EP2279112B1 - Turbo-machine having at least two counter-rotatable rotors and having mechanical torque compensation - Google Patents

Turbo-machine having at least two counter-rotatable rotors and having mechanical torque compensation 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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Application number
EP09753819.3A
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German (de)
French (fr)
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EP2279112A1 (en
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)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Description

Die Erfindung betrifft eine Strömungsmaschine gemäß Oberbegriff des Patentanspruchs 1; eine derartige Strömungsmaschine ist beispielsweise durch die US 2,509,442 A , die als nächstliegender Stand der Technik angesehen wird, bekannt.The invention relates to a turbomachine according to the preamble of patent claim 1; Such a turbomachine is for example by the US 2,509,442 A known as the closest prior art.

Die WO 98/38085 A1 offenbart eine Strömungsmaschine mit zumindest zwei Rotoren, die in zueinander entgegen gesetzter Richtung um eine Drehachse drehbar gelagert sind und an deren Außenseite Schaufeln oder Flügel angeordnet sind, mit einer um die gleiche Drehachse drehbar gelagerten Welle und mit einem Antriebsmechanismus in Form eines Getriebes zur Umwandlung einer Drehbewegung der Welle in zueinander entgegen gesetzt gerichtete Drehbewegungen, d.h. eine Kontrarotation, der Rotoren und/oder umgekehrt. Die Welle verläuft dabei entlang der Drehachse der Rotoren durch diese hindurch.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.

Die Strömungsmaschine kann besonders vorteilhaft bei einem Schiffsantriebssystem wie z.B. einem POD verwendet werden, bei dem der erste Rotor mit seinen Schaufeln oder Flügeln einen ersten Propeller und der zweite Rotor mit seinen Schaufeln oder Flügeln einen zweiten Propeller ausbilden, die von der Welle über den Antriebsmechanismus angetrieben werden. Durch den kontrarotierenden zweiten Propeller wird der verlustbehaftete Drall des Propellerabstromes des ersten Propellers teilweise wieder umgerichtet und in Schub umgewandelt. Durch einen derartigen mechanischen Momentenausgleich wird der Wirkungsgrad des Schiffsantriebssystems verbessert. Die Welle kann dabei beispielsweise von einem elektrischen Motor oder einem Verbrennungsmotor angetrieben werden. Das Drehmoment der Welle wird durch den Antriebsmechanismus auf die beiden Propeller verteilt, wobei die Rotationsgeschwindigkeit der Welle vorteilhafterweise größer als die Rotationsgeschwindigkeit der beiden Rotoren gewählt ist. Der Antriebsmechanismus hat somit die Funktion eines Reduktionsgetriebes.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.

Dies ist besonders vorteilhaft bei Antriebssystemen, in denen die Welle von einem Elektromotor angetrieben wird, weil die Rotationsgeschwindigkeit des Elektromotors höher sein kann als ohne Reduktionsgetriebe und infolgedessen der Durchmesser des Elektromotors verkleinert werden kann.This is particularly advantageous in drive systems in which the shaft is driven by an electric motor, because the rotational speed of the electric motor can be higher than without a reduction gear and, as a result, the diameter of the electric motor can be reduced.

Die Strömungsmaschine kann besonders vorteilhaft auch als Turbine, zum Beispiel zum Antrieb eines Generators, verwendet werden. Die Rotoren treiben dann die Welle an, wobei die Rotationsgeschwindigkeiten der zumindest 2 Rotoren vorteilhafterweise kleiner als die Rotationsgeschwindigkeit der Welle sind. Der Antriebsmechanismus hat dann die Funktion eines Steigerungsgetriebes, wodurch das durch die Welle zu übertragende Moment sinkt.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.

Bei der bekannten Strömungsmaschine besteht das Problem, dass der Antriebsmechanismus in der relativ kleinen Nabe untergebracht werden muss. Dies führt zu einer hohen mechanischen Komplexität der Nabe. Die dichte Bauweise führt weiterhin zu Problemen bei der Lagerung und der Schmierung der Lager, wodurch ggf. die Zuverlässigkeit der Strömungsmaschine beeinträchtigt wird. Um dem entgegenzuwirken, müsste die Nabe grö-βer gebaut werden, was jedoch fluiddynamisch von Nachteil ist und die Wirkungsgradvorteile der kontrarotierenden Anordnung zunichte machen würde.In the known turbomachine, 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. To counteract this, 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.

Eine Strömungsmaschine gemäß Oberbegriff des Patentanspruchs 1 ist aus der US 2,509,442 A bekannt. Die Welle ist dabei senkrecht zu dem Gehäuse angeordnet und ragt daher aus dem Gehäuse.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.

Ausgehend von dieser bekannten Strömungsmaschine ist es Aufgabe vorliegender Erfindung, eine Strömungsmaschine anzugeben, bei der die hydrodynamischen Vorteile mehrerer kontrarotierender Rotoren genutzt werden können, die jedoch eine vergleichsweise geringere mechanische Komplexität und Bauteildichte und somit erhöhte Zuverlässigkeit aufweist.Starting from this known 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.

Die Lösung dieser Aufgabe gelingt durch eine Strömungsmaschine gemäß Patentanspruchs 1. Vorteilhafte Weiterbildungen sind Gegenstand der Ansprüche 2 bis 8. Eine Maschinenanordnung mit einer erfindungsgemäßen Strömungsmaschine ist Gegenstand der Ansprüche 9 bis 11. Besonders vorteilhafte Verwendungen der Strömungsmaschine oder der Maschinenanordnung sind Gegenstand der Ansprüche 12 bis 16.The solution of this object is achieved by a turbomachine according to claim 1. Advantageous developments are subject matter of claims 2 to 8. A machine assembly with a turbomachine according to the invention is the subject of claims 9 to 11. Particularly advantageous uses of Turbomachine or the machine assembly are the subject of claims 12 to 16.

