WO2017125115A1

WO2017125115A1 - Turbomachine for obtaining pressurized air and pressurized water

Info

Publication number: WO2017125115A1
Application number: PCT/EP2016/001808
Authority: WO
Inventors: Karl-Heinz Göhre
Original assignee: Apa Energie Gmbh
Priority date: 2016-01-22
Filing date: 2016-10-28
Publication date: 2017-07-27
Also published as: DE102016000693A1

Abstract

The present invention relates to a turbomachine for obtaining pressurized air and pressurized water, having a pump wheel (2) which comprises at least one spiral-shaped delivery duct (6) which has an inlet (7) at an outer peripheral section of the pump wheel (2), and a pressure outlet (8) at an inner section of the pump wheel (2). What is proposed is that the pump wheel (2) be arranged such that the inlet of the spiral-shaped delivery duct (6) cyclically dips into and emerges from a liquid reservoir (12) and, accordingly, liquid and ambient gas, in particular air, enter the delivery duct (6) in cyclical or alternating fashion, so as to produce a gas-liquid mixture and/or a pulsating liquid flow and gas flow, and liquid and gas are expelled in a pulsating fashion from the pressure outlet.

Description

Turbomachine for obtaining compressed air and pressurized water

The present invention relates to a turbomachine for obtaining compressed air and pressurized water, comprising an impeller comprising at least one spiral-shaped delivery channel having an inlet at an outer edge portion of the impeller and a pressure outlet at an inner portion of the impeller.

In water systems, there are various applications that require not only pressurized water but also compressed air, for example in the form of a pressure-air-water mixture. For example, turbomachinery with an upright turbine wheel are known, the turbine blades run in a water-filled housing, wherein in the water introduced pressurized gas or the resulting, pressurized air-water mixture by the rise of the pressurized gas drives the turbine wheel, see. For example, the document DE 10 2013 008 859 A1. On the other hand, such a pressure-air-water mixture can also be used in water treatment, for example, to aerate low-oxygen waters such as ponds or ponds. Conventional pumps with spiraling conveying channels, as they are known for example from the document EP 05 79 888 B1, try mostly to produce a pulse-free as possible, uniform flow and thereby draw as little air in the pressurized water, which is an application that a higher Need compressed air, is less suitable.

The present invention is therefore based on the object to provide an improved turbomachine of the type mentioned, which avoids the disadvantages of the prior art and the latter further advantageously. In particular, an efficient extraction of compressed air and pressurized water is to be made possible, in which the compressed air content can be controlled in a simple manner and also higher proportions of compressed air can be generated.

According to the invention, said object is achieved by a turbomachine according to claim 1. Preferred embodiments of the invention are the subject of the dependent claims.

It is therefore proposed to arrange the impeller such that the spiral conveyor channel cyclically dips with its inlet into a liquid reservoir and emerges therefrom and therefore cyclically or alternately liquid and ambient gas, in particular air enters the delivery channel, so that a pulsating liquid flow and gas flow is generated and from the pressure outlet, a gas-liquid mixture and / or pulsating liquid and gas is pressed out. According to the invention, the impeller is arranged partially underneath and partially above the level of a liquid reservoir, so that the inlet of the delivery channel is cyclically immersed in the reservoir when the impeller rotates and emerges therefrom. Depending on the position of the inlet opening of the channel, the rotary or delivery channel absorbs air and water components or gas and liquid components. The pressure is created in the delivery channel by the gravity of the liquid in the individual turns during rotary operation of the impeller. By such a partially above and partially below the level of the liquid reservoir lying arrangement of the impeller, the air or gas content or the ratio of pressurized water to compressed air can be controlled in a simple manner. In a development of the invention, adjusting means for adjusting the immersion depth of the impeller may be provided. If a greater immersion depth is set, so that the impeller or the delivery channel dips deeper into the liquid reservoir or the inlet of the delivery channel circulates a longer distance under water, a larger proportion of pressurized water and less compressed air is achieved. Conversely, if the immersion depth is reduced, the segment of the orbit of the delivery channel inlet, in which the delivery channel inlet under water runs smaller, so that a higher compressed air content and a smaller proportion of pressurized water is achieved.

The aforementioned adjustment means can in principle be designed differently. If the water or liquid level of the reservoir can not be changed or can not be changed fast enough, the adjustment means can have a height adjustment device by means of which the pump wheel can be adjusted in its height. Such height variability of the impeller can be particularly advantageous for natural waters such as ponds, lakes or rivers whose level can not be changed easily. The height adjustment device can be designed differently depending on the storage and foundation structure. If a firm foundation is provided for the bearing of the impeller, a height-adjustable impeller shaft or a height-adjustable axle bearing can be provided. If a floating foundation for the pump wheel in the manner of a raft or a pontoon is provided in order to store the turbomachine floating on the water, floating tanks with variable buoyancy volume can be provided in order to be able to vary the immersion depth. Alternatively or additionally, however, can be provided for the impeller also in such a floating pontoon storage height adjustable axle bearings.

