to the rotor hub 2, for example, by means of fastening means, in particular screws 5. The rotor blades 4 are subjected to a water flow, thereby causing the rotor hub 2 to rotate. The rotationally fixed connection of the rotor hub 2 to the rotor main shaft 6 in turn drives a rotor 12 of the generator 10, which is rotationally fixedly connected to the rotor main shaft 6.The rotor 12 can be attached directly to the main rotor shaft 6, but it is also possible for a gearbox (not shown) to be arranged between the main rotor shaft 6 and the generator 10, which converts the slow rotation of the main rotor shaft 6 into a fast rotation for power generation. The main rotor shaft 4, in turn, is rotatably mounted in the nacelle 8 by means of bearing units 14, 16. The bearing units 14, 16 are particularly designed to accommodate axial and radial loads. For example, the main rotor shaft 6 can be mounted on axial and radial bearing units.

[0048] The rotor blades 4 are preferably also mounted so that they can be adapted to the respective flow direction without having to rotate the entire nacelle 8. Furthermore, the adjustment of the rotor blades 4 also allows the rotor blades 4 to be rotated into the so-called feathered position, in which the flow does not cause the rotor hub 2 to rotate. This allows the underwater turbine 1 to be shut down entirely.

[0049] The rotor blades 4 themselves are typically arranged symmetrically to one another and, in the case of two rotor blades 4-1, 4-2, are arranged directly opposite one another. With more than two rotor blades, such as three or four rotor blades 4, these can be arranged at a distance of 120° or 90° from one another.

[0050] In the embodiments shown in Figures 1 to 23, a two-bladed rotor is shown which has two opposing rotor blades 4-1; 4-2.

[0051] Furthermore, Figures 2 to 23 show various details and embodiments of the underwater turbine 1. In particular, Figures 2 to 5 show various basic designs of a rotor hub assembly 200. The rotor hub assembly 200 typically comprises a rotor hub housing 202 into which a rotor blade shaft 204 is inserted.

[0052] The rotor blade shaft 204, in turn, is designed to be connected to the actual rotor blades 4 (see Fig. 1) and can be constructed in one piece or in multiple pieces. It is also possible for the rotor blade shaft to be designed as a shaft stub. The two-part design, namely rotor blade 4 and rotor blade shaft 204, allows the rotor hub assembly 200 to be transported pre-assembled, with the rotor blades only being connected to the rotor hub assembly 200, and more precisely to the rotor blade shaft 204, at the site of use. In some embodiments, it is even possible to mount the rotor blades on the rotor blade shaft underwater. For this purpose, it is particularly advantageous if a rotor hub interior 210 is sealed off from the water into which the underwater turbine is installed.

[0053] In the two-bladed rotor shown in Figs. 2 to 5, the rotor blade shafts 204-1, 204-2 each have a seaward end 207 and a rotor hub end 208. The seaward end 206 is designed to be connected to the actual rotor blades 4, while the rotor hub end 208 projects into an interior space 210 of the rotor hub assembly 200 and is designed to be connected to a preferably central rotor blade twisting device 300. To enable twisting of the rotor blades or the rotor blade hubs 204, the rotor blade shafts 204 are rotatably mounted relative to the housing 202 of the rotor hub 2 by means of a rotor blade bearing assembly 214.

[0054] The rotor blade shafts 204 themselves define a length L of the rotor blade shaft 204 between their seawater-side end 207 and their rotor hub-side end 208. The two rotor hub-side ends 208-1 and 208-2 and the two seawater-side ends 207-1, 207-2 are in turn spaced apart by a distance X and Y, respectively. If more than two rotor blades are present, the rotor hub-side ends 207 and the seawater-side ends 208 each lie on a circle with a diameter X and Y, respectively.

[0055] The rotor blade bearing assembly 214 further comprises a first offshore bearing unit 220 and a second rotor hub-side bearing unit 230. The bearing units 220 and 230 can be designed as rolling bearing units 221, 231, as shown in Figures 2 to 5. However, it is also possible, as shown in Figures 6 to 8, to design the bearing units 214 as plain bearing units 225; 235.

[0056] If the bearing units 220; 230 are designed as rolling bearings 221; 231, they each have an inner ring 222; 232 and an outer ring 223; 233, which define a bearing interior between them in which rolling elements 224; 234 are arranged. The rolling elements 224; 234 can optionally be guided in a rolling bearing cage (not shown). If the bearing units 220; 230 are designed as plain bearings 225; 235, plain bearing bushings 226; 236 can be provided, which ensure particularly good plain bearing support.

[0057] The bearing inner rings 222; 232, more precisely an inner bore 227, 237 of the bearing inner rings 222;

[0058] 232, or the plain bearing bushings 226; 236 each have an inner diameter d11, d21 dimensioned such that the bearing inner rings 222, 232 or the plain bearing bushings 226; 236 can be connected in a rotationally fixed manner to the respective rotor blade shaft 204. The inner diameters d11, d21 are typically dimensioned such that they overlap with an outer diameter of the rotor blade shaft 204, so that the bearing inner rings 222, 232 or the plain bearing bushings 226; 236 can be fastened to the rotor blade shaft 204 with a press fit.

[0059] The bearing outer rings 223, 233 are non-rotatably mounted on a rotor hub housing section 252; 262. The rotor hub housing section 252 can be designed as an integral component of the rotor hub housing 202 (see, for example, Figs. 2 and 3), but it is also possible for the rotor hub housing section 262 to be a separate housing section that is connected to the rotor hub housing by means of fastening means 264 (see, for example, Figs. 4 and 5).

