DE102011000420B4 - Turbo-generator unit - Google Patents

Abstract

Turbo-generator unit (1) comprising a drive device (2) designed as a turbine (2) with a drum (8) and a generator (4) with a rotor (10) and a stator (15), the turbine ( 2) and the generator (4) are arranged integrated into one another and have a common central axis (18), and wherein the turbine (2) in external rotor construction and the generator (4) are formed in internal rotor construction, characterized in that the rotor (10) the generator (4) is arranged coaxially around the drum (8) of the turbine (2) and has a hollow cylindrical outer wall and an inner wall corresponding to the outer shape of the drum (8) of the turbine (2), the inner wall and the outer wall being spaced from one another , an annular gap (19) forming, are arranged.

Description

The invention relates to a turbo-generator unit with a high-speed drive machine and a high-speed generator in integral design.

In conjunction with the increased use of renewable energies and the use of industrial waste heat, increasingly consumer-oriented and thus decentralized units are needed to generate electricity and heat. The decentralized generating units have outputs ranging from a few kilowatts to a few megawatts. The use of steam turbine plants with back pressure turbines is widespread. These steam turbine systems, also referred to as steam turbine sets, are based on a mature developed and reliable technology for commercial use.
However, for cost reasons, there is a significant discrepancy between the diffusion of steam turbine sets of smaller power and their level of development. The steam turbine sets of low power have a low conversion efficiency and are manufactured in a material-intensive heavy duty construction. In the event of fluctuations in the heat load, that is to say in the case of fluctuations in the steam demand, the steam mass flow is changed by the backpressure control in order to ensure a constant vapor pressure at the outlet of the turbine. The back pressure control acts on the turbine control valves. At constant turbine speed, however, the mass flow change leads to an increase in the flow losses within the turbine and thus to a reduction of the already low effective efficiency, which is only in the range of 50% to 65% due to the significant losses by fission and secondary flows as well as partial loading.

As the state of the art, transmission steam turbine sets of constant speed are known in the resolved design of turbine and generator. Under the resolved design is the spatially separated arrangement of turbine and generator to understand, with the shafts of the turbine and generator are mechanically coupled together and form a shaft train.

1 shows a conventional transmission-steam turbine concept with a designed as a steam turbine drive device 2 , a gearbox 3 and a generator 4 , The steam turbine 2 is in the flow direction 5 steamed. The steam has an inlet pressure of less than 130 bar and an inlet temperature below 530 ° C. The outlet pressure of the steam from the turbine 2 is dependent on the use of waste heat. About the transmission 3 is the constant speed of the shaft of the steam turbine 2 converted into a likewise constant, lower speed at which the generator 4 running. For high-speed turbines 2 In the power range from 150 kW to 10,000 kW, speeds up to 23,000 rpm are achieved via the gearbox 3 be reduced to 1,500 1 / min and 3,000 1 / min, respectively. As steam turbines 2 Single-stage axial turbines with low internal efficiencies are used, which are also operated partially powered at powers below 500 kW. For outputs from 1 MW to 2 MW, the turbines become 2 used in the so-called twin construction and / or tandem construction. In twin construction, a high-pressure turbine and a low-pressure turbine are designed with two shafts and connected in series on the steam side. The generator 4 is about a gearbox 3 driven. In the tandem construction, two identical turbines are operated in parallel, which together form a generator 4 drive.
The generator 4 generated electrical energy is in the electrical network 6 fed.

In addition to the constant-speed gearbox steam turbine sets, gearless steam turbine sets in the dissolved design of turbine and high-speed generator with load-dependent speed variability are also known. However, these steam turbine sets are still in the development phase.

The known in the art transmission-Dampfurbosätzen is own, to be executed in material-intensive heavy construction and have a low by the transmission and the generator compared to the turbine speed. The conventional transmission steam turbine sets require the design of an oil system for transmission, bearings and the valve actuators. As a result of operating at a constant speed occur especially at part load conditions, that is, steam demand fluctuations, increased losses.
The trained in dissolved construction of turbine and generator steam turbine sets also claim a large amount of space.