With regard to the delivery channel, the impeller can basically be designed differently. In development of the invention, the said conveyor channel formed consistently and without interruption. In particular, said conveying channel can be single-lane or catchy and bifurcated from the inlet to the pressure outlet.

In a further development of the invention, the conveyor channel may have a substantially constant cross-section or a substantially constant cross-sectional area, wherein the conveyor channel over at least the vast majority of its longitudinal extent such a constant cross-section or a constant cross-sectional area may have and possibly. Only in the inlet and / or Outlet a cross-sectional change or cross-sectional area change can be provided. The said cross section is considered perpendicular to the longitudinal axis of extension - that is, in each case perpendicular to the spiral sections. In particular, the cross-sectional area of the conveying channel can remain the same over its entire longitudinal extent from the inlet to the pressure outlet.

Alternatively, however, it is also possible that the cross-section or the cross-sectional area of the conveying channel changes over its longitudinal extent. In particular, it can be provided in a development of the invention that the cross-sectional area of the conveyor channel continuously decreases from the inlet to the pressure outlet, in particular decreases steadily.

In order to enable the most efficient possible flowing through the turns of the conveying channel, the conveying channel in development of the invention may have a continuously curved course, wherein the curvature of the spiral conveyor channel from its inlet to the pressure outlet can be continuously stronger, that is, the radius of curvature are continuously smaller can.

Instead of such a continuous helical curvature, the conveying channel may also have a polygonal and / or polygonal course, which only approximates or approximates the aforementioned continuous, harmonic spiral curvature. In particular, the conveyor channel may have a polygonal gen, have polygonal course and be composed in segmental construction of several, interconnected channel segments. Such a segment construction with sections of straight delivery channel course facilitates the production of the impeller significantly. In particular, the peripheral channel walls can be formed by straight sheet metal strips or straight, plate-shaped material portions which can be accommodated between plate-shaped end side walls of the impeller.

The transitions between the straight sections of such a polygonal channel can remain angular in the sense of juxtaposed wall segments. Alternatively, however, a rounded transition region between the straight wall sections may be provided to minimize flow losses.

If necessary, such a rounding can again be approximated by two folds, with which the corner or edge angle between two straight channel sections is, so to speak, halved or broken.

For example, the delivery channel may have a hexagonal, octagonal, or octagonal configuration in which a delivery channel turn adjacent to said rectilinear sections 6, 8, or 10 includes corners, one turn being a 360 ° turn.

The delivery channel may form a planar spiral in which the inlet, the delivery channel windings and the delivery channel outlet lie in one plane, said pressure outlet may of course be continued by a pressure line, which may extend, for example, perpendicular to the plane of the impeller or its Förderkanalwindungen , Such a planar design of the conveying channel without axial displacement between the inlet and pressure outlet or without the slope of the conveying channel windings, an axially very compact design of the impeller can be achieved. The impeller can form a flat disc, at the conveyor channel is sandwiched between two end walls.

Alternatively, however, the delivery channel may also have an axial pitch and / or be designed in the manner of a screwing spiral, wherein the inlet of the delivery channel relative to the pressure outlet may have an axial offset. The turns of such a conveyor channel are viewed from the inlet ever close and screwed while a fixed or varying pitch in the axial direction.

The impeller may only include the said one conveyor channel. Alternatively, however, two, three or more delivery channels may be provided, each of which may have a spiral course and nested from each other at the outer edge region inlet to a common pressure outlet or separate pressure outlets in the center of the impeller can lead. The inlets arranged on the edge section of the impeller can in this case be offset relative to one another in the circumferential direction, with 180 ° in the case of two conveyor channels, for example with respect to one another.

A drive device for driving the impeller can basically be designed differently, for example, an electric motor can be used, which can be operated for example by means of a solar panel. Alternatively or additionally, a mechanical drive device for driving the impeller may be provided, for example, a hydropower turbine or a wind turbine can provide the drive energy.

The invention will be explained in more detail with reference to preferred embodiments and associated drawings. In the drawings show:

1 shows a schematic representation of a turbomachine with a

Impeller, which has a spiral conveying channel and with the generated pressurized water and the generated compressed air drives a turbine wheel,

1, which uses the generated pressurized water and the compressed air generated to drive a turbine wheel, in which the driven turbine wheel shows the compressed air rising on the right half of the turbine wheel, which drives the turbine blades, FIG.