Eine erfindungsgemäße Strömungsmaschine umfasst zumindest zwei Rotoren, die in zueinander entgegen gesetzter Richtung um eine Drehachse drehbar gelagert sind und an denen Schaufeln oder Flügel angeordnet sind, eine drehbar gelagerte Maschinenwelle und einen Antriebsmechanismus, der die Maschinenwelle mit den zumindest zwei Rotoren verbindet und der eine Drehbewegung der Maschinenwelle in zueinander entgegen gesetzt gerichtete Drehbewegungen, d.h. eine Kontrarotation, der Rotoren umwandelt oder umgekehrt. Ein Gehäuse bildet einen Kanal für ein Strömen eines Fluids aus, wobei die Rotoren in dem Kanal in Strömungsrichtung des Fluids hintereinander angeordnet sind. Die Maschinenwelle und die Rotoren sind dabei ringförmig ausgebildet und drehbar in dem Gehäuse gelagert, wobei die ringförmig ausgebildeten Rotoren jeweils eine Ringinnenseite und eine Ringaußenseite aufweisen und wobei die Schaufeln oder Flügel jeweils auf der Ringinnenseite der Rotoren angeordnet sind.A turbomachine according to the invention 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.

Durch die ringförmige Ausbildung der Welle und der Rotoren, die Anordnung der Schaufeln bzw. Flügel auf der Ringinnenseite der Rotoren und die Lagerung der Rotoren in dem Gehäuse besteht ein wesentlich größerer Einbauraum für den Antriebsmechanismus zwischen der Welle und den Rotoren. Aufgrund des größeren Einbauraumes kann die mechanische Komplexität des Antriebsmechanismus und die Bauteildichte der Maschine verringert und somit die Zuverlässigkeit erhöht werden. Bei dem Fluid kann es sich hierbei um eine Flüssigkeit oder um ein Gas handeln.Due to the annular design of the shaft and the rotors, the arrangement of the blades or wings on the inner ring side of the rotors and the bearing of the rotors in the housing has a much larger installation space for the drive mechanism between the shaft and the rotors. Due to the larger installation space, the mechanical complexity of the drive mechanism and the component density of the machine can be reduced and thus the reliability can be increased. The fluid may be a liquid or a gas.

Durch die ringförmige Ausbildung des Rotors ist es besonders vorteilhaft möglich, bei den Rotoren auf eine (zentrale) Welle, d.h. eines Bauteiles, das die Schaufel- oder Flügelenden eines Rotors an ihrer dem ringförmigen Rotor abgewandten Seite miteinander verbindet, und dafür notwendige Halterungen zu verzichten, was störend für ein die Rotoren anströmendes Fluid wäre und den Wirkungsgrad einer Strömungsmaschine verringerte. Die Strömungsmaschine ist deshalb bevorzugt frei von einem Bauteil, das entlang der Drehachse der Rotoren durch diese hindurch verläuft. Der Verzicht auf eine zentrale Welle hat auch den Vorteil, dass in den Kanal eintretende Fremdkörper, wie z.B. Schnüre oder Netze, keine großen Beschädigungen anrichten können.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.

Um eine besonders gleichmäßige Kraftübertragung zwischen der Maschinenwelle und den Rotoren zu erzielen, ist der Antriebsmechanismus bevorzugt ebenfalls ringförmig ausgebildet.In order to achieve a particularly uniform force transmission between the machine shaft and the rotors, the drive mechanism is preferably also formed annular.

Gemäß einer konstruktiv besonders einfachen Ausgestaltung umfasst der Antriebsmechanismus ein erstes Antriebsrad, mehrere in Umfangsrichtung des ringförmigen Antriebsmechanismus verteilt angeordnete zweite Antriebsräder mit jeweils einer um eine Drehachse drehbaren Antriebswelle, und ein drittes Antriebsrad umfasst, wobei

  • das erste Antriebsrad drehfest mit der Maschinenwelle verbunden ist,
  • das dritte Antriebsrad drehfest mit einem ersten der beiden Rotoren verbunden ist,
  • die Antriebswellen der zweiten Antriebsräder drehbar in dem anderen der beiden Rotoren gelagert sind,
  • und wobei die zweiten Antriebsräder mit dem ersten und mit dem dritten Antriebsrad gekoppelt sind.
According to a structurally particularly simple embodiment, the drive mechanism comprises a first drive wheel, a plurality of distributed in the circumferential direction of the annular drive mechanism arranged second drive wheels each having a rotatable about an axis of rotation drive shaft, and a third drive wheel, wherein
  • the first drive wheel is rotatably connected to the machine shaft,
  • the third drive wheel is non-rotatably connected to a first of the two rotors,
  • the drive shafts of the second drive wheels are rotatably mounted in the other of the two rotors,
  • and wherein the second drive wheels are coupled to the first and the third drive wheels.

Dabei muss es sich bei dem ersten Antriebsrad und bei der Maschinenwelle nicht unbedingt um zwei separate Bauteile handeln, sondern beide können auch ein einziges Bauteil bilden, d.h. das erste Antriebsrad kann auch in die Maschinenwelle integriert sein. Gleiches gilt für das zweite bzw. dritte Antriebsrad und den jeweils damit verbundenen Rotor.In this case, 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 same applies to the second and third drive wheel and the respectively associated rotor.

Eine bezogen auf den Umfang besonders platzsparende Drehmomentübertragung ist dabei dadurch möglich, dass das erste Antriebsrad, die zweiten Antriebsräder und das dritte Antriebsrad jeweils als ein mit einer Verzahnung versehenes Kegelrad ausgebildet sind, wobei die zweiten Antriebsräder sowohl mit dem ersten Antriebsrad als auch mit dem dritten Antriebsrad jeweils ein Kegelradgetriebe bilden, und wobei die Drehachsen der Antriebswellen der zweiten Antriebsräder in einem rechten Winkel zu den Drehachsen des ersten und dritten Antriebsrades stehen.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.

Gemäß einer alternativen vorteilhaften Ausgestaltung ist das erste Antriebsrad als ein mit Innenzähnen versehenes zylindrisches Antriebsrad und sind die zweiten Antriebsräder und das dritte Antriebsrad jeweils als zylindrische, mit Außenzähnen versehene Antriebsräder ausgebildet, wobei die zweiten Antriebsräder mit dem ersten Antriebsrad und dem dritten Antriebsrad ein Planetengetriebe bilden und wobei die Drehachsen der Antriebswellen der zweiten Antriebsräder parallel zu den Drehachsen des ersten und dritten Antriebsrades verlaufen.According to an alternative advantageous embodiment, 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.