[0060] Of course, it is equally possible to connect the plain bearing bushes 226; 236 to the rotor hub housing section 252; 262 in a rotationally fixed manner, preferably by pressing them into the rotor hub housing section 252; 262.

[0061] For the rotationally fixed connection, an inner diameter of the rotor hub housing section 252, 262 is usually dimensioned such that it has an overlap with an outer diameter of the bearing outer rings 223, 233 or the plain bearing bushes 226; 236, so that the bearing outer rings 223, 233 or the plain bearing bushes 226; 236 can be fastened with a press fit in the rotor hub housing section 252; 262.

[0062] Furthermore, the rotor hub assembly 200 has a preferably dynamic seawater sealing arrangement 240, which is designed to seal a gap 242 between the rotor blade shaft 204 and the housing 202 to prevent water from entering the interior of the rotor hub 2. In order to achieve ideal tilting rigidity and thus high load-bearing capacity, and at the same time to compensate for the effects of thermal differences in the rotor blade bearing assembly 214, the first bearing unit 220 and the second bearing unit 230 are spaced apart from one another at a specific bearing distance W, each measured from the center of the bearing unit (see Figs. 2, 3 and 6, 7). The bearing distance W is set in relation to the inner diameter dli of the inner bore 227 of the offshore bearing unit 220, so that 0.8*dli < W < 2*dli, preferably l*dli < W < l.5*dli.

[0063] This also makes it possible to compensate for the possible thermal growth of the rotor blade shaft 204, as well as the ring growth of the warm bearing inner rings 222 compared to the cooler bearing outer rings 223, in rolling bearings 221; 231, especially in tapered roller bearings, which ensures jam-free operation of the bearing units 220, 230. Furthermore, this also makes it possible to counteract a loss of preload in the bearing arrangement—provided the bearing units 220, 230 are installed with a preload, as is common, for example, with tapered roller bearings.

[0064] The special spaced arrangement of the bearing units 220, 230 further allows the rotor blade shaft 204 to be longer and thus extend further into the interior 210 of the rotor hub 2. Furthermore, the diameter of the rotor blade shaft 204 can be reduced, as the forces exerted by the rotor blade 4 on the rotor blade shaft 204 and on the bearings 220, 230 are distributed over a longer distance. The smaller shaft diameter, in turn, allows the seawater-side seal assemblies 240, which seal the rotor hub, to also have a smaller diameter. This reduces the relative movement of the seals, which contributes to the overall slower wear of the seals.

[0065] It is particularly preferred that a length L of the rotor blade shaft 204 is adapted such that a distance X of the rotor hub-side ends 208-1, 208-2 of two opposing rotor blade shafts 204-1, 204-2 and a distance of the seawater-side ends 207-1, 207-2 of the opposing rotor blade shafts 204-1, 204-2 (or alternatively the diameters X, Y of the circles described by the corresponding ends 208 and 207, respectively) satisfy the following relationship: X: Y ≡ 6: 1. This enables a short distance between the rotor blade shafts 204-1, 204-2 and a relatively large rotor blade spacing.

[0066] Fig. 9 further shows that the rotor hub housing 202 has rib structures 250 which structurally reinforce the housing 202 and make it possible to provide a relatively thin-walled housing 202 which, however, can withstand high loads, in particular high water pressure at greater depths.

[0067] As can be seen in particular from Figs. 2 to 6, the bearing units are arranged such that they form an O-arrangement, wherein the O-arrangement is designed such that a force flow can be absorbed by the rib structures 250 arranged in the housing 202 and transmitted to the rotor main shaft 6. This is possible both with rolling bearing units, in particular tapered roller bearings, and with a corresponding plain bearing design (see Fig. 6).

[0068] Furthermore, Figures 2, 3 and 6 to 8 show that the rotor blade shaft 204 can be inserted into the rotor hub housing 202 together with the bearing units 220 and 230, wherein the rotor hub housing 202 in this embodiment has the rotor hub housing section 252 which is formed integrally with the rotor hub housing and extends inwardly in a tubular manner and which can be designed as a bearing seat for the outer rings 223; 233 or as a sliding surface or seat for the plain bearing bushes 226; 236.

[0069] Alternatively, however, the rotor blade shaft 204 and the bearing units 220 and 230 can also be designed as a module 260, which can be inserted in its entirety into the rotor hub housing 202 (see in particular Figures 4 and 5). For this purpose, the module 260 further comprises the separate rotor hub housing section 262, which is also tubular and is referred to below as the module housing section 262 and is designed as a bearing seat for the outer rings 223; 233 or as a sliding surface or seat for the plain bearing bushes 226; 236 for the bearing units 220 and 230, respectively. The tubular module housing section 262 can be fastened to the housing 202 of the rotor hub assembly by means of fastening elements 264. The design as module 260 has the advantage that the bearing units 220 and 230 can be provided fully assembled and, if necessary, preloaded and only need to be inserted into the housing.Furthermore, in this case, the seawater seal 240 can already be attached to the module 260, so that the assembly steps when assembling the module 260 into the rotor hub housing 202 can be significantly simplified.

[0070] Tapered roller bearings are particularly suitable as bearing units 220; 230, since they can absorb high external loads, especially bending moments, in an O-arrangement and enable a continuous force introduction into the main rotor shaft 6. This also allows the bearings to be dimensioned smaller overall.

