WO2012024704A1

WO2012024704A1 - Hydropower dynamic-pressure machine

Info

Publication number: WO2012024704A1
Application number: PCT/AT2011/000331
Authority: WO
Inventors: Andreas Sternecker
Original assignee: Maschinenfabrik Kba-Mödling Aktiengesellschaft
Priority date: 2010-08-24
Filing date: 2011-08-03
Publication date: 2012-03-01
Also published as: AT510320A1; AT510320B1

Abstract

The invention relates to a hydropower dynamic-pressure machine (1), comprising at least one rotor (2), which is rotatably mounted on a frame and which has a hub (3) and blades (9) connected to the hub and which defines a water level height as the difference between an upper water level and a lower water level during operation, and comprising an electric motor-generator machine (21'), which is coupled to the rotor (2) by means of a gear train (21) and which is combined with the rotor in a module (20), wherein a carrying part (22), which is rigidly connected to the frame (5) and which is sealed off from the rotor (22) and which has a plurality of slot-like receptacles (25) preferably arranged on the lower water side for one machine (21')-gear train (21) module (20) each, is arranged adjacent to at least one end face of the hub (3) of the rotor, machine-gear train modules (20) are fastened in at least some receptacles (25), a drive pinion (34) of each machine-gear train module meshing with a ring gear (33, 33') rigidly attached to the end face of the hub (3), and switches (PWR1, PWR2,... PWRn) for selectively switching the machine-gear train modules (20) on and off are associated with the machine-gear train modules (20).

Description

Hydro-dynamic pressure machine

The invention relates to a hydro-dynamic pressure machine with at least one rotatably mounted in a frame impeller having a hub and associated blades, and which defines a water level in operation as a difference between a head level and an underwater level, and with a with the impeller via a Gearbox coupled in a module with this combined electric motor-generator machine.

Hydropower dynamic pressure machines are known from AT 404 973 B and AT 501 575 AI. The impeller is arranged transversely to the flow direction in a channel. The hub of the impeller can replace a weir, which in hydraulic engineering is understood to mean a reservoir that closes off a flow region. Depending on the design weirs can be overflowed or flowed through as needed, the section of the channel in the direction of flow above the weir as upper water and the section of the channel below the weir is referred to as underwater. In the past, weirs with low stowage heights were only provided for damming water as required; Starting from this it was proposed in AT 404 973 B or AT 501 575 A1 to use the dynamic pressure for energy generation. For this purpose, the inflowing water drives the blades of the impeller, which is connected to the motor-generator machine. In generator operation, a braking torque is built up, and there is a conversion of the mechanical power into an electrical useful power, which is supplied to an energy storage ^¬ or fed into a power grid. This type of hydro-electric machine has the advantage that the generator is driven by the pressure of the flowing water. Accordingly, in terms of high efficiency at large

Swallowing capacity used both the flow velocity of the channel and the potential level corresponding to the water level for energy production.

The output power and the achievable efficiency depend inter alia on the headwater level, ie on the upstream water level of the channel relative to the hub of the impeller. The headwater level affects the impellers available to drive the impeller Amount of water. It has already been proposed (see http://de.wi-kipedia.org/wiki/Staudruckmaschine and the previously unpublished earlier application AT A 1195/2010) to regulate the upper water level to the current Oberwasserpegel continuously to the Oberwas ^¬ serpegel -Soll value to be adjusted.

More specifically, in a dynamic pressure machine, the amount of water flowing from the upper water through the system into the underwater per unit of time, usually called the intake capacity, depends on the speed of the impeller. Since the water flow is expediently not offered a possibility to avoid the impeller arranged across the entire channel, the entire water flows through the dynamic pressure machine. At a high speed of the impeller is a high absorption capacity of the dynamic pressure machine, with a larger amount of water is transported by the blades to the underwater side and thus the head water level is reduced; conversely, reducing the speed of the impeller results in a lower one

Sucking power of the dynamic pressure machine, so that less water flows through the ram pressure machine and as a result the head water level rises. To comply with the predetermined head water level, which is aimed at a certain power output or optimum efficiency, thus the rotational speed of the impeller can be influenced, which can be accomplished via the braking torque of the motor-generator machine. To reduce the speed of the impeller, the braking torque of the generator can be increased; on the other hand, to achieve a higher speed of the impeller to achieve a greater absorption capacity of the dynamic pressure machine, the braking torque of the motor-generator machine can be reduced. Such influencing is relatively expensive in a conventional dynamic pressure machine with a motor-generator machine control technology.