Alternativ kann auch das dritte Antriebsrad als ein mit Innenzähnen versehenes zylindrisches Antriebsrad sein und können die zweiten Antriebsräder und das erste Antriebsrad jeweils als zylindrische, mit Außenzähnen versehene Antriebsräder ausgebildet sein, wobei die zweiten Antriebsräder mit dem ersten Antriebsrad und mit dem dritten Antriebsrad ein Planetengetriebe bilden und wobei die Drehachsen der Antriebswellen der zweiten Antriebsräder parallel zu den Drehachsen des ersten Antriebsrades und des dritten Antriebsrades verlaufen.Alternatively, the third drive wheel may be a cylindrical drive wheel provided with inner teeth, and 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.

Um einen Einfluss auf den Strömungswiderstand in dem Kanal zu vermeiden, ist der Antriebsmechanismus bevorzugt in das Gehäuse integriert.In order to avoid an influence on the flow resistance in the channel, the drive mechanism is preferably integrated in the housing.

Es ist dabei auch möglich, dass mehr als zwei Rotoren in Strömungsrichtung des Fluids hintereinander angeordnet sind, wobei jeweils hintereinander angeordnete Rotoren über jeweils einen vorstehend beschriebenen Antriebsmechanismus derart miteinander gekoppelt sind, dass sie sich in jeweils entgegen gesetzter Richtung drehen, d.h. kontrarotieren.It is also possible that more than two 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.

Eine erfindungsgemäße Maschinenordnung umfasst eine vorstehend beschriebene erfindungsgemäße Strömungsmaschine und eine elektrische Maschine, wobei die elektrische Maschine einen ringförmig ausgebildeten Rotor, der mit der Maschinenwelle gekoppelt und um die gleiche Drehachse wie die Rotoren der der Strömungsmaschine drehbar gelagert ist, und einen ringförmig um den Rotor angeordneten Stator umfasst. Da die elektrische Maschine mit im Vergleich zu den Rotoren deutlich höherer Geschwindigkeit betrieben werden kann, kann der Motor im Vergleich zu konventionellen Maschinenanordnungen bei gleicher Leistung kleiner und leichter gebaut werden. Durch die ringförmige Ausbildung des Rotors der elektrischen Maschine und dessen Drehbarkeit um die gleiche Drehachse wie die der Rotoren und der Maschinenwelle der Strömungsmaschine kann die elektrische Maschine direkt, d.h. ohne ein zwischengeschaltetes Getriebe, mit der Maschinenwelle gekoppelt werden und somit auf ein Getriebe zur Kraftübertragung zwischen der elektrischen Maschine und der Strömungsmaschine verzichtet werden. Die Maschinenanordnung kann somit vergleichsweise kompakt mit einem relativ geringen Gewicht und Platzbedarf gebaut werden. Die elektrische Maschine ist dabei in Strömungsrichtung des Fluids vorzugsweise vor oder hinter den Rotoren angeordnet. Hierdurch kann der Durchmesser des Gehäuses klein gehalten werden, wodurch sich hydrodynamisch Vorteile ergeben können. Es ist aber auch möglich, dass die elektrische Maschine ringförmig um nur einen der Rotoren oder um beide Rotoren herum angeordnet ist.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. without an intermediate gear, are coupled to the machine shaft and thus dispensed with a transmission for power transmission between the electric machine and the turbomachine. 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.

Bevorzugt ist dabei der Innendurchmesser des ringförmigen Rotors der elektrischen Maschine größer oder gleich dem Innendurchmesser der ringförmigen Rotoren der Strömungsmaschine. Die elektrische Maschine weist dann einen größeren Innendurchmesser als der Kanal für das Strömen des Fluids auf und stellt somit keinen zusätzlichen Strömungswiderstand für das Fluid dar.Preferably, 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.

Von Vorteil ist dabei die elektrische Maschine in das Gehäuse der Strömungsmaschine integriert.The advantage here is the electrical machine integrated into the housing of the turbomachine.

Da sich eine erfindungsgemäße Strömungsmaschine oder Maschinenanordnung durch einen hohen Wirkungsgrad, Robustheit, Wartungsfreundlichkeit, ein relativ geringes Gewicht, einen relativ geringen Platzbedarf und gute Kavitationseigenschaften auszeichnet, eignet sie sich vor allem als Vortriebseinrichtung für schwimmende und tauchende Einrichtungen, insbesondere für Unterwasserschiffe.Since 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.

Weiterhin machen diese Vorteile eine erfindungsgemäße Strömungsmaschine oder Maschinenanordnung auch besonders geeignet zur Verwendung als horizontal und/oder vertikal verdrehbare Antriebsvorrichtung oder als Querstrahl-Antriebsvorrichtung einer schwimmenden Einrichtung, insbesondere eines Schiffes. Eine vertikale Verdrehbarkeit ist hierbei beispielsweise mittels einer kardanischen Aufhängung möglich. Aufgrund ihres relativ geringen Gewichtes kann eine derartige Antriebsvorrichtung auch aus einem Schiffsrumpf ein- und ausfahrbar und/oder um 360° drehbar ausgebildet sein.Furthermore, these advantages make a 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 °.

Eine erfindungsgemäße Strömungsmaschine oder Maschinenanordnung eignet sich aufgrund der vorgenannten Vorteile auch besonders gut zur Verwendung in einer Wasserstrahl (Waterjet)-Antriebsvorrichtung einer schwimmenden Einrichtung, insbesondere eines Schiffes.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.

Zusätzlich kann eine erfindungsgemäße Strömungsmaschine oder Maschinenanordnung auch als eine Pumpe, als ein Ventilator oder ein Verdichter verwendet werden, wobei insbesondere ihr hoher Wirkungsgrad und ihre Robustheit zum Tragen kommen.In addition, 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.

Von besonderem Vorteil kann eine erfindungsgemäße Strömungsmaschine oder Maschinenanordnung auch als eine Turbine, insbesondere in einem Flussströmungskraftwerk, verwendet werden. Eine derartige Turbine kann aber auch zur Stromerzeugung bei schwimmenden, tauchenden oder auch fliegenden Einrichtungen genutzt werden und hierzu beispielsweise aufgrund ihres relativ geringen Gewichtes aus einem Schiffsrumpf ein- und ausfahrbar und um 360° drehbar sein.Of particular advantage, a turbomachine or machine arrangement according to the invention can also be used as a turbine, in particular in a flow stream power plant. However, such 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 °.