[0071] Alternatively, Figures 6 to 8 show the above-mentioned plain bearing of the rotor blade shaft 204. Figures 6 to 8 show a rotor shaft 204 that is inserted into the housing 202 of the rotor hub 2, with a sliding pairing being formed between the tubular housing section 252 of the raw hub housing 202, or the module housing section 262, and the rotor blade shaft 204, which pairing each forms a first offshore sliding surface pairing 280 and a rotor hub-side sliding surface pairing 290. Figures 6 to 8 only show the integrated design with a housing section 252 and not the modular design. However, the following statements apply analogously.

[0072] To form the rotor hub-side sliding surface pairing 280 or the seawater-side sliding surface pairing 290 with outer sliding surfaces 281; 291 and inner sliding surfaces 282, 292, the housing section 252 has, in particular, a first rotor hub-side section 254 and a second seaside section 255, which are designed as outer sliding surfaces 281, 291. In this exemplary embodiment, the inner sliding surfaces 282; 292 are formed by the plain bearing bushes 226; 236. The inner and outer sliding surfaces 281, 291, 282, 292 are designed as radial sliding surfaces that serve to radially support the rotor blade shaft 204 with respect to the rotor hub housing section 252.

[0073] Analogously, an outer surface 203 of the rotor blade shaft 204 can serve as counter sliding surfaces. Fig. 8 illustrates such an embodiment, in which the plain bearing bushes 226, 236 are pressed into the rotor hub housing section 252 and the rotor blade shaft 204 has a first surface section 203-1 and a second surface section 203-2, which are designed as inner sliding surfaces 282, 292. Additionally, axial sliding surfaces 283, 293 (outer); 284, 294 (inner) can also be provided. The axial sliding surfaces 283, 293; 284, 294 enable, for example, the rotor blade shaft 204 to be provided at its seaward end 207 with a stop surface 206 which cooperates with a corresponding counter-stop surface 256 on the rotor hub housing section 252 in order to define a defined insertion position of the rotor blade shaft 204 into the rotor hub housing 202.The outer axial sliding surface 293 is then formed on the stop surface 206, while the inner axial sliding surface 294 is formed on the counter stop surface 256 of the rotor hub housing section 252.

[0074] Analogously, an axial plain bearing can also be formed on the rotor hub-side end 208 of the rotor blade shaft 204 or the rotor hub-side end 254 of the rotor hub housing section 252. In the illustrated embodiments in Figs. 7 and 8, a stop surface 257 is also formed on the rotor hub side of the rotor hub housing section 252, which is designed as an outer axial sliding surface 283 for the rotor hub-side plain bearing 235. A shaft nut 246, which is equipped with an inner sliding surface 284, can cooperate with this sliding surface 283, for example. The shaft nut 246 serves, for example, to secure the rotor blade shaft 204 in the rotor hub housing 202.

[0075] Instead of the plain bearing bushings 226; 236 shown in the figures, the corresponding sliding surfaces 281, 291; 282, 292; 283; 293; 284; 294 can also be provided with a sliding coating, for example made of a fiber composite material, to avoid a steel-on-steel sliding pair. The plain bearing bushing 226; 236 can also be made of a fiber composite material. Such a fiber composite material preferably comprises a sliding fiber and / or a plastic matrix made of a lubricious material, such as PTFE.

[0076] In the embodiments shown in Figures 6 and 7, plain bearing bushes 226; 236 are used, which are non-rotatably attached to the rotor blade shaft 204, while in Figure 8 the plain bearing bushes are pressed into the rotor hub housing section 252.

[0077] Fig. 6 shows an embodiment in which, analogous to an O-arrangement of a tapered roller bearing, tapered plain bearing bushes are used, which are also arranged in an O-arrangement. The rotor blade shaft 204 can have a tapered plain bearing bush receiving surface (or sliding surface) 205; however, it is also possible for an additional bearing element, such as an inner ring 286, to be arranged on the rotor blade shaft 204. This bearing element supports the tapered plain bearing bush 236 or serves as a sliding surface for the tapered plain bearing bush. The angle of attack of the tapered plain bearing arrangement is again selected such that force can be introduced into the reinforcing ribs 250.

[0078] The plain bearing bushings 226, 236 can also form cylindrical sliding surfaces, as shown in Fig. 7 and Fig. 8. Furthermore, Fig. 7 and 8 show that the plain bearing bushings 226; 236 have a cylindrical sleeve portion 228; 238 serving as a radial bearing, with the aid of which the radial sliding surfaces 281, 291; 282, 292 are formed, and a flange portion 229, 239 serving as an axial bearing, with the aid of which the axial sliding surfaces 283, 293, 284, 294 are formed.

[0079] According to a further preferred embodiment, the plain bearing is also fluid-lubricated, in particular water-lubricated. For this purpose, the entire interior 210 of the rotor hub 2 can preferably be flooded with a fluid, so that not only the plain bearing bushings 226; 236, as shown in Figures 6 to 8, are lubricated with the fluid, but also other bearing units arranged in the rotor hub interior 210. The fluid can be water, in particular deionized and demineralized water, which, compared to seawater, has corrosion-reducing properties, or a fluid that has a density similar to water.

[0080] If water is used as the fluid, the seawater seal 240, which completely seals the gap 242 between the rotor housing 202 and the rotor blade shaft 204, can be omitted and only a simple seal 244 with a dirt retention function can be provided (see Fig. 7). Since the same pressure prevails both in the rotor housing interior 210 and in the surrounding medium, this seal 244 is not subjected to significant stress and merely retains dirt particles that could endanger the plain bearing pairing between the rotor housing 202 and the rotor blade shaft 204.