In the prior art integral turbine-generator arrangements are described which reduce the space requirement of the turbo sets and thus achieve a more compact design.
From the US 2 984 751 A shows an integral turbine-generator unit in which the turbine is designed as a run with air or combustion gas two-stage gas turbine. The first turbine stage is provided as the primary drive of the rotor with integrated generator. Within the second stage producing a lower torque than the first stage, the air is relieved to a lower pressure or lower temperature prior to exiting the unit as cooling air for a common turbine-generator hollow shaft to be usable. The gas flows in the axial direction through the first, outer stage before it is deflected by an angle of 180 ° and axially guided by the second, internally arranged stage and an annular gap formed between a central drive shaft and the hollow shaft. The flow guide was chosen for reasons of Axialschubausgleichs.

The gas used to drive the turbine is thus used simultaneously for the generator cooling. The compact design of the turbine-generator unit is also intended to make it possible to use it as an auxiliary power supply for aircraft.

Also in the US 3 148 282 A An integral turbine generator set is described, which is designed to shorten the length of the turbo generator coupled turbine set and thus reduce vibrations and noises. The intended also for operation with steam turbine turbine generator set is operated at low speeds.

In the prior art, however, no, for example, on the US 2 984 751 A or the US 3 148 282 A based applications of turbine generator units known, which could also be related to the feasibility of the published arrangements.

In the US 5,376,827 A a generic unit with a turbine and a generator is disclosed. The turbine has counter rotating outer and inner rotor blades extending from respective outer and inner rotors. The outer and inner rotors are supported on stationary frames. The electric generator has a field core for generating magnetic poles, which is arranged coaxially with an armature in order to generate electrical energy relative to each other in relative rotation. The field core and the armature are arranged coaxially and radially outward to the outer rotor. The field core or anchor is fixedly connected to the outer rotor, while the other is firmly connected to the frame.

Object of the present invention is to provide a compact turbo-generator unit having a reduced to a minimum weight and a minimum space requirement. The turbo-generator unit is to convert the energy under minimum load conditions with minimal losses. The turbo-generator unit should be low-maintenance and therefore less expensive to operate.

The object is achieved by a turbo-generator unit according to the invention, which comprises a drive device designed as a turbine and a generator with a rotor and a stator. The turbine and the generator are integrated with each other and have a common center axis.
According to the concept of the invention, the turbine are designed in external rotor construction and the generator in internal rotor construction.
In the turbine, the flow energy of the fluid flowing through the turbine is converted into rotational energy. In the internal rotor design turbine, the rotational energy is tapped using a arranged on an axis, formed of blades paddle wheel, wherein the axis is rotated with the paddle wheel in rotation. In comparison, in the outer rotor design turbine, in which the blades are fixed to an outer circumference of the turbine, the rotational energy is consequently dissipated at the outer circumference of the turbine. The outer circumference rotates.
In the generator in internal rotor design of the moving part, which is also referred to as a rotor or rotor, arranged in the interior of the generator and is enclosed by the stationary part, which is also referred to as the stator of the generator.
As a result, the generator, comprising a rotor and a stator, can advantageously be arranged on the outer circumference of the turbine.
The design of the turbine in external rotor design and the generator in internal rotor design allows direct power transmission from the moving turbine part to the rotor of the generator with minimal space requirements in axial and radial extent. In addition, the bending dynamic and rotationally dynamic properties of the power transmission over other arrangements, such as the internal rotor internal rotor construction or the external rotor outer rotor construction of turbine and generator, improved.
Due to the arrangement of the stator of the generator on the outside of the turbo-generator unit, the heat loss generated at this point is safe and can be discharged with little technical effort, since the stator is disposed on the turbine side facing away from the generator and thus on the side with lower temperature , The stator generates most of the heat lost inside the generator.
In addition, the arrangement of the stator on the outside allows an uncomplicated Spannungsausleitung from the turbo-generator unit or a simple voltage connection to a machine converter, since no additional enclosure for steam supply and / or steam discharge is formed. In addition, no critical sealing gap is formed in the winding space of the stator to the high-pressure part of the steam of the turbine.