Another disadvantage of the known hydroelectric or dynamic pressure machines results from the fact that in case of failure of the motor-generator machine, the hydropower or dynamic pressure machine fails until the motor-generator machine

repaired or replaced. This disadvantage is also given in the hydropower plant according to DE 43 13 509 AI, in which directly in a disc wall of the hub of the water wheel a recess is provided as a receptacle for a transmission with which a generator is coupled, wherein a kind of module is obtained; The generator is supported by a support bracket, which is attached to a building wall. It is also essential here that a coaxial arrangement of the - single - gear generator module is provided.

Also in the hydropower plant according to WO 2009/121824 A2 and in the generator system according to US 2009/0322093 AI, a single generator, as usual, is provided, which is driven by a gear wheel driven by an impeller and thereby eccentrically relative to the axis of rotation of its own holder is arranged.

It would also be desirable, moreover, in the case of the module design mentioned, for example, in AT 501 575 A1, to allow an adapted total generator output depending on the power of the impeller, which in the known dynamic pressure machines only by replacing the motor-generator-machine, i. by attaching a motor-generator machine with adapted to the drive power generator power can be accomplished.

It is an object of the invention to propose a hydro-dynamic pressure machine as stated above, with which not only such a power adjustment in a modular design of the dynamic pressure machine can be realized in a simple manner, but also a total failure of the hydropower in case of failure Motor-generator machine can be avoided, and further in a simple manner, operation in an optimal generator power range depending on the head water level or possibly also underwater level, ie

particular of the water level or the difference between the upper water level and underwater level, is made possible.

To solve this problem, the invention provides a hydro-dynamic machine as characterized in the independent claim. Advantageous embodiments and further developments of this dynamic pressure machine are specified in the dependent claims. In the present hydropower ram printing machine is thus provided primarily that adjacent at least one end ^¬ side of the hub of the impeller firmly connected to the frame support member with a plurality of slot-like, preferably underwater side arranged receptacles for each machine Ge ^¬ transmission module is arranged, opposite the impeller

is sealed, that are fixed in at least some shots machine gearbox modules, each of which a drive ^¬ pinion meshes with a fixedly mounted on the front side of the hub ring gear, and that the machine-transmission modules associated switching means or switch for selective On or off the machine-transmission modules are provided. Characterized in that a plurality of machine-transmission modules are provided, the sprockets complement each other to a "matrix drive", for example, depending on the width of the impeller by attaching more or less machine gearbox modules with the matrix drive simply Gesamtan ^¬ operating power (total generator power ) are adapted to the particular design of the impeller.

Furthermore, by (electrical) Removal of individual modules, depending on the water supply, it is possible push the remaining operating individual generators in an optimal power range to be ^¬. The electrically disconnected modules turn then empty without power extraction. This allows the electrical power output to be adapted to the needs of the local water supply.

Should an engine-transmission module fail (electrically), the hydro-electric machine can continue to operate with the modules still operating, possibly with reduced power, i. it does not fail the entire system, as is the case in the prior art.

As far as the performance or modular design is concerned, a wide water wheel, given a diameter, delivers more power than a narrower impeller (with the same diameter). As a good approximation, a wheel that is twice as wide (waterwheel) produces twice the torque and twice as much power. With the support part according to the invention for a plurality of machine-transmission modules can, depending on the width of the impeller, the number of modules to be used are determined, which are mounted in the desired receptacles of the support member. Unused recordings, ie free recordings, in which no machine-gearbox modules are inserted, are sealed in a suitable manner. This means that at a maximum wide wheels the maximum number of machine-Ge ^¬ gear modules is attached to the supporting part, whereas simply fewer machines gear modules can be attached to the support member at narrower wheels.

