EP2652315A2 - Segment de bague de palier, bague de palier, palier, arbre d'entraînement et procédé de montage associé - Google Patents

Segment de bague de palier, bague de palier, palier, arbre d'entraînement et procédé de montage associé

Info

Publication number
EP2652315A2
EP2652315A2 EP11796977.4A EP11796977A EP2652315A2 EP 2652315 A2 EP2652315 A2 EP 2652315A2 EP 11796977 A EP11796977 A EP 11796977A EP 2652315 A2 EP2652315 A2 EP 2652315A2
Authority
EP
European Patent Office
Prior art keywords
bearing
bearing ring
drive shaft
flange
ring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP11796977.4A
Other languages
German (de)
English (en)
Inventor
Johannes Goetz
Hubert Herbst
Fred Menig
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SKF AB
Original Assignee
SKF AB
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by SKF AB filed Critical SKF AB
Publication of EP2652315A2 publication Critical patent/EP2652315A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B11/00—Parts or details not provided for in, or of interest apart from, the preceding groups, e.g. wear-protection couplings, between turbine and generator
    • F03B11/06—Bearing arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B13/00—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates
    • F03B13/10—Submerged units incorporating electric generators or motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
    • F16C17/14—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load specially adapted for operating in water
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/26—Systems consisting of a plurality of sliding-contact bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/50—Bearings
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/20—Hydro energy