Die Erfindung sowie weitere vorteilhafte Ausgestaltungen der Erfindung gemäß Merkmalen der Unteransprüche werden im folgenden anhand von Ausführungsbeispielen in den Figuren näher erläutert; darin zeigen:

FIG 1
einen Längsschnitt durch eine erste Ausführungsform einer erfindungsgemäße Maschinenanordnung,
FIG 2
einen Längsschnitt durch eine zweite Ausführungsform einer erfindungsgemäße Maschinenanordnung
FIG 3
eine Verwendung von erfindungsgemäßen Strömungsmaschinen bei einem Überwasserschiff und
FIG 4
eine Verwendung einer erfindungsgemäßen Strömungsmaschine bei einem Unterwasserschiff.
The invention and further advantageous embodiments of the invention according to features of the subclaims are explained in more detail below with reference to exemplary embodiments in the figures; show in it:
FIG. 1
a longitudinal section through a first embodiment of a machine arrangement according to the invention,
FIG. 2
a longitudinal section through a second embodiment of an inventive machine arrangement
FIG. 3
a use of turbomachines according to the invention in a surface vessel and
FIG. 4
a use of a turbomachine according to the invention in an underwater vessel.

FIG 1 zeigt eine Strömungsmaschine 1 mit einem düsenförmig ausgebildeten Gehäuse 2, das einen Kanal 3 für ein Strömen eines Fluids von einem Einlass 4 zu einem Auslass 5 in einer Strömungsrichtung 6 ausbildet. In dem Kanal 3 sind in der Strömungsrichtung 6 des Fluids hintereinander zwei ringförmig ausgebildete Rotoren 10, 11 angeordnet, die über nicht näher dargestellte Lager in zueinander entgegen gesetzter Richtung um eine gemeinsame Drehachse 7 drehbar in dem Gehäuse 2 gelagert sind. Die Rotoren 10, 11 weisen jeweils eine Ringinnenseite 12 und einen Ringaußenseite 13 auf. An der Ringinnenseite 12 sind in Umfangsrichtung der Rotoren 10, 11 gleichmä-βig verteilt jeweils Schaufeln oder Flügel 14 angeordnet, die mit dem jeweiligen Rotor 10, 11 mitrotieren. Die Rotoren 10, 11 sind über nicht näher dargestellte Lager z.B. mittels ihrer Ringaußenseite 13 axial und radial drehbar in dem Gehäuse 2 gelagert. Die Schaufeln 14 sind lösbar an den Rotoren 10, 11 befestigt, so dass sie ausgetauscht werden können. 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. In the channel 3, 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.

Unter der Ringaußenseite 13 wird hierbei die Seite eines Rotors 10, 11 verstanden, die durch die radial äußere Begrenzungsfläche des Rotors 10, 11 definiert ist, und unter der Ringinnenseite 12 wird die Seite eines Rotors 10, 11 verstanden, die durch die radial innere Begrenzungsfläche des Rotors 10, 11 definiert ist.Under the ring outer side 13 in this case the side of a rotor 10, 11 is understood, which is defined by the radially outer boundary surface of the rotor 10, 11, and below the ring inner side 12 is the side of a rotor 10, 11 understood by the radially inner boundary surface of the rotor 10, 11 is defined.

Die Strömungsmaschine 1 umfasst weiterhin eine Maschinenwelle 15 und einen Antriebsmechanismus 16, der die Maschinenwelle 15 mit den zwei Rotoren 10, 11 verbindet und der eine Drehbewegung der Maschinenwelle 15 in zueinander entgegen gesetzt gerichtete Drehbewegungen der Rotoren 10, 11 umwandelt oder umgekehrt. Sowohl die Maschinenwelle 15 als auch der Antriebsmechanismus 16 (welcher prinzipiell ein Differentialgetriebe darstellt) sind ringförmig ausgebildet. Die Maschinenwelle 15 ist hierbei über nicht näher dargestellte Lager um die gleiche Achse 7 wie die Rotoren 10, 11 drehbar in dem Gehäuse 2 gelagert.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.

Der Antriebsmechanismus 16 umfasst ein erstes Antriebsrad 21, mehrere in Umfangsrichtung des ringförmigen Antriebsmechanismus 16 gleichmäßig verteilt angeordnete zweite Antriebsräder 22 mit jeweils einer um eine Drehachse 28 drehbaren Antriebswelle 24, und ein drittes Antriebsrad 23. Das erste Antriebsrad 21 ist dabei um die gleiche Drehachse 7 wie die Rotoren 10, 11 und die Maschinenwelle 15 drehbar und hierzu drehfest mit der Maschinenwelle 15 verbunden. Das dritte Antriebsrad 23 ist ebenfalls um die gleiche Drehachse 7 wie die Rotoren 10, 11 und die Maschinenwelle 15 drehbar und hierzu drehfest mit dem Rotor 11 verbunden. Die Antriebswellen 24 der zweiten Antriebsräder 22 sind drehbar in dem Rotor 10 gelagert. Somit sind in Strömungsrichtung 6 des Fluids durch den Kanal 3 das erste Antriebsrad 21, ein jeweils zweites Antriebsrad 22 und das dritte Antriebsrad 23 hintereinander angeordnet. Zur Drehmomentübertragung sind die zweiten Antriebsräder 22 jeweils mit dem ersten Antriebsrad 21 und mit dem dritten Antriebsrad 23 gekoppelt. Der Antriebsmechanismus 16 und die Rotoren 10, 11 sind dabei über Dichtungen 17 gegenüber dem Kanal 3 abgedichtet.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. Thus, in the flow direction 6 of the fluid through the channel 3, the first drive wheel 21, a respective second drive wheel 22 and the third drive wheel 23 are arranged one behind the other. For torque transmission, 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.

