EP2279112B1 - Strömungsmaschine mit zumindest zwei kontrarotierbaren rotoren und mechanischem momentenausgleich - Google Patents

Strömungsmaschine mit zumindest zwei kontrarotierbaren rotoren und mechanischem momentenausgleich Download PDF

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Publication number
EP2279112B1
EP2279112B1 EP09753819.3A EP09753819A EP2279112B1 EP 2279112 B1 EP2279112 B1 EP 2279112B1 EP 09753819 A EP09753819 A EP 09753819A EP 2279112 B1 EP2279112 B1 EP 2279112B1
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EP
European Patent Office
Prior art keywords
machine
drive
drive wheel
rotors
continuous
Prior art date
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Active
Application number
EP09753819.3A
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German (de)
English (en)
French (fr)
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EP2279112A1 (de
Inventor
Dierk SCHRÖDER
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Siemens AG
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Siemens AG
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H5/00—Arrangements on vessels of propulsion elements directly acting on water
    • B63H5/07—Arrangements on vessels of propulsion elements directly acting on water of propellers
    • B63H5/08—Arrangements on vessels of propulsion elements directly acting on water of propellers of more than one propeller
    • B63H5/10—Arrangements on vessels of propulsion elements directly acting on water of propellers of more than one propeller of coaxial type, e.g. of counter-rotative type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H1/00—Propulsive elements directly acting on water
    • B63H1/02—Propulsive elements directly acting on water of rotary type
    • B63H1/12—Propulsive elements directly acting on water of rotary type with rotation axis substantially in propulsive direction
    • B63H1/14—Propellers
    • B63H1/16—Propellers having a shrouding ring attached to blades
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D19/00—Axial-flow pumps
    • F04D19/02—Multi-stage pumps
    • F04D19/024—Multi-stage pumps with contrarotating parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H1/00—Propulsive elements directly acting on water
    • B63H1/02—Propulsive elements directly acting on water of rotary type
    • B63H1/12—Propulsive elements directly acting on water of rotary type with rotation axis substantially in propulsive direction
    • B63H1/14—Propellers
    • B63H1/16—Propellers having a shrouding ring attached to blades
    • B63H2001/165—Hubless propellers, e.g. peripherally driven shrouds with blades projecting from the shrouds' inside surfaces
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H23/00—Transmitting power from propulsion power plant to propulsive elements
    • B63H2023/005—Transmitting power from propulsion power plant to propulsive elements using a drive acting on the periphery of a rotating propulsive element, e.g. on a dented circumferential ring on a propeller, or a propeller acting as rotor of an electric motor

Definitions

  • the invention relates to a turbomachine according to the preamble of patent claim 1;
  • a turbomachine is for example by the US 2,509,442 A known as the closest prior art.
  • the WO 98/38085 A1 discloses a turbomachine with at least two rotors, which are rotatably mounted in opposite directions about an axis of rotation and on the outside of blades or vanes are arranged, with a rotatably mounted about the same axis of rotation shaft and with a drive mechanism in the form of a transmission for converting a Rotational movement of the shaft in mutually opposite directed rotational movements, ie a Kontrarotation, the rotors and / or vice versa.
  • the shaft runs along the axis of rotation of the rotors through it.
  • the turbomachine can be used to particular advantage in a marine propulsion system such as a POD, in which the first rotor forms with its blades or blades a first propeller and the second rotor with its blades or blades a second propeller driven by the shaft via the drive mechanism become. Due to the contrarotating second propeller, the lossy swirl of the propeller outflow of the first propeller is partially re-directed and converted into thrust. By such a mechanical torque compensation, the efficiency of the ship propulsion system is improved.
  • the shaft can be driven, for example, by an electric motor or an internal combustion engine.
  • the torque of the shaft is distributed by the drive mechanism on the two propellers, wherein the rotational speed of the shaft is advantageously selected to be greater than the rotational speed of the two rotors.
  • the drive mechanism thus has the function of a reduction gear.
  • the turbomachine can also be used particularly advantageously as a turbine, for example for driving a generator.