[0081] With such a fluid-lubricated bearing, sealing devices at the rotor hub-side end 208 of the rotor blade shaft 204 can also be dispensed with. Typically, an interior space of both the rotor blade shaft 204 and the rotor blade 4 is filled with water to prevent floating or buoyancy due to trapped air. As a result, the rotor blade shaft 204, as shown in particular in Figure 8, can be designed entirely as a hollow shaft, which is closed, for example, only by means of crank disks. Of course, it is also possible to design the rotor blade shaft 204 not entirely as a hollow shaft, as shown in Figures 6 and 7.

[0082] Furthermore, the embodiments of Figures 2, 4, and 10 to 13 show that a bevel gear drive 310 is used as the central rotor blade rotation device 300 for adjusting the rotor blade shafts 204. For adjustment using a bevel gear drive 310, in the illustrated embodiments, a bevel gear 312-1 or 312-2 is attached to the rotor blade shaft 204 at the rotor hub end 208, which mesh with a central bevel gear 314. The central bevel gear 314 is in turn driven by a drive unit 316 or an electric motor and enables adjustment of the rotor blades by 360°. This solution is possible both with a modular design as shown in Figure 4 and with the rotor blade shaft being installed in the housing 202 itself (see Figures 2 and 10 to 13). The electric motor 316 can be designed compactly and in the interior 210 and rotor hub 2 (see Fig. 11) or in the rotor main shaft 6 designed as a hollow shaft (see Fig.12) may be arranged.

[0083] In the embodiment shown in Fig. 11, the drive motor 316 is compact and can therefore transmit the required torque directly. To provide the required torque to the rotor blade shaft 204, a gear is arranged between the bevel gear 312 and the rotor blade shaft 204 in the embodiment shown.

[0084] 317. The bevel gears 312-1, 312-2 are connected to a transmission input shaft

[0085] 318. The speed is reduced and the torque increased via a gear ratio 319. The rotor blade shaft is non-rotatably mounted on the gearbox output side. The gearbox 317 is preferably designed with one or more planetary stages.

[0086] However, if the electric motor 316 is structurally relatively bulky, it may further be provided to provide an additional housing section 272 on the housing 202 of the rotor hub assembly 200, which is designed to accommodate the electric motor 316. In order not to impair the streamlining of the underwater turbine 1 in this case or to improve the flow to the rotor blades 4, a so-called spinner 274 may be attached to the housing section 272 (see in particular Figs. 2, 10 and 13).

[0087] Instead of an electric motor 316, the housing section 272 can of course also accommodate other types of drive units.

[0088] Furthermore, in particular, Figs. 4, 10, and 12 show that the main rotor shaft 6 is hollow and that cables 270 can be passed through it, which can be used to control the electric motor 316. Furthermore, Figs. 2, 4, and 10 to 13 show that the rotor blade shafts 204 can also have a bore 209 through which cables 270 can be passed, for example, to supply current to sensors (not shown) and to transmit signals that detect, for example, a deformation of the rotor blades 4 and / or a load acting on the rotor blades 4.

[0089] Since the rotor blades do not need to constantly move to new positions, and it is sometimes useful to move the rotor blades into a so-called feathered position and hold them there, in which no torque can be transmitted from the water flow to the rotor blades, e.g., for maintenance purposes, it is also useful to provide a locking device 320 that fixes the rotor blades in a specific position. For this purpose, as shown in Figure 13, a locking device 320 can be provided that is non-rotatably attached to the rotor hub housing 202. This locking device also has a bevel gear 322 that can be engaged with the bevel gears 312-1 and 312-2 by means of actuating elements 324 to prevent them from rotating further. If the locking bevel gear 322 is in engagement with the bevel gears 312, the drive unit 316 can be de-energized and does not have to constantly hold the bevel gears 312 and thus the respective rotor blade shafts 204 in their position.This is also advantageous in terms of energy. Furthermore, the locking device 320 can be designed such that, in the event of a power failure, the locking bevel gear 322 only engages with the bevel gears 312 when the rotor blades 4 move into the feathered position due to the water flow and because no force is rotating the rotor blades into the water flow. The locking device 320 then ensures that further rotation of the rotor blades 4 is not possible. Instead of a bevel gear arrangement, a push rod arrangement 330 can also be used as the central rotor blade rotation device 300.

[0090] Figures 3, 5, and 14 to 23 show, as an alternative central rotor blade twisting device 300, the push rod assembly 330 with a push rod 332 that is axially movable and cooperates with the rotor blade shaft 204 to twist it. The push rod 332 typically has a first rotor hub-side end 334 and a second opposite end 336, and extends through a bore 60 in the main rotor shaft 6. This bore can be sealed by means of a seal 374 (see Fig. 17) in the case of a flooded rotor hub.

[0091] The push rod 332 is moved axially by means of a linear drive 400, whereby the linear drive 400 can interact directly with the push rod (see Figs. 14 and 15), but can also act indirectly on the push rod as a separate component (see Fig. 16).

[0092] As can be seen in particular from Figures 17 and 18, the push rod 332 is connected to the rotor hub end 208 of the rotor blade shaft 204 by means of a connecting device 340.

[0093] The connecting device 340 has one connecting rod 342 per rotor blade shaft 204. Each connecting rod 342 comprises a connecting rod 344, at the ends 346; 348 of which an eye 350; 352 is formed. The eyes 350; 352 serve as plain bearings for bolts 354; 356, which ensure a rotatable attachment of the connecting rod 342.

[0094] The connecting rod 342 is rotatably connected at its first end 346 by means of the bolts 354 to a connecting rod-push rod connecting element, in particular a connecting rod holder 358, which in turn is non-rotatably attached to the push rod 332.