Bei der in FIG 1 gezeigten Ausführungsform der Erfindung sind zur Kopplung der Antriebsräder 21, 22, 23 das erste Antriebsrad 21, die zweiten Antriebsräder 22 und das dritte Antriebsrad 23 jeweils als ein mit einer Verzahnung versehenes Kegelrad ausgebildet, wobei die zweiten Antriebsräder 22 sowohl mit dem ersten Antriebsrad 21 als auch mit dem dritten Antriebsrad 23 jeweils ein Kegelradgetriebe bilden, bei dem das Antriebsrad 22 das Ritzel und die Antriebsräder 21 und 23 jeweils das Tellerrad bilden. Die Antriebswellen 24 der zweiten Antriebsräder 22 sind dabei in der Ringaußenseite 13 des Rotors 10 drehbar gelagert und ihre Drehachsen 28 stehen in einem rechten Winkel zu der Drehachse 7 des ersten Antriebsrades 21 und des dritten Antriebsrades 23. Dabei greift sowohl die Verzahnung des ersten Antriebsrades 21 als auch die Verzahnung des dritten Antriebsrades 23 in die Verzahnungen der zweiten Antriebsräder 22.At the in 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

Grundsätzlich kann eine Drehmomentübertragung zwischen den Antriebsrädern statt über eine Verzahnung natürlich auch über eine Reibschlussverbindung erfolgen. Weiterhin ist es auch möglich, dass das erste Antriebsrad 21 und die Maschinenwelle 15 keine separaten Bauteile, sondern ein einziges Bauteil bilden, d.h. dass die Verzahnung des ersten Antriebsrades 21 direkt auf der Maschinenwelle 15 aufgebracht ist. In entsprechender Weise können auch der zweite Rotor 11 und das dritte Antriebsrad 23 ein einziges Bauteil bilden, d.h. die Verzahnung des dritten Antriebsrades 23 kann direkt auf dem Rotor 11 aufgebracht sein.In principle, a torque transmission between the drive wheels instead of via a toothing course, via a frictional connection. Furthermore, it is also possible that the 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. Likewise, the 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.

Der Antriebsmechanismus 16 hat die Funktion eines Differentialgetriebes. Er kann zum einen für eine Kraftübertragung von der Maschinenwelle 15 zu den Rotoren 10, 11 genutzt werden. Eine Drehbewegung der Maschinenwelle 15 wird dann durch den Antriebsmechanismus 16 in zueinander entgegen gesetzt gerichtete Drehbewegungen, d.h. eine Kontrarotation, der Rotoren 10, 11 umgewandelt. Dreht sich die Maschinenwelle 15 beispielsweise in Richtung des Pfeils 25, so bewegt sie den ersten Rotor 10 in die entgegen gesetzt gerichtete, durch den Pfeil 26 symbolisierten Richtung und den zweiten Rotor 11 in die zu dem Rotor 10 wiederum entgegen gesetzte Richtung, d.h. in Richtung der Maschinenwelle 15, wie durch den Pfeil 27 symbolisiert ist, mit.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.

Der Antriebsmechanismus 16 kann aber auch für eine Kraftübertragung von den Rotoren 10, 11 zu der Maschinenwelle 15 genutzt werden. Entgegengesetzt gerichtete Drehbewegungen der Rotoren 10, 11 werden durch den Antriebsmechanismus 16 dann in eine Drehbewegung der Maschinenwelle 15 umgewandelt.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.

In beiden Fällen ist die Drehgeschwindigkeit (bzw. Winkelgeschwindigkeit) der Rotoren 10, 11 je nach gewählter Übersetzung signifikant kleiner als die Drehgeschwindigkeit (bzw. Winkelgeschwindigkeit) der Maschinenwelle 15.In both cases, 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.

Die Strömungsmaschine 1 kann somit sowohl als Arbeitsmaschine verwendet werden, die Arbeit an einem durch den Kanal 3 strömenden Fluid leistet, oder als eine von einem in dem Kanal 3 strömenden Fluid angetriebene Kraftmaschine verwendet werden, die mechanische Leistung an der Maschinenwelle 15 abgibt.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.

Durch den zweiten Rotor 11 kann der verlustbehaftete Drall des Abstromes des ersten Rotors 10, d.h. Strömungskomponenten des Fluids, die von der Strömungsrichtung 6 abweichen (z.B. radiale oder zirkulare Strömungskomponenten), zumindest teilweise wieder in die Hauptströmungsrichtung umgelenkt und somit in Schub bzw. aufnehmbares Drehmoment eines nachfolgenden Rotors umgewandelt werden. Durch den zweiten Rotor 11 wird somit ein zumindest teilweiser Momentenausgleich bewirkt. Durch einen derartigen mechanischen Momentenausgleich kann ein besonders guter Wirkungsgrad einer Strömungsmaschine erzielt werden.By the second rotor 11, the lossy spin of the effluent of the first rotor 10, i. Flow components of the fluid that deviate from the flow direction 6 (for example, radial or circular flow components) are at least partially redirected in the main flow direction and thus converted into thrust or torque of a subsequent rotor. By the second rotor 11 thus at least partial torque compensation is effected. By such a mechanical torque compensation, a particularly good efficiency of a turbomachine can be achieved.

Da die Wandlung von Drehzahl zu Drehmoment erst kurz vor der leistungsübertragenden Komponente von der Mechanik zum Fluid erfolgt, kann die gesamte Strömungsmaschine 1 mit relativ wenig Gewicht ausgeführt werden.Since the conversion of speed to torque is only shortly before the power-transmitting component of the mechanism to the fluid, the entire turbomachine 1 can be performed with relatively little weight.

Bei einer besonders vorteilhaften Maschinenanordnung 35 ist die Strömungsmaschine 1 mit einer elektrischen Maschine 30 gekoppelt. Die elektrische Maschine 30 umfasst einen ringförmig ausgebildeten Rotor 31 mit einem nicht näher dargestellten Erregersystem (z.B. einer Wicklungsanordnung oder einer Anordnung von Permanentmagneten), der drehfest mit der Maschinenwelle 15 verbunden ist und mittels nicht näher dargestellter Lager um die gleiche Drehachse 7 wie die Rotoren 10, 11 der Strömungsmaschine 1 drehbar in dem Gehäuse 2 gelagert ist. Die Maschinenwelle 15 und der Rotor 31 der elektrischen Maschine 30 können dabei auch eine einzige bauliche Einheit bilden, d.h. das rotorseitige Erregersystem der elektrischen Maschine 30 kann auch direkt auf der Maschinenwelle 15 angeordnet sein.In a particularly advantageous machine arrangement 35, 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.