Definitions

  • the present invention is in the field of low-maintenance support of drive shafts, in particular drive shafts in underwater power plants.
  • Submarine power plants are already known from the field of conventional technology.
  • well-known storage concepts for underwater power plants are briefly summarized.
  • DE102009005556A1 discloses a concept for flushing of underwater power plants, which consciously dispenses with encapsulation of the bearings used.
  • the area in direct contact with the surrounding water is to be protected against excessive sediment.
  • the growth in this area must be limited.
  • One of the measures involved is to rinse the flooded area and, in particular, the bearings and the components associated therewith, such as sealing elements and the like.
  • One concept provides for applying at least one flushing connection to an underwater power station, by means of which a flushing medium can be supplied to the system from outside. Accordingly, there is no delivery system, such as a pump or the like, for the flushing medium in the system itself between the external flushing connection and the area to be flushed. Furthermore, an additional filter system is dispensed with. Instead, the flushing medium is supplied at such an overpressure at the external flushing connection that there is a sufficiently strong flow through the area to be flushed and an outflow to the outside area, whereby sediments and preferably an originally present growth are transported to the outside.
  • a concept for optimized power control and control of underwater power plants is disclosed in DE102008053732B3.
  • DE102008031615A1 shows a generator assembly which can be handled as a whole and can be mounted as a unit, which can be transported and mounted separately from the actual drive shaft of an underwater power plant.
  • This includes a generator rotor and a generator stator, the basic components of an electric generator.
  • a generator housing is part of the generator unit.
  • the control and power components of the electric generator can be additionally included in the generator assembly.
  • DE102008061912 AI deals with bearing pads, for example, for seawater suitable bearings. For a hydrodynamically building up lubricating film and the associated parabolic pressure development for soft or elastic sliding linings, a concave deflection occurs in the central area.
  • DE102008006899A1 discloses a concept for supporting a drive shaft of an underwater power plant.
  • a bearing arrangement is provided, for supporting a shaft of a device for generating energy from a water flow, the bearing arrangement having at least one radial sliding bearing and at least one axial sliding bearing and wherein the bearing arrangement can be lubricated by water penetrating from the outside.
  • FIG. 3 shows a schematic structure of an underwater power plant.
  • FIG. 3 shows a machine nacelle 300 with a segmented structure.
  • a hood 305 and a propeller-shaped water turbine 310 adjoin the machine nacelle 300 in the front region.
  • the nacelle 300 includes two segments 315 and 320 that contain the drive shaft 325.
  • another segment 330 is a generator 335 which is coupled to the drive shaft 325.
  • Another hood 340 terminates the underwater power plant after the generator 335.
  • the hood 305 forms with the water turbine 310, a circumferential unit which is coupled to the drive shaft 325.
  • a plurality of plain bearings are provided for storage of the drive shaft 325 .
  • a radial sliding bearing 345 In the front side of the drive shaft 325 facing the water turbine 310 there is a radial sliding bearing 345.
  • a radial sliding bearing 350 In the rear region of the drive shaft 325 facing the generator 335 there is another radial sliding bearing 350. Axial forces of the drive shaft are absorbed by the two axial sliding bearings 355 and 360 axially supporting the track pulley 365 connected to the drive shaft 325.
  • the plain bearings 345, 350, 355 and 360 can be carried out seawater resistant, in particular water lubricated. This makes it possible to flood the entire interior of the nacelle 300 and to dispense with elaborate seals, especially the bearings.
  • the sliding bearings used 345, 350, 355 and 360 are partially realized directly on the drive shaft 325.
  • very hard coatings are applied at the two respective ends of the shaft 325 over a width of approximately 100-4000 mm, which then each represent the inner ring for one of the radial sliding bearings 345, 350.
  • a coating method e.g. high-speed flame spraying (also HVOF, derived from high-velocity oxygen-fuel) or another thermal coating process for surface treatment.
  • HVOF high-speed flame spraying
  • a steel ring can be applied by welding and on the surface of which the coating takes place.
  • the warehouse runs directly in the water or seawater.
  • a disadvantage of the conventional concepts is the need to handle a large one-piece shaft.
  • the length of such a drive shaft which is usually designed as a hollow shaft, may be several meters, the diameter may also be over one meter, typical values would be 3 - 15 m in length with a diameter of 100 mm to 6000 mm with a power of 50kW - 15 MW.
  • the weight of such a drive shaft can easily amount to several tons, a typical weight would be 1 - 100 t.
  • a core idea of the present invention lies in the realization that radial bearings and drive shaft of an underwater power plant can be mechanically decoupled. This allows on the one hand to shorten the drive shaft and thus make it easier to handle, on the other hand to be able to produce the bearing separately from the drive shaft. Thus, the bearing is easier to handle and any coatings can be performed much easier or applied.
  • the mechanical separation can be realized by providing a flange on a bearing ring of the radial bearing.
  • the bearing ring itself may be in one piece or composed of several bearing ring segments. Zen.
  • the bearing ring segments may be equal to each other, but in embodiments, these may also be different.
  • the bearing ring described below may therefore be present in embodiments in various embodiments.
  • the flange which may also be composed of several segments, each of which may be the same or different.