  • the rotors then drive the shaft, wherein the rotational speeds of the at least two rotors are advantageously smaller than the rotational speed of the shaft.
  • the drive mechanism then acts as a step-up gear, reducing the moment to be transmitted by the shaft.
  • the problem is that the drive mechanism must be accommodated in the relatively small hub. This leads to a high mechanical complexity of the hub.
  • the dense construction also leads to problems in storage and lubrication of the bearings, which may affect the reliability of the turbomachine.
  • the hub would have to be made larger, but this would be disadvantageous in terms of fluid dynamics and would negate the efficiency advantages of the contrarotating arrangement.
  • a turbomachine according to the preamble of claim 1 is known from US 2,509,442 A known.
  • the shaft is arranged perpendicular to the housing and therefore protrudes from the housing.
  • turbomachine it is an object of the present invention to provide a turbomachine, in which the hydrodynamic advantages of several contra-rotating rotors can be used, but which has a comparatively lower mechanical complexity and component density and thus increased reliability.
  • a turbomachine comprises at least two rotors, which are rotatably mounted in opposite directions about an axis of rotation and on which blades or vanes are arranged, a rotatably mounted machine shaft and a drive mechanism which connects the machine shaft with the at least two rotors and a rotational movement the machine shaft in opposite directions directed rotational movements, ie a contrarotation that converts rotors or vice versa.
  • a housing forms a channel for a flow of a fluid, wherein the rotors are arranged in the channel in the flow direction of the fluid one behind the other.
  • the machine shaft and the rotors are annular and rotatably mounted in the housing, wherein the annular rotors each have an inner ring side and a ring outer side and wherein the blades or vanes are respectively arranged on the inner ring side of the rotors.
  • the fluid may be a liquid or a gas.
  • the annular design of the rotor it is particularly advantageous possible to dispense with the rotors on a (central) shaft, ie a component that connects the blade or wing ends of a rotor on its side facing away from the annular rotor with each other, and necessary holders , which is disturbing for a fluid flowing in the rotors would be and reduced the efficiency of a turbomachine.
  • the turbomachine is therefore preferably free of a component which extends along the axis of rotation of the rotors therethrough.
  • the absence of a central shaft also has the advantage that in the channel entering foreign bodies, such as cords or nets, can cause no major damage.
  • the drive mechanism is preferably also formed annular.
  • the first drive wheel and the machine shaft need not necessarily be two separate components, but both may also form a single component, i. the first drive wheel can also be integrated into the machine shaft.
  • the second and third drive wheel and the respectively associated rotor need not necessarily be two separate components, but both may also form a single component, i. the first drive wheel can also be integrated into the machine shaft.
  • a particularly space-saving torque transmission relative to the circumference is thereby possible in that the first drive wheel, the second drive wheels and the third drive wheel each have a bevel gear provided with a toothing are formed, wherein the second drive wheels each form a bevel gear with both the first drive wheel and the third drive wheel, and wherein the axes of rotation of the drive shafts of the second drive wheels are at a right angle to the axes of rotation of the first and third drive wheel.
  • the first drive wheel is provided with an internal teeth provided with cylindrical drive wheel and the second drive wheels and the third drive wheel respectively as cylindrical, provided with external teeth drive wheels, wherein the second drive wheels with the first drive wheel and the third drive wheel form a planetary gear and wherein the axes of rotation of the drive shafts of the second drive wheels are parallel to the axes of rotation of the first and third drive wheels.
  • the third drive wheel may be a cylindrical drive wheel provided with inner teeth
  • the second drive wheels and the first drive wheel may each be formed as cylindrical drive wheels provided with outer teeth, the second drive wheels forming a planetary gear with the first drive wheel and with the third drive wheel and wherein the axes of rotation of the drive shafts of the second drive wheels are parallel to the axes of rotation of the first drive wheel and the third drive wheel.
  • the drive mechanism is preferably integrated in the housing.