[0095] On the second side 348, the respective connecting rods 342-1, 342-2 are rotatably attached to the connecting rod-rotor blade shaft connecting element, for example, crank disks 360-1, 360-2, by means of bolts 356, wherein each crank disk 360 is in turn connected in a rotationally fixed manner to the corresponding rotor blade shaft 204, wherein, for example, fastening elements 362 can be used. The sectional view of Fig. 8 shows in particular a further embodiment of the connecting rod-rotor blade shaft connection, wherein here too a crank disk 360 is used, which is fastened to the rotor blade shaft 204 with fastening elements 362. Furthermore, it can be seen from this exemplary embodiment that the connecting rods 342-1, 342-2 each have a spherical bearing unit 380-1, 380-2 in their second connecting rod eyes 352, which in the illustrated exemplary embodiment is designed as a spherical plain bearing.The spherical bearing unit 380, in turn, has an outer ring 381 and an inner ring 382, ​​which are arranged slidingly against one another. The spherical plain bearing 380 can be pressed into the connecting rod eye 352, for example, with the aid of a bolt 384 that supports the bearing, and connected to the crank disk 360.

[0096] Furthermore, it can be seen in Fig. 8 that an O-ring 390 can be inserted as a seal between the crank disk 360 and the rotor blade shaft 204, which, for example, seals a flooded rotor blade shaft against a dry rotor hub interior.

[0097] If the push rod is moved axially, as shown in Figures 18, A, B, and C, the rotor blade shaft 204 can be rotated from a first maximum position I (see Figure 11A) to a second maximum position II (see Figure 11C). In the center position shown in Figure 11B, the connecting rod 342 is at its maximum angle. Furthermore, it is preferred that the first maximum position I corresponds to a feathered position, and the second maximum position II corresponds to a maximum force absorption position of the rotor blades 4 in the water flow.

[0098] Furthermore, it is preferred that the push rod 332 is pre-tensioned into the vane position I, so that only when the push rod 332 is actively moved is the rotor blade 4 moved into a position in which the water flow exerts a torque on the rotor blades 4.

[0099] The push rod 332 can, as shown in Figures 15 to 23, be accommodated in the rotor main shaft 6, which is designed as a hollow shaft. However, it is also possible for the push rod 332, as shown in Figure 14, to be arranged on a side of the rotor hub 2 opposite the rotor main shaft 6. In this case, analogous to the bevel gear drive of Figures 2 and 3, a housing 272 is provided that surrounds the push rod mechanism 330, and the housing 272 can in turn be equipped with a spinner 274 as a flow optimization element. If the push rod 332 extends through the rotor main shaft 6 designed as a hollow shaft, as shown in Figures 3, 5 and 15 to 23, a linear bearing unit 370 in the form of a bearing bush 372 is also arranged on the rotor main shaft 6, which supports the push rod 332 with respect to the rotor main shaft 6 and ensures axial mobility of the push rod 332.The push rod 332 itself, as mentioned above, has a rotor hub-side end 334 and a second end, which in Figs. 3, 5, and 15 to 23 is designed as a nacelle-side end 336. The second end 336 can extend through the entire rotor shaft 6; however, it is also possible, as shown particularly in Fig. 15, for the nacelle-side end 336 of the push rod 332 to be received in the main rotor shaft 6.

[0100] To move the push rod 332 axially, as mentioned above, the second end 336 of the push rod 332 is subjected to axial force directly or indirectly by means of a linear drive 400. In the exemplary embodiments illustrated in Figures 14 and 15, the push rod 332 is designed at its second end 336 as a hydraulic piston 402, which is received in a hydraulic cylinder 404. In Figure 14, the hydraulic cylinder 404 is received in the housing section 272, while in the exemplary embodiment of Figure 15, the hydraulic cylinder is inserted into the rotor main shaft 6.

[0101] Of course, in addition to the hydraulic linear drive 400 shown here, any other linear drive 400 can be used, for example a pneumatic linear drive or a worm drive.

[0102] The push rod 332, designed as a piston, has a flange 405 at its second end, which is sealingly guided in the piston housing 404 and thus forms a first working chamber 406 and a second working chamber 408. The first working chamber 406 and the second working chamber 408 can each be pressurized with hydraulic fluid in order to move the push rod piston 402 and thus the push rod 332 from the first position I to the second position II. A pump unit 410 is also provided for the application of hydraulic fluid, which, in the embodiment shown in Fig. 15, is non-rotatably received in the nacelle 8 and is rotatably attached to the hydraulic cylinder 404 via a rotary union 412. Such rotary unions 412 are known in the prior art and will therefore not be described further. The rotary union 412 is in turn fastened to the nacelle 8 in a rotationally fixed manner by means of a fastening element 414.Furthermore, control units 416 are accommodated in a stationary manner in the nacelle 8. Figure 15 shows that a cable feedthrough is provided for the cable 270, which runs from the nacelle 8 or the control units 416 through the main rotor shaft 6 and extends into the rotor blades 4, for example, to supply current to sensors and / or transmit signals. This cable 270 is also connected to the stationary elements 416; 410 in the nacelle 8 via a rotary feedthrough 419 at the end of the rotor hub 6.