  • bearing ring segments may have corresponding flange segments. Therefore, when the flange is described below, it may also be integral or multi-piece, i. composed of flange segments, be formed.
  • This flange is used to attach the bearing ring to the drive shaft.
  • the flange may be attached to both the bearing inner ring and the bearing outer ring.
  • the bearing ring may be formed integrally with the flange. In other embodiments, bearing ring and flange may also be formed in several pieces.
  • the drive shaft Due to the mechanical separation of bearing and drive shaft, maintenance can be considerably facilitated. During maintenance work on the bearing or the shaft, it is no longer necessary to change the entire drive shaft or the entire drive train, but the drive shaft and bearings can also be removed and maintained separately after the mechanical decoupling. This advantage increases with the number of mechanically decoupled bearings. In other words, the drive shaft may be supported by a plurality of decoupled or flanged bearings, reducing maintenance expense due to the possibility of separate handling for each decoupled bearing.
  • Another key idea of the present invention is to equip a bearing with a flange so that it can be frictionally coupled to a drive shaft. Such a coupling can then take place at both ends of the drive shaft, ie for the storage of the area facing a water turbine and / or the region facing a generator.
  • the radial bearings can be flanged to the respective ends of the shaft.
  • the radial bearings can then consist of one piece, a welding of rings on the shaft can be omitted. The handling of the radial stock in their manufacture can thus be facilitated.
  • These can be coated as required, a coating of the shaft is eliminated.
  • the processing of the now smaller components i. Radial bearing and drive shaft, to be separated from each other.
  • smaller production plants can be used, which can further reduce the production costs.
  • the manufacturing precision can be increased and the radial bearings can be individually coated separately.
  • the coating such as e.g. Dipping / bath treatment, as direct coating on the wave surface is no longer necessary. There is also no longer any distortion due to welding and no cleaning work is necessary, which was the case with conventional concepts after welding.
  • the complex conventional system can thus be broken down by embodiments into several simplified subsystems.
  • the individual subsystems can be processed more expediently, or can only be made accessible to certain process or processing steps due to the disassembly. This can allow a better adaptation or optimization of the processes to the subsystems and thus a cost reduction.
  • the assembly and disassembly of the radial bearing and the drive shaft facilitates. Downtimes of the system can be reduced, in particular by the fact that now storage changes are possible on site. Also, a storage preparation without great logistics effort is possible by embodiments. As a result, a cost reduction in production - assembly and maintenance can be achieved.
  • bearings can be machined separately, thereby making tribologically more favorable surface design possible, and, for example, facilitating the introduction of application-oriented lubrication grooves and holes.
  • lubricant lines and lubricant delivery systems can be more easily introduced into the system, thereby reducing the cost of lubricants In the end, in turn, the maintenance and thus the operating costs can be reduced.
  • Figure 2a shows another embodiment of a bearing ring, or of bearing ring segments;
  • FIG. 2b shows the shortening of a drive shaft in one embodiment
  • FIG. 2c shows an exemplary embodiment of a flow chart of an assembly method
  • Figure 3 is a conventional underwater power plant.
  • FIG. 1a shows an exemplary embodiment of a bearing ring 110, 110a, or of a bearing ring segment 110, 110a.
  • a bearing ring segment 110, 110a is understood as meaning a part of a bearing ring 110, 110a.
  • the bearing ring segment may accordingly comprise, for example, a certain angular range of a bearing ring 110, 110a, i. in embodiments, a plurality of identical or unequal bearing ring segments can form a bearing ring.
  • Embodiments are not limited to a specific subdivision of a bearing ring in bearing ring segments, there are any axial and radial segmentation conceivable.
  • the figure la also shows a portion of the drive shaft 130.
  • the attachment may include, for example, attachment means, such as e.g. Holes, threads, weld studs, weld nuts, screws, lands or grooves, clamps, etc. include.
  • a bridge Under a flange here is a bridge, a nose, a spring, an extension oa. understood, which serves for attachment to another component.
  • the respective other component can likewise have fastening means or fastening possibilities such as bores, threads, screws, welding studs, webs or grooves, clamps, etc.
  • the flange 120 may include grooves, lands, or teeth to achieve, for example, secure engagement with the drive shaft and secure against rotation with the drive shaft.
  • the bearing ring 110 can be designed as a bearing inner ring 110a, as shown in FIG. 1a, or bearing outer ring 110b.
  • the figure lb shows an embodiment in which the bearing ring 110, 110b is formed as a bearing outer ring 110b.
  • the flange 120 may also be attached to a bearing outer ring 110b.
  • the figure lb of the bearing inner ring is designated by the reference numeral 140.
  • the flange 120 can extend along the axis of rotation of the bearing 100, that is to say in the axial direction.
  • the flange 120 may at least partially enclose the drive shaft 130 and screwed, riveted, or the like, for example, with this. become. Since hollow shafts are also used in exemplary embodiments, it is also conceivable that the flange 120 also protrudes into the drive shaft 130 and is fastened to the drive shaft 130 from the inside becomes.
  • the drive shaft 130 may have radial mounting holes in embodiments. Depending on whether the flange 120 overlaps the drive shaft 130 inside or outside, the attachment holes or generally the attachment means may be provided inside or outside the drive shaft 120.
  • FIG. lc Another embodiment is shown in the figure lc.
  • the figure lc again shows a radial bearing 100 with a bearing ring 110, 110a, which is designed here as a bearing inner ring 110a.