Thus, in the present machine-transmission modules, there is a generator with an integrated transmission, e.g. a planetary gear or spur gear, in front; a drive pinion of this transmission is accessible from the outside, and this drive pinion is in engagement with the ring gear on the hub end face; via the gearbox, the relatively low speed of the impeller is converted into a suitably high speed of the generator.

Theoretically, it is also conceivable to provide only the meshing with the ring gear drive pinion when the translation between sprocket and pinion already sufficient for the speed over ^¬ tion to the generator. It is for these purposes

In particular, it is advantageous if the toothed rim on the hub end face is an internally toothed ring gear which is thus present on the outside (that is to say outside the pinions) and thus has a relatively large tooth area

Diameter and thus has a large number of teeth, so that the relatively small pinion, with a small number of teeth, can be driven in operation with a comparatively much higher speed from the sprocket.

In principle, it is of course also possible, for example, if this is necessary for other structural conditions to provide an externally toothed ring gear on the hub end face, in which case the pinion of the machine-gearbox modules outside of this ring gear are present, then compared to a internal gear ring has a smaller diameter, so that the translation can not be as high as an internally toothed ring gear.

For a simple, space-saving, compact design, the Support member preferably plate-shaped, for example as a side plate, out ^¬ forms.

Furthermore, the support member can be easily connected to the frame via at least one bracket projecting from the frame; As already mentioned, the machine-gearbox modules are preferably located on the underwater side of the dynamic pressure machine, and the console, preferably two consoles, project from the underbody side of frame supports and support the supporting part with the required strength. The support member can also be used to support the impeller, i. the supporting part is part of the bearing frame via the console (s).

To easily mount the machine-gearbox modules on the support part, it is advantageous if these modules are attached to the support part via flange connections. In the case of free recordings of the support member, these free receptacles of the support member are preferably closed by blind flanges.

In order to allow the best possible power adjustment, it is advantageous if the support member contains more than three shots for machine-gearbox modules. But it is also possible in principle to provide only two or three shots.

For proper operation of the dynamic pressure machine, it is further preferred if between the support member and the hub end side seals, eg lip seals, against water inlet on the one hand and oil outlet on the other are arranged; or when arranged between the supporting member and a wheel-shaft Seal ^¬ gen against water inlet on the one hand and oil outlet on the other.

For a possible automatic power adjustment, for optimal operation of the dynamic pressure machine and in particular of the generators, it is furthermore favorable if the switching means are connected to a control unit, eg with PLC module, which in turn is connected to a level sensor, preferably an upstream water level sensor, is connected to switch off at a comparatively low water level (for example, in the order of shutdown) switching means for switching off individual machine To control transmission modules.

The invention will be further elucidated on the basis of preferred embodiments, to which, however, it should not be restricted, and with reference to the drawing. In detail in the drawing:

Figure 1 is a perspective view of a hydro-dynamic pressure machine according to the invention, as seen from the underwater side, wherein the side of the impeller with the engine-transmission modules is visible.

Fig. 2 is a similar perspective view of the underwater side of the dynamic pressure machine of Figure 1, but now from the other side, opposite to the side where the machine transmission modules are mounted;

3 shows an oblique view of the dynamic pressure machine according to FIGS. 1 and 2 from the upper water side;

Fig. 4 is a side view of the dynamic pressure machine according to Figures 1 to 3, wherein the side with the machine-gearbox modules is visible.

5 is an elevational view of the dynamic pressure machine according to FIGS. 1 to 4 seen from the upper water side;

Fig. 6 is a side view of the ram pressure machine similar to Fig. 4, but with the stationary frame and the storage frame of the ram pressure machine cut away, substantially along line VI-VI in Fig. 5; FIGS. 7A and 7B show two embodiments with regard to the arrangement of the sprocket on the end face of the hub of the dynamic pressure machine, namely once with internal teeth (FIG. 7A) and once with external teeth (FIG. 7B);

Fig. 8 is a partial view, partially broken away, the dynamic pressure machine of FIG. 1 to 4, wherein in particular the bearing of the impeller and a formation of an externally toothed ring gear illustrated at the hub; 9 and 10 are partial sectional views in the region of the seal between the module support member and the hub (detail IX in FIG. 9) or between the module support member and the impeller shaft (detail X in FIG. 10); and

Fig. 11 is a block diagram illustrating an electric circuit including a control unit for turning on and off the electric machines (generators) depending on the water level.