  • rotors are arranged one behind the other in the flow direction of the fluid, wherein in each case rotors arranged one behind the other are each coupled to each other via a drive mechanism described above in such a way that they rotate in opposite directions, ie, they contrarotate.
  • a machine order according to the invention comprises a turbomachine according to the invention described above and an electric machine, wherein the electric machine has a ring-shaped rotor which is coupled to the machine shaft and rotatably mounted about the same axis of rotation as the rotors of the turbomachine, and an annular arranged around the rotor Stator includes. Since the electric machine can be operated at a significantly higher speed compared to the rotors, the motor can be built smaller and lighter compared to conventional machine arrangements with the same power. Due to the annular design of the rotor of the electric machine and its rotatability about the same axis of rotation as that of the rotors and the machine shaft of the turbomachine, the electric machine can be directly, i.
  • the machine assembly can thus be built comparatively compact with a relatively low weight and space requirements.
  • the electric machine is preferably arranged in front of or behind the rotors in the flow direction of the fluid. As a result, the diameter of the housing can be kept small, which can result in hydrodynamic advantages. But it is also possible that the electrical machine is arranged annularly around only one of the rotors or around both rotors.
  • the inner diameter of the annular rotor of the electric machine is greater than or equal to the inner diameter of the annular rotors of the turbomachine.
  • the electric machine then has a larger inner diameter than the channel for the flow of the fluid and thus does not constitute an additional flow resistance for the fluid.
  • the advantage here is the electrical machine integrated into the housing of the turbomachine.
  • an inventive turbomachine or machine arrangement is characterized by high efficiency, robustness, ease of maintenance, a relatively low weight, a relatively small footprint and good cavitation properties, it is particularly suitable as a propulsion device for floating and diving equipment, especially for underwater vessels.
  • turbomachine or machine arrangement according to the invention also particularly suitable for use as a horizontally and / or vertically rotatable drive device or as a transverse jet drive device of a floating device, in particular a ship.
  • a vertical twistability is possible, for example by means of a gimbal. Due to its relatively low weight, such a drive device may also be designed to be retractable and extendable from a hull and / or rotatable through 360 °.
  • a turbomachine or machine arrangement according to the invention is also particularly well suited for use in a water jet (waterjet) drive device of a floating device, in particular a ship, due to the aforementioned advantages.
  • a turbomachine or machine arrangement according to the invention can also be used as a pump, as a fan or a compressor, in particular its high efficiency and its robustness come into play.
  • a turbomachine or machine arrangement according to the invention can also be used as a turbine, in particular in a flow stream power plant.
  • a turbine can also be used to generate electricity in floating, diving or flying equipment and, for example, due to their relatively low weight from a ship's hull on and extendable and rotatable by 360 °.
  • FIG. 1 shows a turbomachine 1 with a nozzle-shaped housing 2, which forms a channel 3 for a flow of fluid from an inlet 4 to an outlet 5 in a flow direction 6.
  • two ring-shaped rotors 10, 11 are arranged in the flow direction 6 of the fluid behind one another, which are mounted on non-illustrated bearing in mutually opposite direction about a common axis of rotation 7 rotatably mounted in the housing 2.
  • the rotors 10, 11 each have an inner ring side 12 and a ring outer side 13.
  • On the inside of the ring 12 in the circumferential direction of the rotors 10, 11 evenly distributed blades or vanes 14 are arranged, which co-rotate with the respective rotor 10, 11.
  • the rotors 10, 11 are axially and radially rotatably mounted in the housing 2 via bearings, not shown, for example, by means of their ring outer side 13.
  • the blades 14 are releasably secured to the rotors 10, 11 so that they can be exchanged.
  • the turbomachine 1 further comprises a machine shaft 15 and a drive mechanism 16 which connects the machine shaft 15 with the two rotors 10, 11 and which converts a rotational movement of the machine shaft 15 into oppositely directed rotational movements of the rotors 10, 11 or vice versa.
  • Both the machine shaft 15 and the drive mechanism 16 (which in principle constitutes a differential gear) are annular.