[0103] Figures 16 to 23 show embodiments in which the gondola-side end 336 of the push rod 332 extends into the gondola interior 802. In these illustrated embodiments, too, the push rod 332 is moved from the first I to the second II position by means of a hydraulic linear drive 400. In contrast to the embodiment shown in Figure 12, however, in the embodiments shown in Figures 16 to 23, the push rod 332 or its gondola-side end 336 is not directly pressurized with a hydraulic fluid, but the gondola-side end 336 of the push rod 332 is moved from the first I to the second II position by means of a separate linear drive unit 400, which is non-rotatably fastened in the gondola 8.However, since the push rod 332 rotates with the rotor hub 2 in the same way as the rotor main shaft 6, but the linear drive 400 is stationary, a rotational decoupling must be provided between the push rod 332 and the linear drive 400.

[0104] The figures further show that the linear drive 400 again has an axially moving piston 402, which is now, however, designed as a separate element and acts on the nacelle-side end 336 of the push rod 332. For this purpose, the piston 402 has a push rod-side end 420 and a nacelle-side end 422. The nacelle-side end 422 of the piston 402 is received in a piston-cylinder housing 404 and is designed to be pressurized with hydraulic fluid. For this purpose, a first working chamber 406 and a second working chamber 408 are provided, which, analogous to the exemplary embodiment described above, are pressurized with hydraulic fluid supplied by the pump unit 410 in order to move the piston 402 from the first position I to the second position II.Furthermore, Figures 16, 19 and 20, 21 in particular show that the push rod-side end 420 of the piston 402 and the nacelle-side end 336 of the push rod 332 are accommodated in a push rod-piston connecting housing 426. The push rod-piston connecting housing 426 is in turn axially displaceably accommodated in a linear drive housing 428, which in turn is non-rotatably coupled to the rotor main shaft 6. The piston 402, more precisely the push rod-side end 420 of the piston 402, can be connected in a rotationally fixed manner to the push rod-piston connecting housing 426 (see Fig. 16, 19), but it is also possible, as shown in Figs. 20 and 21, that the nacelle-side end 336 of the push rod 332 is coupled in a rotationally fixed manner to the push rod-piston connecting housing 426.

[0105] In both cases, it should be noted that the linear drive housing 428 and the push rod 332 rotate together with the rotor main shaft 6, while the piston 402 of the linear drive 400 is stationary. For this reason, a first and a second bearing unit 430, 440 are arranged in the push rod-piston connecting housing 426. In the illustrated embodiment, the bearing units 430; 440 are designed as rolling bearings with an inner ring 432; 442, an outer ring 434; 444, and rolling elements 436; 446 arranged therebetween, but can also be a plain bearing. As can be seen in particular from the detailed views of Figures 19, 20 and 21, the bearing inner rings 432 and 442 are fixedly secured against rotation to the push rod 332 (see Figure 19) or to the piston 402 (see Figures 20, 21), while the outer rings 434; 444 are fixedly secured against rotation to the push rod-piston connecting housing 426.

[0106] By providing the bearing units 430 and 440 in the push rod-piston connecting housing 426, a rotational decoupling between the rotating push rod 332 and the stationary piston 402 can be achieved. Accordingly, the push rod-piston connecting housing 426 of the embodiments illustrated in Figures 19 to 23 is also stationary, while in the embodiment of Figures 20, 21 it rotates together with the rotor main shaft 6, the linear drive housing 428, and the push rod 332.

[0107] As further illustrated in Figures 3, 5, and 16 to 23 and mentioned above, the linear drive 400 is also designed as a hydraulic piston drive in this exemplary embodiment. The piston 402 is guided in a cylinder 404 and, together with the cylinder, forms a first working chamber 406 and a second working chamber 408, which are alternately supplied with hydraulic fluid by means of a hydraulic fluid provided by the hydraulic pump 410 in order to move the piston 402 from a first position I to a second position II. For this purpose, the piston 402 has a flange 405 at the cylinder-housing-side end 422, with which the piston 402 is sealingly guided in the piston housing 404 and separates the working chambers 406, 408 from one another. The piston housing 404 is supported, on the one hand, in a rotationally fixed manner in the nacelle by means of a fastening means 414 and is at least partially enclosed by the linear drive housing 428.This ensures a defined position and fastening of the linear drive 400 in the gondola.

[0108] However, since, as mentioned above, the linear drive housing 428 is non-rotatably connected to the rotor main shaft 6 and therefore also rotates, but the piston housing 404 is stationary, rotational decoupling must also be provided between the piston housing 404 and the linear drive housing 428.

[0109] In the embodiments illustrated in Figures 16 and 19 to 23, this rotational decoupling is achieved via two bearing units 450, 460, which, analogous to the bearing units 420, 430, are designed as rolling bearings, in particular tapered roller bearings, and each have an inner ring 452, 462, an outer ring 454; 464, and rolling elements 456; 466 arranged therebetween. The inner rings 452, 462 are arranged in a rotationally fixed manner on the piston housing 424, while the outer rings 454, 464 are arranged in a rotationally fixed manner in the linear housing 428. Of course, a plain bearing can also be used here, or the bearing units can be arranged differently.

[0110] As can also be seen from the detailed views of Figures 19, 20 and 21, a preloading element 470 in the form of a spring is also arranged on the push rod-piston connecting housing 426, which preloads the push rod 332 into a first position I (see in particular Fig. 21). The first position I is preferably the feather position, so that in the event of a power failure or no hydraulic fluid supply, the rotor blades 4 are rotated out of the flow, so that no torque is introduced into the underwater turbine 1. If the push rod-piston connecting housing 426 is connected to the piston 402 in a rotationally fixed manner, the spring is preferably supported, as can be seen from Figure 19, on the one hand on the push rod-piston connecting housing 426 and on the other hand on the piston housing 404. If, on the other hand, the push rod-piston connecting housing 426 is connected to the push rod 332 in a rotationally fixed manner (see Fig.20, 21), it rotates with the push rod 332 and the linear drive housing 428, so that the spring return element 470 can be supported on the one hand on the push rod-piston connecting housing 426 and on the other hand on the linear drive housing 428, as shown in Figures 21 and 22.