In Fig. 1 and 2, a hydro-dynamic machine 1 with an impeller 2 is seen from the underside seen schematically illustrated. Figs. 3 and 5 show this dynamic pressure machine 1 seen from the upper water side.

The impeller 2 has a cylindrical hub 3, whose axis is simultaneously the axis of rotation of the impeller 2, also called rotor. At this hub 3 annular end plates 4 are fixedly attached to the axial ends, which limit the width of the impeller 2. These cover plates 4 allow an advantageous sealing of the impeller 2 in a bearing frame 5 by means of in Figs. 3 and 5 apparent, on a stationary frame 6 on the upper side attached sheets 7 and attached to these sealing lips. 8

At the periphery of the wheel hub 3 suitably shaped blades 9 are mounted, e.g. screwed and / or welded to form bags for water transport, i. to absorb the water pressure and to effect a torque around the wheel axle.

The vanes 9 of the impeller 1 may have, in addition to the V-shaped arrangement shown, other arrangements, such as simple oblique arrangements (see, for example, AT 404 973 B), and may also have a curvature depending on the objective.

The frame 5 supporting the impeller 2 has an overall rectangular shape with two vertical supports 10, 11 and a lower support 12 and an upper support 13 around the impeller 2 around. The carriers 10 to 13 are preferably formed from rectangular in cross-section mold tubes, whereby a simple, lightweight, yet stable construction of the frame 5 is achieved, which also allows easy adaptation to different dimensions, in particular widths of wheels 2. In this regard, reference should be made to the prior unpublished application AT A 1193/2010, the contents of which are incorporated herein by reference.

The vertical supports 10, 11 carry wheel bearings 14 (only one of these bearings is visible in Fig. 2, the other is concealed in Figs 1 to 3, but see also Fig. 8), wherein the wheel bearing 14 according to FIG is fastened to a bracket 15 projecting from the bracket 15, as shown in FIG. 2 can be seen. This attachment of the bearing 14 is provided in the preferred embodiment on the downstream side (underwater side) of the dynamic pressure machine 1.

The vertical supports 10, 11 are on their outer sides, ie on the side facing away from the impeller 2, with not further apparent guide roller units (or other a low-friction displacement of the frame 5 in the stationary machine frame 6 ensuring guiding elements) equipped, see. 1 to 3, so as to raise or lower the frame 5 relative to the frame 6, for example for maintenance purposes or to adapt the impeller height to the respective underwater level, with the aid of a suitable, To allow not shown in detail lifting device; see. the mentioned A 1193/2010; the raising or lowering of the frame 5 is schematically illustrated in Fig. 3 with a double arrow 5 '.

3, which shows the upstream side or upstream side of the dynamic pressure machine 1, a curved crop pan 17, which is arranged in the lower region of the rotor 2 and is shown by means of holders 18A attached to the vertical supports 10, 11, is shown. 18B is attached to the frame 5 and has a curvature which is adapted to the path of movement of the impeller 2 and the blades 9 thereof. With the help of this bolster 17 can thus tan the water gential in the lower area around the impeller 2 are introduced, so that it expires at the underside (Fig. 1 and 2) on the underside of the impeller 2 in an outlet region 19 (Fig. 2) above the lower support 12 and flows.

The arrangement with the sealing lips 8 and further with the cropping plate 17 ensures that the water of the channel is optimally utilized for the generation of electrical energy, i. the efficiency of the dynamic pressure machine 1 shown is thereby additionally improved.