According to a preferred embodiment of the invention, the turbine of the turbo-generator unit as an axial steam turbine and multi-stage educated. Each stage has a guide grid and a playpen. Under the playpen, which is also referred to as a blade grid, the settlement of the circumferentially arranged blades and their projection is to be understood in the plane. In each case, a guide grid arranged on a drum and a blade grid designed as a ring form one stage of the multi-stage turbine. Under a ring or a series is a uniformly spaced arrangement to understand in the radial direction of the inner wall of the rotor projecting blades. The rotor can be advantageously driven via the rotor blades and set into rotational movement about the central axis. The guide gratings, which have a multiplicity of guide vanes, are arranged in full on an advantageously circular-cylindrical or truncated-cone-shaped drum.

According to a first embodiment of the invention, the drum is fixed. As the vanes are fixed around the circumference of the drum, a portion of the material-bound energy of the fluid is converted into kinetic energy, such that the flow at the exit has a higher velocity and an angular momentum. As a result, act on the blades forces in the circumferential direction. It comes to rotation. In the multi-stage embodiment of the turbine, the vanes and blades are arranged in the flow direction of the fluid in alternating order.

According to a second embodiment of the invention, the drum with the vanes arranged on the circumference is arranged to be movable in a rotary manner counter to the direction of rotation of the moving blades. The drum with guide vanes is therefore likewise designed to be rotatable in such a way that the guide vanes and the vane grille of each stage rotate in opposite directions relative to one another. In this way, with the same power of the turbine, the number of stages compared to the design with a fixed guide grid can be reduced. This makes the turbine and the turbo-generator unit even more compact and space-saving.

According to the invention, the rotor of the generator is arranged coaxially around the drum of the turbine and has a hollow-cylindrical outer wall as well as an inner wall corresponding to the outer shape of the drum and the guide gratings arranged thereon. The drum of the turbine and the rotor of the generator are arranged having a common center axis. As a result of the expansion of the fluid during the expansion, the flow cross-sectional area, in particular the height or the length of the rotor blades, increases in the direction of flow of the fluid through the multi-stage turbine. The flow space inside the turbine is cone-shaped.

In a drum having a circular cylindrical outer shape and increasing in diameter vanes and blades, the inner wall of the rotor is frusto-conical and thus corresponds to the outer shape of the drum and the vanes arranged thereon. Since the density of the fluid changes as it flows through the turbine depending on temperature and pressure, the flow cross sections do not change linearly, so that the shape of the inner wall of the rotor can deviate from that of an ideal truncated cone.

In a drum with a frusto-conical outer shape, the inner wall of the rotor is circular cylindrical and thus also corresponds to the outer shape of the drum and the vanes arranged thereon, wherein the diameter of the truncated cone in the flow direction of the fluid is smaller as the diameter of the vanes and Blades is increasing.

The inner wall and the outer wall of the rotor are conceptually arranged spaced from each other such that an annular gap is formed between the inner wall and the outer wall. The outer wall and the inner wall are preferably mechanically interconnected via wheel discs.

A development of the invention is that the blades of the turbine are arranged on the inner circumference of the inner wall of the rotor, fixedly connected to the rotor. The blades are preferably arranged in a row, annular on the circumference and form the blade grid.

According to a further embodiment of the invention, the stator of the generator is circumferentially surrounding the rotor of the generator. The stator is preferably provided with stator windings. The wall of the stator is formed with the outer wall of the rotor correspondingly and advantageously as a housing of the turbo-generator unit. The wall of the stator and the outer wall of the rotor have substantially the same contours and shapes, so that the rotor can be integrated within the stator and the rotor is rotatably movable relative to the stator.
On the outer wall of the rotor, a permanent magnet is preferably arranged such that the permanent magnet is guided past during the rotational movement of the rotor to the stationary stator windings. The relative movement between rotor and stator or between Permanent magnet and stator winding leads to the induction of a voltage within the stator windings.