[0111] In addition to the preload element 470, which preloads the push rod 332 into a specific position, it is further advantageous if a locking device 480 is also provided, which blocks the linear movement of the push rod 332. The locking device 480 can have locking elements, for example in the form of bolts 482, 484, which, as shown in Figures 19 to 21, engage with the push rod-piston connecting housing 426 and fix it in a specific position. For this purpose, the push rod-piston connecting housing 426 has an opening 486 into which the bolt 482 or 484 can be inserted and holds the push rod 332 in a specific, predetermined position. The first position I (see Figure 21) can again be the feathered position of the rotor blades, while the second position II (see Figure 20) can correspond to an optimal torque transmission position of the rotor blades 6. Of course, several locking bolts can also be provided.

[0112] Alternatively or in addition to the bolts 482, 484, which interact with the push rod-piston connecting housing 426, it can also be provided, as can be seen from the exemplary embodiment in Figs. 22 and 23, that the locking device 480 acts directly on the push rod 332. For example, a bolt 488 can be arranged on the main rotor shaft 6, which extends through a bore 490 in the main rotor shaft 6 in the direction of the push rod 332 and there interacts with a bolt receptacle 492 provided in the push rod 332 to secure the push rod 332 in a specific position. In this case, too, it is advantageous that this position corresponds to the feathering position of the rotor blades 4, since in this case it is ensured that even in the event of a power failure or inactive control of the rotor blades, they remain rotated out of the flow and do not introduce any further torque into the underwater turbine.

[0113] The locking device 480, as well as other elements and sensors, can in turn be powered or controlled via control units 416 arranged in the nacelle 8. Cables 418 can also be provided for this purpose, which extend via corresponding rotary unions to the locking elements or the rotor blades in order to conduct signals or current.

[0114] List of reference symbols

[0115] 1 underwater turbine

[0116] 2 rotor hub

[0117] 4 rotor blades

[0118] 5 screws

[0119] 6 Rotor main shaft

[0120] 8 gondolas

[0121] 802 gondola interior

[0122] 10 Generator

[0123] 12 Generator rotor

[0124] 14, 16 bearing units rotor main shaft

[0125] 200 rotor hub arrangement

[0126] 202 rotor hub housing

[0127] 203 Rotor blade shaft lateral surface

[0128] 204 Rotor blade shaft

[0129] 205 tapered bearing surface for tapered plain bearing bush

[0130] 206 stop surface

[0131] 207 seaward end of the rotor blade shaft

[0132] 208 rotor hub end of the rotor blade shaft

[0133] 209 Rotor blade shaft bore

[0134] 210 Interior

[0135] 214 Rotor blade bearing arrangement

[0136] 220 offshore rotor blade shaft bearing unit

[0137] 230 rotor hub-side rotor blade shaft bearing unit

[0138] 221; 231 rolling bearings

[0139] 222; 232 inner ring

[0140] 223; 233 outer ring

[0141] 224; 234 Rolling elements; 235 Plain bearings; 236 Plain bearing bushes; 237 Inner bore of the bearing rings; 238 Sleeve section of the plain bearing bush; 239 Optional flange section of the plain bearing bush

[0142] S eewas serdi chtung

[0143] Gap between housing and rotor blade shaft

[0144] Dirt retention seal

[0145] shaft nut

[0146] Rib structures

[0147] Rotor hub housing section Rotor hub-side first housing section Sea-side second housing section Counter stop surface

[0148] Module tubular module housing section

[0149] Fasteners for module

[0150] Cable

[0151] Drive device housing

[0152] Spinner rotor-side sliding surface pairing sea-side sliding surface pairing ; 291 outer radial sliding surfaces ; 292 inner radial sliding surfaces ; 293 outer axial sliding surface ; 294 inner axial sliding surface

[0153] inner ring

[0154] Rotor blade twisting device

[0155] Bevel gear drive

[0156] Bevel gear on rotor blade shaft central bevel gear

[0157] Bevel gear drive (electric motor)

[0158] Gearbox

[0159] Transmission input shaft

[0160] Translation level

[0161] locking device

[0162] locking bevel gear

[0163] Thrust rod arrangement

[0164] push rod

[0165] Rotor hub side first end second end

[0166] Holding element

[0167] Connecting device

[0168] connecting rod

[0169] Connecting rod first connecting rod end second connecting rod end first connecting rod eye second connecting rod eye

[0170] bolt

[0171] bolt

[0172] Connecting rod-push rod connecting element; connecting rod holder

[0173] Connecting rod-rotor blade shaft connecting element; crank disc

[0174] Fasteners

[0175] Linear bearing unit

[0176] Bearing bush spherical plain bearing

[0177] Outer ring

[0178] inner ring

[0179] bolt

[0180] O-ring linear actuator

[0181] hydraulic piston

[0182] flange

[0183] Hydraulic cylinder first working chamber second working chamber

[0184] pump

[0185] rotary union

[0186] Fastening in gondola

[0187] Control units

[0188] Cable

[0189] Slip ring, hub end of the piston, nacelle end of the piston, piston housing = cylinder, push rod-piston connecting housing, linear drive housing; 440 bearing units; 442 bearing inner ring; 444 bearing outer ring; 446 rolling elements; 460 bearing units