Die elektrische Maschine 30 umfasst weiterhin einen ringförmigen Stator 32, der in das Gehäuse 2 integriert und drehfest mit dem Gehäuse 2 verbunden ist. Der Stator 32 weist ebenfalls ein nicht näher dargestelltes Erregersystem auf, das mit dem Erregersystem des Rotors 31 elektromagnetisch wechselwirkt. Der Stator 32 ist dabei in radialer Richtung in Bezug auf die Drehachse 7 vor dem Rotor 31 angeordnet. Bei der elektrischen Maschine 30 handelt es sich somit um eine außen laufende Maschine, d.h. der Rotor 31 ist ringförmig um den Stator 32 angeordnet. Die elektrische Maschine 30 ist hierbei in Strömungsrichtung 6 des Fluids vor dem ersten Rotor 10 angeordnet.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.

Die elektrische Maschine 30 kann zum einen als getriebeloser Direktantrieb zum Antrieb der Maschinenwelle 15 und somit der Rotoren 10, 11 genutzt werden. Die elektrische Maschine 30 kann aber auch als von den Rotoren 10, 11 und der Maschinenwelle 15 angetriebener Generator verwendet werden.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.

Alternativ kann die Strömungsmaschine natürlich auch über anderweitige dem Fachmann geläufige Mittel (z.B. über ein Getriebe) durch eine elektrische Maschine oder eine Verbrennungskraftmaschine angetrieben werden, wobei diese Maschine nicht zwangsläufig ringförmig ausgebildet sein muss, sondern auch eine Vollwelle mit einer Drehachse aufweisen kann, die parallel oder in einem Winkel zur Drehachse 7 der Rotoren 10, 11 steht.Alternatively, the 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.

Die in FIG 1 dargestellte Maschinenanordnung 35 ist besonders widerstandsarm für das durch den Kanal 3 strömende Fluid ausgebildet. Hierzu ist die Strömungsmaschine 1 frei von einem Bauteil (z.B. einer zentralen Welle), das entlang der Drehachse 7 der Rotoren 10, 11 durch diese hindurch verläuft. Au-βerdem sind die Maschinenwelle 15, der Stator 31 und der Rotor 32 der elektrischen Maschine 30 in das Gehäuse 2 der Strömungsmaschine 1 integriert. Weiterhin sind die ringförmigen Rotoren 10, 11 derart ausgebildet, dass der Durchmesser der Ringinnenseite 12 (ggf. einschließlich der Dicke einer auf der Ringinnenseite 12 angeordneten Dichtung 17) dem Durchmesser des Kanals 3 unmittelbar vor dem jeweiligen Rotor 10, 11 entspricht. Der ringförmige Rotor 10, 11 ist hierzu in dem Gehäuse 2 versenkt angeordnet bzw. bildet mit seiner Ringinnenseite 12 (ggf. einschließlich einer auf der Ringinnenseite 12 angeordneten Dichtung 17) die äußere Begrenzungsfläche des Kanals 3 im Bereich des Rotors 10, 11, wobei diese äußere Begrenzungsfläche mit der angrenzenden, von dem Gehäuse 2 gebildeten äußeren Begrenzungsfläche fluchtet. Die ringförmigen Rotoren 10, 11 selbst stellen somit keinen Strömungswiderstand für das Fluid dar.In the FIG. 1 shown machine assembly 35 is particularly resistant to resistance to the fluid flowing through the channel 3 formed. For this purpose, 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. In addition, 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. Furthermore, 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.

Der Innendurchmesser des ringförmigen Rotors 31 der elektrischen Maschine 30 ist größer als der Innendurchmesser der ringförmigen Rotoren 10, 11 der Strömungsmaschine 1. Der Innendurchmesser des ringförmigen Stators 32 der elektrischen Maschine 30 ist (einschließlich der Dicke einer ggf. auf der Ringinnenseite 12 angeordneten Dichtung 17) gleich dem Durchmesser des Kanals 3 im Bereich der elektrischen Maschine 30 und bildet somit die äußere Begrenzungsfläche des Kanals 3 im Bereich der elektrischen Maschine 1, wobei diese äußere Begrenzungsfläche mit der angrenzenden, von dem Gehäuse 2 sowie den Rotoren 10, 11 gebildeten äußeren Begrenzungsfläche fluchtet. Auch die elektrische Maschine 30 stellt somit keinen Strömungswiderstand für das Fluid dar.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.

Eine in FIG 2 gezeigte Strömungsmaschine 40 unterscheidet sich von der in FIG 1 gezeigten Strömungsmaschine 1 dadurch, dass erste Antriebsrad 41 als ein mit Innenzähnen versehenes zylindrisches Antriebsrad und die zweiten Antriebsräder 42 und das dritte Antriebsrad 43 jeweils als zylindrische, mit Außenzähnen versehene Antriebsräder ausgebildet sind. Die zweiten Antriebsräder 42 bilden dabei mit dem ersten Antriebsrad 41 und mit dem dritten Antriebsrad 43 ein Planetengetriebe mit einem Hohlrad, einem Sonnenrad und mehreren dazwischen angeordneten Planetenrädern, wobei das erste Antriebsrad 41 das Hohlrad, das dritte Antriebsrad 43 das Sonnenrad und die zweiten Antriebsräder 42 die Planetenräder darstellen. Dabei greift sowohl die Verzahnung des ersten Antriebsrades 41 als auch die Verzahnung des dritten Antriebsrades 43 in die Verzahnungen der zweiten Antriebsräder 42.An in FIG. 2 shown 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. In this case, 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.

Die Antriebswellen 44 der zweiten Antriebsräder 42 sind hierbei auf der dem Rotor 10 zugewandten Stirnseite 45 des Rotors 11 angeordnet und weisen Drehachsen 48 auf, die parallel zu der Drehachse 7 des ersten Antriebsrades 41 und des dritten Antriebsrades 43 verlaufen. Unter der Stirnseite eines Rotors wird hierbei die in axialer Richtung, d.h. in Richtung seiner Drehachse 7, äußere Begrenzungsfläche verstanden.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. In this case, 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.