It is particularly advantageous that integrated bearings are formed in the housing of the turbo-generator unit. The bearings, which are preferably designed as magnetic bearings, guide and support the rotor which is rotatably mounted within the stator. In this case, a bearing is designed as a radial and axial bearing and a bearing as a radial bearing. The bearings guide the rotor each in the radial direction. The designed as a radial and axial bearing bearing is located on both sides of adjacent, formed on the rotor circumferentially formed formations in the direction of the central axis and thus additionally guides the rotor in the axial direction. The formations protrude in the radial direction from the outer wall of the rotor in the direction of the stator or the housing of the turbo-generator unit. Alternatively, the bearing formed as a radial and axial bearing comprises a circumferentially formed on the rotor molding in the direction of the central axis on both sides, wherein the formation is formed projecting in the radial direction from the outer wall of the rotor in the direction of the stator.
The bearings are preferably arranged in the axial direction, that is to say in the direction of the center axis of the turbo-generator unit, next to the stator winding. The bearings limit the stator winding in the direction of the central axis on both sides, wherein in each case a bearing is arranged on one side of the stator winding.

A further advantageous embodiment of the invention is that the rotor is formed of thermally decoupled material pairings in order to reduce the heat flows from the turbine to the generator and thus to limit the thermal load of the generator. The thermal decoupling is preferably carried out at the junctions of the wheel discs and the outer wall of the rotor, wherein the wheel discs are hollow-walled. Alternatively, the wheel discs are radially divided into two and positively connected by carbon fiber composite elements and non-positively, the wheel disc parts are dovetailed or hammerhead-shaped.
In addition, the wheel discs have profile slots, so that cooling air can be conducted through the annular gap formed between the inner wall and the outer wall of the rotor. The profile slots are preferably formed such that the cooling air is conveyed through the rotation of the rotor through the gaps between the outer wall of the rotor with the permanent magnets and the inner wall of the rotor as a boundary of the flow channel of the turbine. The cooling air flows through the annular gap and provided in the wheel discs profile slots and reduces the process of heat transfer from the turbine to the generator.

The turbo-generator unit is furthermore advantageously designed to be connectable to an electrical network via a converter. In this case, the converter has a pulsed machine converter, a DC intermediate circuit and a pulsed mains converter, each with a microcontroller-based information processing.

Furthermore, the turbo-generator unit is advantageously designed such that the rotational speed of the turbo-generator unit can be varied and preferably adapted to the power of the turbo-generator unit.

• - kompakte, platzsparende und gewichtsreduzierte Bauweise durch Integration des Generators und Ausbildung ohne zusätzliches mechanisches Getriebe und damit Reduzierung der Länge gegenüber der aufgelösten Bauweise um mindestens 15 %,
• - reduzierte Anzahl von Komponenten, zum Beispiel durch Reduzierung der Anzahl der Lager auf zwei Traglager und ein Axiallager,
• - Betriebsweise mit hoher Drehzahl - schnelllaufend,
• - Betriebsweise mit variabler Drehzahl - Anpassen der Drehzahl an die Leistung der Turbo-Generator-Einheit derart, dass die Strömungswinkel an den Turbinenschaufelprofilen nahezu konstant bleiben, um speziell die Strömungsverluste bei Teillast zu reduzieren,
• - großer Wirkungsgrad auch bei Teillast infolge der Drehzahlvariabilität,
• - Verzicht auf Nebenaggregate und Hilfsverbrauchsstoffe, insbesondere durch eine ölfreie Ausführung,
• - Minimierung der Wartungskosten, da beispielsweise die Wartung des Getriebes mit dazugehörigem Ölwechsel entfällt und
• - Verringerung von Spaltverlusten innerhalb der Turbine durch aktive Spaltkontrolle während des Betriebes - Reduzierung der Dichtspalte mittels Veränderung der Radiallage und der Axiallage der Trommel mit den Leitschaufeln innerhalb der Magnetlager durch gezielte Veränderung der mittels der Magnetlager erzeugten Lagerkräfte.

The inventive solution as integration of a turbine, which is preferably designed as a multi-stage, constructed in Außenläuferbauweise steam turbine with a low-mass, high-speed generator in a turbine-generator unit, which is advantageously formed with a magnetic bearings and thus oil-free storage, has various advantages on:

• - compact, space-saving and weight-reduced design by integration of the generator and training without additional mechanical gear and thus reducing the length compared to the resolved construction by at least 15%,
• - Reduced number of components, for example by reducing the number of bearings on two support bearings and a thrust bearing,
• - high speed operation - fast running,
• Variable speed operation - adjusting the speed to the power of the turbo-generator unit such that the flow angles at the turbine blade profiles remain nearly constant, specifically to reduce the flow losses at part load,
• high efficiency even at partial load as a result of the speed variability,
• - abandonment of ancillary equipment and auxiliary consumables, in particular by an oil-free design,
• - Minimizing maintenance costs, since, for example, the maintenance of the gearbox with associated oil change is eliminated and
• - Reduction of gap losses within the turbine by active gap control during operation - Reduction of the sealing gaps by changing the radial position and the axial position of the drum with the vanes within the magnetic bearings by deliberately changing the bearing forces generated by the magnetic bearings.