  • the figure lc also shows a bearing outer ring 140.
  • the flange 120 can be seen, which also has a radial extent here. The radial extent of the flange 120 allows attachment to the end face of the drive shaft 130, which then may have mounting holes in the axial direction, for example.
  • the figure ld shows a further embodiment in which the bearing ring 110, 110b is formed as a bearing outer ring 110b.
  • the flange 120 in addition to an axial extent also has a radial extent.
  • Conceivable are also other embodiments in which the flange 120 has only a radial extension, that is, not primarily in the axial direction of the bearing ring 110 projects away.
  • the bearing ring 110 in embodiments may have a flange 120 which extends in the axial and / or radial direction.
  • Embodiments may also include a bearing ring segment 110; 110a; 110b for a radial bearing 100 for a propulsion shaft 130 of an underwater power plant having at one axial end a flange 120 or a flange segment 120, wherein the flange 120 or the flange segment 120 a fastening means for attachment of the bearing ring segment 110, 110a, 10b on the drive shaft 130 has.
  • the bearing ring segment 110; 110a; 110b may be designed as a bearing inner ring segment 110a or as a bearing outer ring segment 110b.
  • the flange 120 or the flange segment 120 may extend in embodiments in the axial and / or radial direction.
  • exemplary embodiments also include a bearing 100, for example a sliding or roller bearing 100, which has one of the abovementioned bearing rings 110, 100a, 110b or bearing ring segments 110, 100a, 110b.
  • FIG. 2a shows a further embodiment in which a section of a bearing 100 is shown on the left side. From the bearing 100, the bearing ring 110 can be seen. It can also be seen that the bearing ring 110 has a flange 120, via which the bearing ring 110 can be fastened to the drive shaft 130. It can also be seen in FIG. 2a that both the flange 120 and the drive shaft 130 have bores via which a screw connection can be made. For example, screws of type M 8 - 24 can be used here. In embodiments, the holes, for example, a diameter greater than or equal to 8 - 50mm, z. B. 10 mm, 20 mm or 30 mm.
  • the bearing ring 110 itself may have an outer diameter of, for example, 2200 mm in embodiments, wherein in the figure 2a, the outer radius 155 is shown to the axis of rotation 145 of the bearing.
  • the outer diameter (double outer radius 155) can also be greater than or equal to 100, 1000, 2000, 3000, 4000, 6000 or 10000 mm.
  • the inner diameter, which corresponds to twice the inner radius 150 according to FIG. 2a, of the bearing ring 110 comprises approximately 1800 mm.
  • the inner diameter (double inner radius 150) of the bearing ring 110 can also be greater than or equal to 50, 500, 1000, 1500, 2000, 3000, 5000 or 10000 mm.
  • the inner diameter of the bearing shell may comprise 2000 mm, which corresponds to twice the inner radius 160 of the bearing shell according to FIG. 2a.
  • the bearing ring 110 may have a sheath thickness of 200 mm.
  • double mecanicradii 160 of the bearing shell greater than or equal to 80, 100, 1000, 2000, 3000, 4000, 6000 or 10000 mm are conceivable.
  • the shell thickness of the bearing ring 110 may be greater than or equal to 50, 100, 200, 300 or 400 mm in embodiments.
  • the bearing height 170 i. the axial extent of the bearing ring 110 may be, for example, 1000 mm. In embodiments, however, bearing heights 170 greater than or equal to 100, 200, 300, 500, 1000, 2000, 3000 or 4000 mm are conceivable.
  • exemplary embodiments may also include a drive shaft 130 for an underwater power plant, which has fastening means or a fastening possibility for the flange 120 of a bearing ring 110 on at least one axial end. has.
  • the drive shaft 130 may have axial and or radial bores.
  • the drive shaft 130 itself may in turn comprise a flange to be attached to the bearing ring 110 or its flange 120.
  • the drive shaft 130 may also have teeth as fastening means for the flange 120 or its segments.
  • the drive shaft 130 may also have holes and an additional toothing.
  • FIG. 2b shows a section of a conventional underwater power plant, in particular the area of the drive shaft 325, 130.
  • the two dotted lines 180, 190 indicate which part of the drive shaft can be saved in embodiments, or that the drive shaft 130 in embodiments, at least can be shortened to the area in which was mounted in conventional storage, the bearing inner ring on the drive shaft.
  • Embodiments also include an underwater power plant assembly method including a step of flanging a bearing ring 110 of a bearing 100 to a drive shaft 130.
  • the assembly method may also include a step of assembling a bearing ring 110 of bearing ring segments.
  • An exemplary embodiment of an assembly method is illustrated schematically with reference to a flow chart in FIG. 2c.
  • An assembly method may include a step 210 of merging a bearing ring 110 with a drive shaft 130.
  • the bearing ring 110 can then be flanged to the drive shaft 130, for example by screwing or riveting.
  • the bearing ring 120 and / or the drive shaft may have a flange.
  • other steps may also be taken, such as a step 230 of mounting another bearing ring to complete the bearing 100, or a step 240 of mounting the entire unit into a housing, such as a nacelle.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention concerne une bague de palier (110; 110a; 110b) pour un palier radial (100) destiné à un arbre d'entraînement (130) d'une centrale électrique sous-marine, ladite bague de palier présentant, à une extrémité axiale, une bride (120) qui comporte un moyen de fixation servant à fixer la bague de palier (110; 110a; 110b) à l'arbre d'entraînement (130).
EP11796977.4A 2010-12-16 2011-12-09 Segment de bague de palier, bague de palier, palier, arbre d'entraînement et procédé de montage associé Withdrawn EP2652315A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010063275A DE102010063275A1 (de) 2010-12-16 2010-12-16 Lagerringsegment, Lagerring, Lager, Antriebswelle und Montageverfahren
PCT/EP2011/072255 WO2012080097A2 (fr) 2010-12-16 2011-12-09 Segment de bague de palier, bague de palier, palier, arbre d'entraînement et procédé de montage associé