Grundsätzlich kann eine Drehmomentübertragung zwischen den Antriebsrädern 41, 42, 43 statt über eine Verzahnung natürlich auch über eine Reibschlussverbindung erfolgen.In principle, a torque transmission between the drive wheels 41, 42, 43 instead of via a toothing, of course, via a frictional connection.

Weiterhin ist es auch möglich, dass das erste Antriebsrad 41 und die Maschinenwelle 15 keine separaten Bauteile, sondern ein einziges integriertes Bauteil bilden, d.h. dass die Verzahnung des ersten Antriebsrades 41 direkt auf der Maschinenwelle 15 aufgebracht ist. In entsprechender Weise bilden auch der Rotor 10 und das dritte Antriebsrad 43 ein einziges integriertes Bauteil, d.h. die Verzahnung des dritten Antriebsrades 43 ist direkt auf dem Rotor 10 aufgebracht.Furthermore, it is also possible that the 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. Similarly, 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.

FIGUR 3 zeigt eine Längsschnittdarstellung eines Schiffes 50 vom Typ "Korvette", bei dem eine erste Maschinenanordnung 35 bestehend aus einer Strömungsmaschine 1 und einer elektrischen Maschine 30 gemäß FIG 1 oder 2 mit großer Leistung als eine horizontal verdrehbare Antriebsvorrichtung 51 am Heck 52 des Schiffes verwendet wird. Die Maschinenanordnung 35 ist hierbei drehfest an einem Schaft 53 befestigt, der horizontal drehbar in dem Schiff 50 gelagert ist. 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.

Für bestimmte Schiffstypen kann statt einer horizontal verdrehbaren Antriebsvorrichtung 51 auch eine vertikal verdrehbare Antriebsvorrichtung mit einer Maschinenanordnung 35 am Heck 52 des Schiffes 50 angeordnet sein.For certain types of ship, instead of a horizontally rotatable drive device 51, a vertically rotatable drive device with a machine arrangement 35 can be arranged at the stern 52 of the ship 50.

Außerdem wird eine zweite Maschinenanordnung 35 gemäß FIG 1 oder 2 mit mittlerer Leistung in einer Wasserstrahl (Waterjet) -Antriebsvorrichtung 54 verwendet, die am Schiffsboden 55 angeordnet ist.In addition, 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.

Weiterhin wird eine Maschinenanordnung 35 gemäß FIG 1 mit kleinerer Leistung in einer im Bug 56 des Schiffes 50 angeordneten Querstrahlruder-Antriebsvorrichtung 57 verwendet.Furthermore, a machine assembly 35 according to FIG. 1 with lower power in a bow 56 of the ship 50 arranged transverse thruster drive device 57 used.

An Bord des Schiffes 50 befinden sich ein oder mehrere Generatoren, vorzugsweise Dieselgeneratoren, oder andere Stromquellen oder Energiespeicher, wie z.B. Batterien und/oder Brennstoffzellen, die die als Elektromotor betriebenen elektrischen Maschinen 30 der Maschinenanordnungen 35 mit Strom versorgen.Onboard the ship 50 are one or more generators, preferably diesel generators, or other power sources or energy storage devices such as diesel generators. Batteries and / or fuel cells, which supply the operated as an electric motor electric machines 30 of the machine assemblies 35 with electricity.

Für den dargestellten Schiffstyp "Korvette" mit seiner Typverdrängung von ca. 2000 to und einer angenommenen Maximalgeschwindigkeit oberhalb von 35 kn besteht in der dargestellten Ausführungsform der Antrieb aus zwei horizontal verdrehbaren Antriebsvorrichtung 51 und zwei Wasserstrahl (Waterjet) - Antriebsvorrichtungen 54.For the illustrated type of vessel "Corvette" with its type displacement of about 2000 tons and an assumed maximum speed above 35 kn, in the illustrated embodiment the drive consists of two horizontally rotatable drive devices 51 and two water jet (waterjet) drive devices 54.

Die elektrischen Maschinen 35 können dabei zur Energierückgewinnung auch als Generatoren betrieben werden.The electrical machines 35 can also be operated as generators for energy recovery.

FIG 4 zeigt ein Unterwasserschiff 60, bei dem eine Maschinenanordnung 35 gemäß FIG 1 oder 2 als Vortriebseinrichtung 61 am Heck 62 des Unterwasserschiffes 60 verwendet wird. Die Maschinenanordnung 35 ist dabei mittels einer Halterung 63 am Heck 62 des Schiffes befestigt. Da bei der Maschinenanordnung 35 die Rotorschaufeln von dem Gehäuse umgeben sind, zeichnet sich der Antrieb durch eine besonders geringe Geräuscherzeugung aus, was oft insbesondere für Unterwasserschiffe wichtig ist. Die Stromzuführung zu der elektrischen Maschine der Maschinenanordnung 35 kann dabei über die Halterung 63 erfolgen. 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.

Auch hier befinden sich an Bord des Unterwasserschiffes 60 ein oder mehrere nicht näher dargestellte Generatoren, vorzugsweise Dieselgeneratoren, oder andere Stromquellen oder Energiespeicher, wie z.B. Batterien und/oder Brennstoffzellen, die die als Elektromotor betriebene elektrische Maschine der Maschinenanordnung 35 mit Strom versorgen.Again, 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.