• 2: Prinzipdarstellung einer Turbo-Generator-Einheit ohne Getriebe - Anordnung der Turbine und des Generators auf einer Welle,
• 3: Prinzipdarstellung einer Turbo-Generator-Einheit in integraler Bauweise und
• 4: Konstruktion der Turbo-Generator-Einheit in integraler Bauweise.

Further details, features and advantages of the invention will become apparent from the following description of exemplary embodiments with reference to the accompanying drawings. Show it:

• 2 : Schematic representation of a turbo-generator unit without transmission - Arrangement of the turbine and the generator on a shaft,
• 3 : Schematic representation of a turbo-generator unit in integral construction and
• 4 : Construction of the turbo-generator unit in integral design.

In 2 is a turbo generator unit 1 shown without gear. The trained as a steam turbine drive device 2 and the generator 4 are arranged on a common shaft and thus rigidly coupled together. The of the in the flow direction 5 steam turbine 2 generated variable speed is directly to the generator 4 forwarded, so the turbine 2 and the generator 4 have the same speed.

• - eine Leistungsregelung mit unterlagerter Stromregelung durch einen Maschinenstromrichter,
• - die Realisierung eines Wirkleistungsbetriebes des Generators 4 mit cos (φ) ≈ 1 im gesamten Drehzahlbereich bei geringer Oberschwingungsbelastung,
• - die Drehzahlvariabilität der Turbo-Generator-Einheit 1,
• - eine Zwischenkreisspannungsregelung mit unterlagerter Stromregelung im Netzstromrichter und
• - eine normgerechte Netzeinspeisung in das Energieversorgungsnetz betreffen.

The turbo generator unit 1 is via an inverter 7 to the electrical network 6 connected. The inverter 7 includes a pulsed machine power converter, a DC link and a pulsed AC converter. Due to the decoupling of the variable generator frequency from the mains frequency, the system enables the operation of the turbine 2 at one, according to the load, optimal speed regardless of the mains frequency and thus the speed-independent electrical load of the turbo-generator unit 1 , The speed is both about the control of the turbine 2 by throttling the steam, as well as on the controllable generator torque by means of the machine converter can be varied and is adjusted according to an optimality criterion, the so-called MPPT maximum to the power requirement. MPPT stands for "Power Point Tracking Maximum". Taking into account the corresponding turbine characteristics, the efficiency of the turbine 2 increased in the partial load range.
Through the use of the inverter 7 In connection with a special control concept, various functions are guaranteed, among others

• a power control with subordinate current regulation by a machine converter,
• - The realization of an active power operation of the generator 4 with cos (φ) ≈ 1 in the entire speed range with low harmonic load,
• - The speed variability of the turbo-generator unit 1 .
• - A DC link voltage control with secondary current control in the power converter and
• - relate to a standard-compliant grid feed-in into the energy supply network.