The described frame 5 for supporting the impeller 2 allows a modular principle for the dynamic pressure machine 1, wherein with the help of the carrier 10 to 12 in a simple manner to the respective size (width or diameter) of an impeller 2 adapted La ^¬ ger frame 5 assembled can be. Suitable for this purpose is then provided in the channel stationary arranged frame 6.

In order to meet this modular principle also with regard to the power-generating means, a matrix arrangement with several modules 20, each containing an electric machine (generator motor) and integrated with it a transmission vorgese ^¬ hen. From Fig. 1, three such modules 20, each with a gear 21 and a machine or a generator 21 ',

seen. These modules 20 are fixedly attached to a frame 5 fixed to the support member 22 which is disposed on the front side of the hub 3 of the impeller 2, but does not rotate with this hub 3, but with the aid of brackets 23, 24 with one of the vertical Support of the frame 5, as shown in FIG. 1 with the vertical support 11 shown there on the left, is rigidly connected. The support member 22 is formed plate-shaped or disc-shaped in the embodiment shown, said disk-shaped support member 22 as shown in FIG. 1 is radially inside and adjacent to the circular on this page cover 4, which in turn firmly connected to the hub 3 of the impeller is as mentioned above.

The support member 22, also called circular disc, side plate or motor plate, has a plurality of slot-like receptacles 25 for each one machine-transmission module 20, wherein it is not necessary to install 25 corresponding modules 20 in all recordings. As provided in the example of FIG. 1, to attach one module 20 in three of the five men Recordin ^¬ 25th The two intermediate free slot receptacles 25 that do not accommodate modules 20, s. 1, are tightly closed, for example with the aid of blind flanges 26. The modules 20 in turn are connected in a corresponding manner via schematically shown in FIGS. 1 and 9 flange 27 with the support member 22.

In this way, depending on the size, i. Width and diameter of the impeller 2 more or less modules 20 are mounted so as to optimally recover electrical energy from the kinetic energy of the impeller 2, with optimum efficiency.

From Fig. 4 is a side view of the arrangement of the impeller 2 of the dynamic pressure machine 1 in the frame 6 (the frame 5 is not visible in Fig. 4) illustrated, wherein it is shown that the modules 20 and receptacles 25 in the support member 22 at the Underwater page 28 of the dynamic pressure machine 1 are present; the upper water side is indicated in Fig. 4 at 29, and further is the

Direction of rotation of the impeller 2 indicated by an arrow 30. Wei ^¬ ters can also be seen in the illustration according to Fig. 4, that centrally another bearing 31 is mounted on the shaft of the impeller 2 on the support 11. This bearing 31, like the bearing 14, is preferably a self-aligning bearing; Axis and angle errors can be compensated by the self-aligning bearings.

From the upstream side view of the dynamic pressure machine 1 according to FIG. 5 are again mounted in the frame 6 rectangle frame 5, the impeller 2 with the blades 9, further the sheets 7 with the sealing lips 8 and the cropping tray 17 can be seen.

In a sectional view along the line VI-VI in Fig. 5 then the arrangement of the receptacles 25 for machine-gearbox modules 20 in the side plate support member 22 can be seen in Fig. 6; Furthermore, connecting parts 32 for connecting the supporting part 22 with the brackets 23, 24, thus with the frame 5, can be seen.

In FIGS. 7A and 7B, the end face of the hub 3 can be seen, wherein it is shown that at these hub end faces a sprocket 33 (Fig. 7A) and 33 '(Fig. 7B) is fixedly mounted. In the case of Fig. 7A, the ring gear 33 is an internally toothed ring gear with a relatively large diameter, and with this internally toothed ring gear ^{¬ mesh ¬} three drive pinion 34, which belong to the three machine-gearbox modules 20 as shown in FIG. 1, 2 and 4 , wherein the ring gear 33 with the respective drive pinion 34 already form a gear stage to increase the speed. In certain cases, the resulting translation may already be sufficient to drive the generators 21 'of the modules 20 at a suitable rotational speed, so that further gear parts in the gears 21 of the modules 20 can be dispensed with. The gear 21 is then formed in each case only by the ring gear 33 and the associated pinion 34. As a rule, however, further toothed wheels will be present in order to provide an additional (in the case of FIG. 7A, however, relatively small) ratio (secondary ratio) for driving the rotor of the generator 21 '.