[0190] Reset element

[0191] Locking device; 484 locking elements = bolts

[0192] Bolt receiving opening

[0193] bolt

[0194] drilling

[0195] Bolt holder X distance

[0196] Y distance dli inner diameter d2i inner diameter

[0197] W bearing distance

[0198] L Length of the rotor blade shaft

Claims

P a t e n t a n s p r ü c h e 1. Underwater turbine (1) with a rotor hub (2) which is connected in a rotationally fixed manner to a rotor main shaft (6) and is designed to drive the rotor main shaft (6), wherein the rotor main shaft (6) extends into a nacelle (8) connected to the rotor hub (2) via the rotor main shaft (6) and drives a generator (10) accommodated therein, wherein the rotor hub (2) is further designed to carry at least one rotor blade (4), wherein the at least one rotor blade (4) is fastened to a rotor blade shaft (204), and wherein the rotor blade shaft (204) is rotatably mounted on the rotor hub (2) and has a first rotor-hub-side end (208) which projects into an interior of the rotor hub (2), and a second sea-side end (207) which can be fastened in a rotationally fixed manner to the respective rotor blade (4), wherein the rotor hub-side end (208) of the rotor blade shafts (204) is designed to cooperate with a rotor blade adjustment arrangement (300),to rotate the at least one rotor blade shaft (204), wherein the rotor blade adjustment arrangement (300) further comprises a translationally movable push rod (332) having a first rotor hub-side end (334) designed to protrude into the rotor hub (2) of the underwater turbine (1) and having at least one connecting device (340) designed to be connectable to the rotor blade shaft (204) such that the translational movement of the push rod (332) is converted into a rotational movement of the at least one rotor blade shaft (204), and wherein the push rod (332) has a second nacelle-side end (336) designed to extend in the direction of the nacelle (8) of the underwater turbine (1), characterized in that the rotor blade adjustment arrangement (330) further comprises a locking device (480), which is designed to fix the push rod (332) in at least one predetermined translational position.

2. Underwater turbine (1) according to claim 1, wherein the locking device (480) has at least one adjustable locking element (482; 484; 488) which cooperates with the push rod (332) or a component (406; 426) of the linear drive (400) which moves the push rod (332) in a translational manner in order to fix the push rod (332) in its translational position.

3. Underwater turbine (1) according to claim 2, wherein the push rod (332) has at least one recess (492) on its lateral surface, which is designed to cooperate with the locking element (482; 484; 488).

4. Underwater turbine (1) according to one of the preceding claims, wherein a locking element (488) of the at least one locking element (482; 484; 488) is arranged on the rotor main shaft (6).

5. Underwater turbine (1) according to one of the preceding claims, wherein a locking element (482; 484) of the at least one locking element (482; 484; 488) is arranged on a linear drive housing (428) surrounding the linear drive (400) or on the linear drive (400) itself.

6. Underwater turbine (1) according to claim 5, wherein the linear drive housing (428) is non-rotatably mounted on the rotor main shaft (6).

7. Underwater turbine (1) according to claim 5 or 6, wherein the linear drive (400) further comprises a piston (402) which acts translationally on the push rod (332) and which has a rotor hub-side end (420) with which it acts on the push rod (332), and a nacelle-side end (422) which is subjected to force by means of the linear drive (400), and the nacelle-side end (336) of the push rod (332) and the rotor hub-side end (420) of the piston (402) are accommodated in a push rod-piston connecting housing (426) which is translationally displaceable in the linear drive housing (428).

8. Underwater turbine (1) according to claim 7, wherein the nacelle-side end of the push rod (3336) is connected in a rotationally fixed manner to the push rod-piston connecting housing (426) and the piston (402) is rotatably mounted in the push rod-piston connecting housing (426) by means of a second rotationally decoupling bearing unit (430; 440), and wherein the locking device (480) has at least one blocking element (482; 484) which cooperates with the push rod-piston connecting housing (426).

9. Underwater turbine (1) according to claim 7, wherein the rotor-side end (420) of the piston (402) is connected in a rotationally fixed manner to the push rod-piston connecting housing (426) and the nacelle-side end (336) of the push rod (332) is rotatably mounted in the push rod-piston connecting housing (426) by means of a second rotationally decoupling bearing unit (430; 440), and wherein the locking device (480) is arranged on the linear drive (400) and has at least one locking element (482; 484; 488) which cooperates with the piston (402).

10. Underwater turbine (1) according to one of the preceding claims, wherein the locking device (480) is designed to fix the push rod (332) at a plurality of translational positions.

11. Underwater turbine (1) according to one of the preceding claims, wherein a first translational fixing position of the push rod (332) corresponds to a rotor blade position in which no rotational force is transmitted from the flow to the rotor blade (4).

12. Underwater turbine (1) according to one of the preceding claims, wherein a second translational fixing position of the push rod (332) corresponds to a rotor blade position which enables maximum rotational force transmission of the flow to the rotor blade (4).

13. Underwater turbine (1) according to one of the preceding claims, wherein a third translational fixing position of the push rod (332) corresponds to a rotor blade position which results in a defined reduced rotational force transmission of the flow to the rotor blade (4) enables 50% to 90%, in particular 60% to 80%, preferably 70%, of a maximum rotational force transmission of the flow to the rotor blade (4).

14. Underwater turbine (1) according to one of the preceding claims, wherein the locking device (480) has at least one locking element (482; 484; 488) which can be actuated by means of a hydraulic or electromechanical actuator.

Images