3 shows the schematic diagram of a compact, oil-free, high-speed turbo-generator unit 1 in integral construction.
The steam turbine 2 is axial, multi-level and designed in external rotor design. The vanes 9 , which in each case the Leitgitter 9 the turbine 2 form, are on a circular cylindrical drum 8th arranged. According to an alternative embodiment, not shown, the drum 8th the shape of a truncated cone. The axis of the drum 8th and the central axis 18 the turbo generator unit 1 lie congruently on top of each other. The axes are identical.
The steam hits in the direction of flow 5 on the on the fixed drum 8th arranged, non-rotating vanes 9 on. When flowing around the guide vanes 9 the direction of the steam is changed so that a portion of the material-bound energy of the fluid is converted into kinetic energy, so that the flow has a higher speed and an angular momentum and the steam when hitting the direction of flow 5 subsequent blades 11 the blades 11 set in motion or drives. After flowing around the first blades 11 The steam enters a further arrangement of fixed vanes 9 one and is deflected again, in turn, optimally to the subsequent series of blades 11 impinge. The turbine 2 with a plurality of impellers or assemblies on blades 11 works multi-level.
As the steam flows through the turbine 2 cools and expands as a result of relaxation, the height or the length of the vanes decreases 9 and the blades 11 in the flow direction of the steam 5 to. For this reason, the multi-stage turbine 2 cone-shaped. Alternative to the fixed drum 8th are the drum 8th and the Leitgitter 9 compared to the blades 11 stored in such a way that the guide grille 9 in the opposite direction to the blades 11 rotate. Due to the optional design of the turbine 2 with counter-rotating guide grille 9 and scoop grid 11 is the number of stages compared to the version with fixed guide grid 9 reduced.
The blades 11 are stuck to the rotor 10 of the generator 4 connected so that the rotor 10 by means of the blades 11 driven and in rotation about the central axis 18 is offset. The design of the steam turbine 2 in external rotor design allows the arrangement of the permanent magnets 14 on the outside of the rotor 10 as components of the high-speed generator 4 ,
The rotor 10 of the generator 4 is inside the stator 15 arranged. The permanent magnets 14 be during movement of the rotor 10 on the stationary stator windings 16 of the generator 4 past. This will be within the stator windings 16 induces a voltage. The stator windings 16 of the generator 4 enclose the turbo-generator unit 1 ,
In addition, the turbo-generator unit 1 of oil-free bearings designed as magnetic bearings 12 . 13 includes. Camps 12 . 13 are in the direction of the central axis 18 each next to the stator winding 16 arranged. Camps 12 . 13 limit the stator winding 16 in the direction of the central axis 18 both sides. To the one from the turbine 2 to the generator 4 leading heat flow, that is the process of heat transfer from the turbine 2 with high temperature to the generator 4 at a lower temperature, minimize the rotor 10 made of thermally decoupling material pairings. In addition, cooling air is in the flow direction 17 through the rotor 10 trained annular gap 19 promoted. Due to the rotation of the rotor 10 The cooling air flows independently through the in the wheel discs 20 of the rotor 10 trained profile slots with appropriate shape.

In 4 will be in terms of 3 further construction of the turbo-generator unit 1 shown in integral construction. The required axial thrust balance is not shown.
The steam flows in the direction of flow 5 through a spiral housing 21 into the steam turbine 2 the turbo generator unit 1 and is through a guide grid 22 on an impeller 23 passed, which is the first stage of the multi-stage turbine 2 represents. The radially or diagonally formed impeller 23 is a structurally favorable design and ensures a low-loss inflow of steam into the turbine 2 , Also, with a radial or diagonal impeller 23 a higher level of energy converted to a trained stage than in an axial stage. Due to the higher proportion of converted energy, the steam temperature is lowered more. The impeller 23 is fixed to the rotor 10 of the generator 4 connected.
The steam flows after the multi-stage relaxation in the flow direction 5 through a diffuser 24 from the turbo-generator unit 1 out.
The stator 15 which is connected to the stator windings 16 is provided, forms the outer end of the turbo-generator unit 1 as part of a housing 26 , The towards the central axis 18 each next to the stator winding 16 arranged bearings 12 . 13 are inside the case 26 integrated. The rotor 10 is circumferential with formations 25 educated. The formations 25 are, in each case to the camp 12 arranged in the axial direction adjacent and include the bearing 12 in the direction of the central axis 18 on both sides. The formations 25 are in the radial direction of the outer wall of the rotor 10 in the direction of the stator 15 excellently formed. According to an alternative, not shown embodiment, also in the radial direction from the outer wall of the rotor 10 in the direction of the stator 15 protruding, on the rotor 10 formed circumferentially from the bearing with respect to the central axis 18 on both sides. The warehouse 12 is thus a radial and axial magnetic bearing 12 which is the rotor 10 leads both in the radial and in the axial direction and is designed as a combination bearing. In addition to the radial and axial magnetic bearings 12 becomes the rotor 10 about that as a radial magnetic bearing 13 trained camps 13 inside the stator 15 guided. The non-contact version of the magnetic bearings 12 . 13 allows the oil-free formation of the turbo-generator unit 1 ,