In the case of FIG. 7B, the ring gear 33 'is externally toothed, wherein the drive pinions 34 of the machine-gearbox modules 20 (see FIG. 1) are located radially outside this ring gear 33'. As can be seen here, the transmission ratio is smaller than in the case of FIG. 7A, so that here a comparatively larger secondary ratio in the transmission 21 of the respective module 20 is required.

It results here that an internally toothed ring gear 33, as shown in Fig. 7A, as a rule, is preferable because a small ^¬ secondary translation - if any - in the module 20 is required, and since lower tooth forces in gear operation.

For reasons of constructive circumstances, however, an external toothing may sometimes be necessary, and as can be seen in FIG. 7B, this is entirely possible in the present dynamic pressure machine 1.

From the partial view in Fig. 8, the bearings 14, 31 for at the hub 3 of the impeller 2 frontally mounted stub shaft 35, 36 can be seen. This can be a camp, namely the camp 14, on the side facing away from the modules 20 Stinseite, example ^{¬ be designed} as a pendulum bearing. The opposite La ^¬ ger 31, for the other stub shaft 36, for example, via a rigid mounting plate 37 is connected to a provided as Na ^¬ ben end face 38 plate.

Furthermore, internal stiffeners 39 on the hub end faces can still be seen from FIG. 8. These stiffeners 39 can be provided for receiving bending moments, which originate from the distances between the bearings 14, 31 and the mounting plates 37 at the hub end faces 38.

Fig. 9 shows in a detail section corresponding to the detail IX in Fig. 8, the region of the seal between the support member 22 and the wheel hub 3. It is illustrated that between the hub 3 and the support member 22 (motor plate or side plate) a Oil space 40 is provided, said oil space 40 or space between the support member 22 and hub 3 is to seal accordingly. Specifically, here is a seal 41, in particular lip seal, provided to prevent ingress of water into the space 40, and another seal 42, in particular Lip ^¬ pendichtung, which lies axially further inside, serves to an oil leakage from the oil chamber 40 prevent. As can be seen further from FIG. 9, the respective toothed rim, for example the internally toothed ring gear 33 (see also FIG. 7A), can be fastened with the aid of bolts or similar fastening means 43

End face 38 or a fixedly connected flange 44 of the hub 3 may be connected.

Fig. 10 shows the detail X of FIG. 8 and concretely the area of a rolling bearing 45 for centering the support member or side plate 22 relative to the shaft 36 and further ent ^¬ speaking part of the oil chamber 40, with a seal 42 'against oil leakage on the one hand or a seal 41 'against Wasserein ^¬ occurs on the one hand between the support member 22 and the shaft or the stub shaft 36th

In Fig. 11, a plurality of strands 51, 52, 53, etc. are each shown with a generator 21 'of a module 20 as described above. The generators 21 'are preferably Asynchronous generators, even if synchronous generators could also be used. The generators of the individual strands 51, 52 ... 53 provide their electrical power to inverter 54, which via switch PWR1, PWR2 ... PWRN with a Rückspei ^¬ seumrichter 55 - in normal operation - are connected to current 55 about this to Rückspeiseumrichter to deliver a network 56. The switches PWR1, PWR2... PWRn form switching means 57 which belong to a control unit 58 with, for example, a PLC control module 59. This PLC module 59 is connected to a level sensor 60 for water level determination, for example, (only) the upper water level is detected. If appropriate, however, it is also possible to detect the upper water level and the underwater level or the level difference, with a specific level difference leading to optimum operation of the dynamic pressure machine 1. At constant underwater level, it is sufficient to detect the head water level, then by raising the speed of the impeller 2 of the dynamic pressure machine 1 and thus the absorption capacity of the dynamic pressure machine 1, for example, a too deep sunken upper water level to raise again or too high

Lowering the headwater level through increased water transport through the dynamic pressure machine 1 back to the optimum level value. In this context, it is favorable if, in the case of a larger number of generator / transmission modules 20 (see FIG. 1), individual generators 21 'can be switched on and off, for which purpose the switching means 57 are provided in conjunction with the SPS control module 59 are. Now, if the detected water level is relatively low, one or more generators 21 'may be turned off via the control unit 59 and the corresponding one or more switches PWRi so as to reduce the water flow rate and increase the upper water level again. In this way, operation of the (remaining) individual generators 21 'in an optimum power range can be achieved. The electrically disconnected generators 21 'turn then empty without power extraction. A mechanical separation of the unused generators 21 'is indeed theoretically possible, but not essential.