Publications (1)

Publication Number Publication Date
EP2652315A2 true EP2652315A2 (fr) 2013-10-23

Family

ID=45349493

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11796977.4A Withdrawn EP2652315A2 (fr) 2010-12-16 2011-12-09 Segment de bague de palier, bague de palier, palier, arbre d'entraînement et procédé de montage associé

Country Status (3)

Country Link
EP (1) EP2652315A2 (fr)
DE (1) DE102010063275A1 (fr)
WO (1) WO2012080097A2 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108086883A (zh) * 2018-01-23 2018-05-29 广西阿赖门窗科技有限公司 电动卷帘门卷轴

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE9304615U1 (de) * 1993-03-26 1993-05-19 Skf Gmbh, 97421 Schweinfurt Anordnung zur Lagerung einer Welle oder Achse in einem Tragteil

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Publication number Priority date Publication date Assignee Title
JPH073217B2 (ja) * 1984-10-03 1995-01-18 株式会社日立製作所 チユ−ブラ水車
DE9102933U1 (de) * 1991-03-12 1991-05-29 Rheinhuette Gmbh & Co, 6200 Wiesbaden Wellenlagerung, insbesondere für eine Laufradwelle einer Magnetkreiselpumpe
DE202004007831U1 (de) * 2004-05-14 2004-07-22 Ab Skf Mehrreihiges Wälzlager für eine Windenergieanlage
DE102008006899A1 (de) 2008-01-31 2009-08-06 Schaeffler Kg Wassergeschmierte Lageranordnung
DE102008017537A1 (de) * 2008-04-03 2009-10-08 Voith Patent Gmbh Rohrturbinen-Generatoreinheit
DE102008031615A1 (de) 2008-07-07 2010-01-14 Voith Patent Gmbh Unterwasserkraftwerk und Verfahren für dessen Montage
DE102008053732B8 (de) 2008-10-29 2013-10-02 Voith Patent Gmbh Verfahren und Vorrichtung für die Leistungsregelung eines Unterwasserkraftwerks
DE102008061912A1 (de) 2008-12-15 2010-06-17 Voith Patent Gmbh Lagerkissen für ein segmentiertes, mediengeschmiertes Gleitlager
DE102009005556A1 (de) 2009-01-20 2010-07-22 Voith Patent Gmbh Verfahren und Vorrichtung zum Durchspülen eines Unterwasserkraftwerks

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE9304615U1 (de) * 1993-03-26 1993-05-19 Skf Gmbh, 97421 Schweinfurt Anordnung zur Lagerung einer Welle oder Achse in einem Tragteil

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2012080097A2 *

Also Published As

Publication number Publication date
DE102010063275A1 (de) 2012-06-21
WO2012080097A3 (fr) 2012-12-27
WO2012080097A2 (fr) 2012-06-21

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