LIST OF REFERENCE NUMBERS

1

Turbo-generator unit

2

Drive device, steam turbine, turbine

3

transmission

4

generator

5

Flow direction of the steam

6

Electrical network

7

inverter

8th

Drum, guide bar carrier

9

Guide vane, guide vanes of the turbine 2

10

Rotor, rotor drum

11

Blade rotor, blade grid

12

Bearing, radial and axial magnetic bearing

13

Bearing, radial magnetic bearing

14

permanent magnet

15

Stator of the generator 4

16

stator

17

Flow direction of the cooling air

18

central axis

19

annular gap

20

Wheel discs with profile slots

21

volute

22

guide grid 1 , step

23

Impeller 1st stage

24

diffuser

25

formation

26

casing

Claims (11)

Turbo-generator unit (1) comprising a drive device (2) designed as a turbine (2) with a drum (8) and a generator (4) with a rotor (10) and a stator (15), the turbine ( 2) and the generator (4) are arranged integrated into one another and have a common central axis (18), and wherein the turbine (2) in external rotor construction and the generator (4) are formed in internal rotor construction, characterized in that the rotor (10) of the generator (4) is arranged coaxially around the drum (8) of the turbine (2) and has a hollow cylindrical outer wall and with the outer shape of the drum (8) of the turbine (2) corresponding inner wall, wherein the inner wall and the outer wall spaced from one another , an annular gap (19) forming, are arranged. Turbo generator unit (1) after Claim 1 , characterized in that, the outer wall and the inner wall of the rotor (10) via wheel discs (20) are mechanically interconnected. Turbo generator unit (1) after Claim 2 , characterized in that the wheel discs (20) have profile slots, so that cooling air in the flow direction (17) through the annular gap (19) is conveyed to reduce the process of heat transfer from the turbine (2) to the generator (4). Turbo generator unit (1) according to one of Claims 1 to 3 characterized in that the rotor (10) is formed of thermally decoupling material pairings to reduce the process of heat transfer from the turbine (2) to the generator (4). Turbo generator unit (1) according to one of Claims 1 to 4 , characterized in that the turbine (2) as axial, multi-stage steam turbine (2) with guide grids (9) and blade grids (11) is formed. Turbo generator unit (1) after Claim 5 , characterized in that the guide gratings (9) on the drum (8) are arranged fully circumferentially, wherein the drum (8) is formed circular cylindrical or frusto-conical. Turbo generator unit (1) after Claim 5 or 6 , characterized in that the drum (8) - fixed or - with the arranged on the circumference of the guide grid (9) against the rotational direction of the blade grid (11) is arranged rotatably movably supported. Turbo generator unit (1) according to one of Claims 5 to 7 , characterized in that the blades, (11) of the turbine (2) on the inner circumference of the inner wall of the rotor (10) are arranged annularly and fixedly connected to the rotor (10), wherein - each one on the drum (8) arranged Leitgitter (9) and formed as a ring series of blades (11) form a stage of the turbine (2) and - the rotor (10) via the rotor blades (11) driven and in rotation about the central axis (18) is displaceable. Turbo generator unit (1) according to one of Claims 1 to 8th , characterized in that the stator (15) surrounding the rotor (10) of the generator (4) circumferentially and the stator (15) is provided with stator windings (16), wherein - the wall of the stator (15) as a housing (26 ) and with the outer wall of the rotor (10) is formed corresponding to and - a permanent magnet (14) on the outer wall of the rotor (10), upon rotation of the rotor (10) on the stator windings (16) is arranged vorbeiführbar. Turbo generator unit (1) according to one of Claims 1 to 9 , characterized in that the turbo-generator unit (1) via an inverter (7) to an electrical network (6) is connectable, wherein the inverter (7) comprises a pulsed machine power converter, a DC intermediate circuit and a pulsed mains converter with one each having microcontroller-based information processing. Turbo generator unit (1) according to one of Claims 1 to 10 , characterized in that the rotational speed of the turbo-generator unit (1) is variable and adaptable to the power of the turbo-generator unit (1).

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