Apart from the automatic activation or deactivation of generators 21 ', as described with reference to FIG. 11, it is naturally also conceivable to use individual generators 22 by hand Help switching means 57 on or off, such as when long-lasting changes in the water levels, in prolonged drought or prolonged periods of rain, given.

The described matrix arrangement with several machine-gearbox modules 20 also provides, apart from the above-described operational optimization, also the advantage that in the event that a generator module fails, the water engine 1 continues to work with the remaining modules 20, optionally with reduced power , can continue to operate. Both

Hydropower machines according to the prior art with only a single generator, however, fails in case of failure of the generator, the entire system.

Claims

Claims:

A hydro-dynamic ram machine (1) having at least one impeller (2) rotatably mounted on a frame and having a hub (3) and blades (9) connected therewith, and in operation a water level height as the difference between a high water level and an underwater level determines, and with a with the run ^¬ wheel (2) via a transmission (21) coupled in a module (20) combined with this electric motor-generator machine (21 ') _/ characterized in that adjacent at least one end of the Hub (3) of the wheel with the frame

(5) fixedly connected support member (22) with a plurality of slot-like, preferably underwater side arranged receptacles (25) for each one machine (21 ¹ ) -Griebe- (21) module (20) is arranged, which support member (22) relative to the impeller (2) is sealed, that in at least some shots (25)

Machine transmission modules (20) are fastened, of which in each case a drive pinion (34) with a on the front side of the hub (3) fixedly mounted sprocket (33, 33 ') meshes, and that the engine-transmission modules (20 ) Switches (PWR1, PWR2 ... PWRn) for selective connection or disconnection of the machine-gearbox modules

(20) are assigned.

Second hydro-dynamic machine according to claim 1, characterized in that the supporting part (22) plate-shaped, e.g. as a disc or side plate is formed.

3. Hydropower dynamic pressure machine according to claim 1 or 2, characterized in that the supporting part (22) with the frame (5) via at least one cantilevered by the latter console (23, 24) is connected.

4. Hydropower dynamic pressure machine according to one of claims 1 to

3, characterized in that the machine gear module (20) via flange (27) on the support member (22) are attached.

5. Hydropower dynamic pressure machine according to one of claims 1 to

4, characterized in that free receptacles (25) of the support member (22) by blind flanges (26) are closed.

6. Hydropower dynamic pressure machine according to one of claims 1 to

5, characterized in that the toothed rim (33) on the hub end face is an internally toothed ring gear.

7. Hydropower dynamic pressure machine according to one of claims 1 to

6, characterized in that the supporting part (22) contains more than three receptacles (25) for machine-gearbox modules (20).

8. Hydropower dynamic pressure machine according to one of claims 1 to

7, characterized in that between the support member (22) and the hub end side seals (41, 42), e.g. Lip seals, against water inlet on the one hand and oil outlet on the other are arranged.

9. Hydropower dynamic pressure machine according to one of claims 1 to

8, characterized in that between the support member (22) and an impeller shaft (36) seals (41 ', 42') against water inlet on the one hand and the oil outlet on the other hand are arranged.

10. Hydropower dynamic pressure machine according to one of claims 1 to

9, characterized in that the switches (PWR1, PWR2 ... PWRn) are connected to a control unit (58), e.g. with PLC module (59) are connected, which in turn with a level sensor (60), preferably an upper water level sensor, connected to a comparatively low water level individual switches (PWR1, PWR2 ... PWRn) for switching off individual machine gearbox To drive modules (20).