  • the machine shaft 15 is in this case mounted on the bearing not shown in detail about the same axis 7 as the rotors 10, 11 rotatably in the housing 2.
  • the drive mechanism 16 comprises a first drive wheel 21, a plurality of circumferentially distributed annular drive mechanism 16 evenly distributed second drive wheels 22 each having a rotatable about a rotation axis 28 drive shaft 24, and a third drive wheel 23.
  • the first drive wheel 21 is about the same axis of rotation as the rotors 10, 11 and the machine shaft 15 rotatably and rotatably connected thereto with the machine shaft 15.
  • the third drive wheel 23 is also rotatable about the same axis of rotation 7 as the rotors 10, 11 and the machine shaft 15 and for this purpose rotatably connected to the rotor 11.
  • the drive shafts 24 of the second drive wheels 22 are rotatably supported in the rotor 10.
  • the first drive wheel 21, a respective second drive wheel 22 and the third drive wheel 23 are arranged one behind the other.
  • the second drive wheels 22 are respectively coupled to the first drive wheel 21 and to the third drive wheel 23.
  • the drive mechanism 16 and the rotors 10, 11 are sealed by seals 17 relative to the channel 3.
  • FIG. 1 shown embodiment of the invention for coupling the drive wheels 21, 22, 23, the first drive wheel 21, the second drive wheels 22 and the third drive wheel 23 each formed as a toothed bevel gear, wherein the second drive wheels 22 both each form a bevel gear with the first drive wheel 21 and the third drive wheel 23, in which the drive wheel 22, the pinion and the drive wheels 21 and 23 each form the ring gear.
  • the drive shafts 24 of the second drive wheels 22 are rotatably mounted in the ring outer side 13 of the rotor 10 and their axes of rotation 28 are at a right angle to the axis of rotation 7 of the first drive wheel 21 and the third drive wheel 23. It engages both the teeth of the first drive wheel 21st as well as the toothing of the third drive wheel 23 in the teeth of the second drive wheels 22nd
  • first drive wheel 21 and the machine shaft 15 do not form separate components, but a single component, i. that the toothing of the first drive wheel 21 is applied directly to the machine shaft 15.
  • second rotor 11 and the third drive wheel 23 may also form a single component, i. the teeth of the third drive wheel 23 may be applied directly to the rotor 11.
  • the drive mechanism 16 has the function of a differential gear. It can be used for a power transmission from the machine shaft 15 to the rotors 10, 11 on the one hand. A rotational movement of the machine shaft 15 is then rotated by the drive mechanism 16 in mutually opposite directed rotational movements, ie a Kontrarotation, the rotors 10, 11 converted. If the machine shaft 15 rotates, for example, in the direction of the arrow 25, it moves the first rotor 10 in the opposite direction, symbolized by the arrow 26 and the second rotor 11 in the direction opposite to the rotor 10 direction, ie in the direction the machine shaft 15, as symbolized by the arrow 27, with.
  • the drive mechanism 16 can also be used for a power transmission from the rotors 10, 11 to the machine shaft 15. Opposite directed rotational movements of the rotors 10, 11 are then converted by the drive mechanism 16 in a rotational movement of the machine shaft 15.
  • the rotational speed (or angular velocity) of the rotors 10, 11 is significantly smaller than the rotational speed (or angular velocity) of the machine shaft 15, depending on the selected ratio.
  • the turbomachine 1 can thus be used both as a working machine that performs work on a fluid flowing through the channel 3, or as an engine driven by a fluid flowing in the channel 3, which outputs mechanical power to the engine shaft 15.
  • the lossy spin of the effluent of the first rotor 10 i.
  • Flow components of the fluid that deviate from the flow direction 6 are at least partially redirected in the main flow direction and thus converted into thrust or torque of a subsequent rotor.
  • the second rotor 11 thus at least partial torque compensation is effected.
  • the entire turbomachine 1 can be performed with relatively little weight.
  • the turbomachine 1 is coupled to an electrical machine 30.