Claims (16)

  1. Continuous-flow machine (1, 40) having
    - at least two rotors (10, 11) which are mounted such that they can rotate about a rotation axis (7) in mutually opposite directions and on which blades (14) or vanes are arranged,
    - a machine shaft (15) which is mounted such that it can rotate, and
    - a drive mechanism (16) which connects the machine shaft (15) to the at least two rotors (10, 11) and converts a rotary movement of the machine shaft (15) to rotary movements of the rotors (10, 11) in mutually opposite directions, or vice versa, and having a housing (2) which forms a channel (3) for a flow of a fluid, wherein
    - the rotors (10, 11) are arranged one behind the other in the channel (3) in the flow direction (6) of the fluid,
    - the rotors (10, 11) are annular and are mounted such that they can rotate in the housing (2),
    and
    - the annular rotors (10, 11) each have an annulus inner face (12) and an annulus outer face (13), wherein the blades (14) or vanes are arranged on the annulus inner face (12), characterized in that the machine shaft (15) is annular and is mounted such that it can rotate in the housing (2).
  2. Continuous-flow machine (1, 40) according to Claim 1, characterized in that the machine has no component which runs along the rotation axis (7) of the rotors (10, 11) and through them.
  3. Continuous-flow machine (1, 40) according to one of the preceding claims, characterized in that the drive mechanism (16) is likewise annular.
  4. Continuous-flow machine (1, 40) according to Claim 3, characterized in that the drive mechanism (16) has a first drive wheel (21, 41), a plurality of second drive wheels (22, 42) which are arranged distributed in the circumferential direction of the annular drive mechanism (16) and each have a drive shaft (24, 44) which can rotate about a rotation axis (28, 48) and a third drive wheel (23, 43) wherein
    - the first drive wheel (21, 41) is connected to the machine shaft (15) such that they rotate together,
    - the third drive wheel (23, 43) is connected to a first of the two rotors (10 or 11) such that they rotate together,
    - the drive shafts (24, 44) of the second drive wheels (22, 42) are mounted such that they can rotate in the other of the two rotors (11 or 10), and wherein the second drive wheels (22, 42) are coupled to the first drive wheel (21, 41) and to the third drive wheel (23, 43).
  5. Continuous-flow machine (1, 40) according to Claim 4, characterized in that the first drive wheel (21), the second drive wheels (22) and the third drive wheel (23) are each in the form of a bevel gear which is provided with a tooth system, wherein the second drive wheels (22), both with the first drive wheel (21) and with the third drive wheel (23), each form a bevel-gear transmission, and wherein the rotation axes (28) of the drive shafts (24) of the second drive wheels (22) are at right angles to the rotation axes (7) of the first drive wheel (21) and of the third drive wheel (23).
  6. Continuous-flow machine (1, 40) according to Claim 4, characterized in that the first drive wheel (41) is a cylindrical drive wheel provided with internal teeth and the second drive wheels (42) and the third drive wheel (43) are each cylindrical drive wheels provided with external teeth, wherein the second drive wheels (42), together with the first drive wheel (41) and the third drive wheel (43) in each case form an epicyclic transmission, and wherein the rotation axes (48) of the drive shafts (44) of the second drive wheels (42) run parallel to the rotation axes (7) of the first drive wheel (41) and of the third drive wheel (43).
  7. Continuous-flow machine (1, 40) according to Claim 4, characterized in that the third drive wheel (41) is a cylindrical drive wheel provided with internal teeth and the second drive wheels (42) and the first drive wheel (43) are each cylindrical drive wheels provided with external teeth, wherein the second drive wheels (42), together with the first drive wheel (41) and the third drive wheel (43), form an epicyclic transmission, and wherein the rotation axes (48) of the drive shafts (44) of the second drive wheels (42) run parallel to the rotation axes (7) of the first drive wheel (41) and of the third drive wheel (43).
  8. Continuous-flow machine (1, 40) according to one of the preceding claims, characterized in that the drive mechanism (16) is integrated in the housing (2).
  9. Machine arrangement (35) comprising a continuous-flow machine (1, 40) according to one of the preceding claims and an electrical machine (30), characterized in that the electrical machine (30) has an annular rotor (31) which is coupled to the machine shaft (15) and is mounted such that it can rotate about the same rotation axis (7) as the rotors (10, 11) of the continuous-flow machine (1, 40), and a stator (32) which is arranged in an annular shape around the rotor (31).
  10. Machine arrangement (35) according to Claim 9, characterized in that the internal diameter of the annular rotor (31) of the electrical machine (30) is greater than or equal to the internal diameter of the annular rotors (10, 11) of the continuous-flow machine (1, 40).
  11. Machine arrangement (35) according to Claim 9 or 10, characterized in that the electrical machine (30) is integrated in the housing (2) of the continuous-flow machine (1, 40).
  12. Use of the continuous-flow machine (1, 40) or machine arrangement (35) according to one of the preceding claims as a propulsion device (61) for floating or diving devices, in particular submarines (60).
  13. Use of the continuous-flow machine (1, 40) or of the machine arrangement (35) according to one of Claims 1 to 11 in a drive apparatus (51) which can rotate horizontally and/or vertically, or in a lateral-jet thruster drive apparatus (57) of a floating device, in particular of a marine vessel (50).
  14. Use of the continuous-flow machine (1, 40) or of the machine arrangement (35) according to one of Claims 1 to 11 in a water-jet drive apparatus (54) for a floating device, in particular a marine vessel (50).
  15. Use of the continuous-flow machine (1, 40) or of the machine arrangement (35) according to one of Claims 1 to 11 as a pump, a fan or a compressor.
  16. Use of the continuous-flow machine (1, 40) or of the machine arrangement (35) according to one of Claims 1 to 11 as a turbine, in particular for electricity generation in a floating or diving device, or in a hydroelectric power station.
EP09753819.3A 2008-05-27 2009-05-20 Turbo-machine having at least two counter-rotatable rotors and having mechanical torque compensation Active EP2279112B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008025210 2008-05-27
PCT/EP2009/056156 WO2009144164A1 (en) 2008-05-27 2009-05-20 Turbo-machine having at least two counter-rotatable rotors and having mechanical torque compensation

Publications (2)

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

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EP09753819.3A Active EP2279112B1 (en) 2008-05-27 2009-05-20 Turbo-machine having at least two counter-rotatable rotors and having mechanical torque compensation

Country Status (6)

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US (1) US8487466B2 (en)
EP (1) EP2279112B1 (en)
KR (1) KR101205147B1 (en)
DK (1) DK2279112T3 (en)
ES (1) ES2409113T3 (en)
WO (1) WO2009144164A1 (en)

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Also Published As

Publication number Publication date
EP2279112A1 (en) 2011-02-02
KR20120096957A (en) 2012-09-03
US8487466B2 (en) 2013-07-16
ES2409113T3 (en) 2013-06-25
KR101205147B1 (en) 2012-11-26
DK2279112T3 (en) 2013-07-29
US20110074158A1 (en) 2011-03-31
WO2009144164A9 (en) 2010-05-20
WO2009144164A1 (en) 2009-12-03

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