  • the electric machine 30 comprises an annular rotor 31 having a not shown Exciter system (eg, a winding arrangement or an arrangement of permanent magnets), which is rotatably connected to the machine shaft 15 and rotatably mounted in the housing 2 by means not shown bearing about the same axis of rotation 7 as the rotors 10, 11 of the turbomachine 1.
  • the machine shaft 15 and the rotor 31 of the electric machine 30 can also form a single structural unit, ie the rotor-side exciter system of the electric machine 30 can also be arranged directly on the machine shaft 15.
  • the electric machine 30 further comprises an annular stator 32, which is integrated in the housing 2 and rotatably connected to the housing 2.
  • the stator 32 also has a not shown in detail excitation system that interacts electromagnetically with the excitation system of the rotor 31.
  • the stator 32 is arranged in the radial direction with respect to the axis of rotation 7 in front of the rotor 31.
  • the electric machine 30 is thus an outside machine, i. the rotor 31 is arranged annularly around the stator 32.
  • the electric machine 30 is in this case arranged in the flow direction 6 of the fluid in front of the first rotor 10.
  • the electric machine 30 can firstly be used as a gearless direct drive for driving the machine shaft 15 and thus the rotors 10, 11. However, the electric machine 30 can also be used as a generator driven by the rotors 10, 11 and the machine shaft 15.
  • turbomachine can of course be driven by other means known to those skilled in the art (eg via a gearbox) by an electric machine or an internal combustion engine, this machine does not necessarily have to be annular, but may also have a solid shaft with a rotation axis parallel or at an angle to the axis of rotation 7 of the rotors 10, 11.
  • machine assembly 35 is particularly resistant to resistance to the fluid flowing through the channel 3 formed.
  • the turbomachine 1 is free of a component (for example, a central shaft) which extends along the axis of rotation 7 of the rotors 10, 11 therethrough.
  • the machine shaft 15, the stator 31 and the rotor 32 of the electric machine 30 are integrated into the housing 2 of the turbomachine 1.
  • the annular rotors 10, 11 are formed such that the diameter of the ring inner side 12 (possibly including the thickness of a ring 17 disposed on the inner side seal 17) corresponds to the diameter of the channel 3 immediately in front of the respective rotor 10, 11.
  • the annular rotor 10, 11 is for this purpose recessed in the housing 2 and forms with its inner ring side 12 (possibly including a arranged on the inner ring 12 seal 17), the outer boundary surface of the channel 3 in the region of the rotor 10, 11, wherein these outer boundary surface flush with the adjacent, formed by the housing 2 outer boundary surface.
  • the annular rotors 10, 11 themselves thus do not constitute a flow resistance for the fluid.
  • the inner diameter of the annular rotor 31 of the electric machine 30 is greater than the inner diameter of the annular rotors 10, 11 of the turbomachine 1.
  • the inner diameter of the annular stator 32 of the electric machine 30 is (including the thickness of a possibly arranged on the inner ring side 12 seal 17th ) equal to the diameter of the channel 3 in the region of the electric machine 30 and thus forms the outer boundary surface of the channel 3 in the region of the electric machine 1, said outer boundary surface with the adjacent, formed by the housing 2 and the rotors 10, 11 outer boundary surface flees.
  • the electric machine 30 thus does not constitute a flow resistance for the fluid.
  • turbomachine 40 differs from the in FIG. 1 characterized turbomachine 1 characterized in that the first drive wheel 41 is designed as a cylindrical drive wheel provided with inner teeth, and the second drive wheels 42 and the third drive wheel 43 are each designed as cylindrical drive wheels provided with outer teeth.
  • the second drive wheels 42 form with the first drive wheel 41 and the third drive 43, a planetary gear with a ring gear, a sun gear and a plurality of planetary gears arranged therebetween, wherein the first drive 41, the ring gear, the third drive 43, the sun gear and the second drive wheels 42nd represent the planet gears.
  • both the toothing of the first drive wheel 41 and the toothing of the third drive wheel 43 engages in the toothings of the second drive wheels 42.
  • the drive shafts 44 of the second drive wheels 42 are in this case arranged on the rotor 10 facing end face 45 of the rotor 11 and have rotational axes 48 which extend parallel to the axis of rotation 7 of the first drive wheel 41 and the third drive wheel 43.
  • outer boundary surface under the end face of a rotor, in the axial direction, i. understood in the direction of its axis of rotation 7, outer boundary surface.
  • first drive wheel 41 and the machine shaft 15 do not form separate components, but rather a single integrated component, i. the toothing of the first drive wheel 41 is applied directly on the machine shaft 15.
  • the rotor 10 and the third drive wheel 43 also form a single integrated component, i. the teeth of the third drive wheel 43 is applied directly to the rotor 10.
  • FIG. 3 shows a longitudinal sectional view of a ship 50 of the type "Corvette", in which a first machine assembly 35 consisting of a turbomachine 1 and an electric machine Machine 30 according to FIG. 1 or 2 is used with great power as a horizontally rotatable drive device 51 at the stern 52 of the ship.
  • the machine assembly 35 is in this case rotationally fixedly attached to a shaft 53 which is horizontally rotatably mounted in the ship 50.
  • a vertically rotatable drive device with a machine arrangement 35 can be arranged at the stern 52 of the ship 50.
  • a second machine assembly 35 according to FIG. 1 or 2 used with medium power in a water jet (waterjet) drive device 54, which is arranged on the ship bottom 55.
  • a water jet (waterjet) drive device 54 which is arranged on the ship bottom 55.
  • generators preferably diesel generators, or other power sources or energy storage devices such as diesel generators.
  • the drive consists of two horizontally rotatable drive devices 51 and two water jet (waterjet) drive devices 54.
  • the electrical machines 35 can also be operated as generators for energy recovery.
  • FIG. 4 shows an underwater vessel 60, wherein a machine assembly 35 according to FIG. 1 or 2 as propulsion device 61 at the stern 62 of the underwater vessel 60 is used.
  • the machine assembly 35 is fastened by means of a bracket 63 at the stern 62 of the ship. Since the rotor blades are surrounded by the housing in the machine assembly 35, the drive is characterized by a particularly low generation of noise, which is often important especially for underwater vessels.
  • the power supply to the electrical machine of the machine assembly 35 can be effected via the holder 63.
  • generators aboard the underwater hull 60 are one or more generators (not shown in detail), preferably diesel generators, or other power sources or energy storage devices, such as wind turbines. Batteries and / or fuel cells, which supply the operated as an electric motor electric machine of the machine assembly 35 with electricity.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Ocean & Marine Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)
EP09753819.3A 2008-05-27 2009-05-20 Strömungsmaschine mit zumindest zwei kontrarotierbaren rotoren und mechanischem momentenausgleich Active EP2279112B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008025210 2008-05-27
PCT/EP2009/056156 WO2009144164A1 (de) 2008-05-27 2009-05-20 Strömungsmaschine mit zumindest zwei kontrarotierbaren rotoren und mechanischem momentenausgleich

Publications (2)

Publication Number Publication Date
EP2279112A1 EP2279112A1 (de) 2011-02-02
EP2279112B1 true EP2279112B1 (de) 2013-04-24

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Country Status (6)

Country Link
US (1) US8487466B2 (es)
EP (1) EP2279112B1 (es)
KR (1) KR101205147B1 (es)
DK (1) DK2279112T3 (es)
ES (1) ES2409113T3 (es)
WO (1) WO2009144164A1 (es)

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DE102012211844A1 (de) * 2012-07-06 2014-01-09 Siemens Aktiengesellschaft RIM-Antriebssystem für Wasserfahrzeuge
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EP2279112A1 (de) 2011-02-02
WO2009144164A9 (de) 2010-05-20
ES2409113T3 (es) 2013-06-25
DK2279112T3 (da) 2013-07-29
US8487466B2 (en) 2013-07-16
KR101205147B1 (ko) 2012-11-26
WO2009144164A1 (de) 2009-12-03
US20110074158A1 (en) 2011-03-31
KR20120096957A (ko) 2012-09-03

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