Fig. 3: a schematic representation of a turbomachine similar to the preceding figures, wherein between the compressed air and the pressurized water generating impeller and driven by the compressed air turbine wheel, which may be similar to the embodiment of Fig. 2, a hydraulic compressor for separating compressed air and pressurized water is provided,

4 shows a schematic representation of a turbomachine according to a further embodiment, the impeller of which drives a water wheel or a pressure turbine with the pressurized water and the compressed air generated thereby, wherein different variants of a drive device for driving the impeller comprising a wind turbine, a photovoltaic system and a hydropower turbine are shown

5 shows a schematic representation of the turbomachine from FIG. 4 with a modified guide of the pressurized water driving the pressure turbine and the compressed air,

6 is a schematic representation of the impeller of a turbomachine similar to the preceding figures, wherein the impeller is accommodated with the spiral conveyor channel in a pump wheel enclosing pump housing, 7 is a schematic representation of the impeller and its spiral conveying channel of a turbomachine similar to the preceding figures, wherein the results in the turns of the conveyor channel pressure water and compressed air batches are shown,

8 shows a schematic representation of a turbomachine having a pump wheel having a spiral conveying channel, similar to the preceding embodiments, wherein the pump wheel is mounted for floating use on waters on a raft-type pontoon with buoyant bodies and a photovoltaic system is provided for driving the pump wheel,

9 shows a schematic representation of the arrangement of a single-channel impeller whose delivery channel is arranged in a plane,

10 shows a schematic representation of an impeller with a plurality of spiral-shaped delivery channels, which are arranged axially next to one another in different pump chambers of graduated diameter,

Fig. 11: a schematic representation of a turbomachine with several

Pump wheels, each with a spiral-shaped delivery channel, wherein the pump wheels are arranged axially spaced side by side on a common axis, wherein in the said axis, a common pressure outlet channel is integrated,

12 is a schematic representation of a turbomachine similar to the preceding figures, wherein the impeller and its spiral conveyor channel is associated with an adjusting device for adjusting the depth of immersion of the conveyor channel in a reservoir, said adjusting means comprises a storage device for damming the water level in the reservoir, 13 shows a schematic representation of a turbomachine which, similar to the previous embodiments, has a wheel with a spiral conveying channel, the wheel and thus the angular position of the spiral conveying channel being adjustable by a control device and the conveying channel being used as flushing device for a water basin,

14 is a schematic representation of a turbomachine similar to the preceding embodiments, wherein the spiral-shaped delivery channel of the impeller does not have a continuously curved course, but a polygonal, polygonal contouring and is composed in segmental construction of a plurality of channel segments,

15 shows a schematic representation of a turbomachine similar to the preceding figures, which has an impeller with a spiral conveying channel, wherein the impeller is housed in a Pumpenradge- housing with overhead air supply and the drive of the impeller is made higher lying, and

Fig. 16: a schematic representation of a turbomachine similar to the preceding figures, having a pump impeller with a spiral conveying channel, wherein the impeller is housed in a closed pump housing, which is connected via a suction line to a reservoir and the pressure line of the impeller has as a pressure drain ,

As shown in FIG. 1, the turbomachine 1 may comprise a substantially upright pump impeller 2, which may be driven in rotation by a suitable drive device 3, which may comprise, for example, an electric motor 4 about a horizontal pump wheel axis 5. Said impeller 2 may comprise a spiral-shaped delivery channel 6, which may comprise an inlet arranged on the edge, for example on the outer circumference of the impeller 2, and a preferably central, substantially central discharge 8. Said inlet 7 may in particular be formed from the outer end to the outer opening cross-section of said conveying channel 6. The pressure outlet 8 can advantageously be arranged coaxially to the impeller axis 5 and / or centered centrally out of an end face of the pump impeller 2.

As shown in Fig. 1, the impeller 2 may comprise two parallel side and end walls 9 and 10, which may be formed for example by closed plates. Between said end walls 9 and 10, said conveying channel 6 extends, wherein here between the end walls 9 and 10, a circumferential conveying channel wall 11 can be spirally wound to lead from the edge-side inlet 7 inwardly to the central outlet 8.

The delivery channel thus advantageously extends in a plurality of turns which extend around the impeller axis 5 and are nested one inside the other. In the embodiment shown in Fig. 1, the spiral-shaped conveying channel 6 extends in the plane of the impeller 2, wherein all turns of said conveying channel 6 can lie in a plane perpendicular to the impeller axis 5.

As shown in FIG. 1, the impeller 2 partially immersed in a liquid, in particular water reservoir 12, so that a lower segment of the impeller 2 and thus a portion of the conveying channel 6 is submerged below the level 13 of the reservoir 12, while a residual, upper Part of the impeller 2 above said level 13 is located. The immersion depth can be set differently, it may be advantageous if the immersion depth is less than two thirds, preferably less than half of the impeller diameter. In particular, the immersion depth can be about one fifth to one third, for example, about one quarter of the impeller diameter, as shown in FIG. 1. Advantageously, an adjusting device 14 is provided for setting said immersion depth to vary the depth of immersion and thereby be able to control the ratio of compressed air to pressurized water, as has already been explained. Said adjusting means 14 may comprise a height adjusting device 5 for variably adjusting the height position of the impeller 2, for example, by displacing the pivot bearing in the height direction. Alternatively or additionally, a stowage device 16 can also variably set the level 13 of the reservoir 12, cf. Fig. 12, to thereby vary the depth of immersion. Alternatively or additionally, a floating device 17 may be provided with volume-variable or adjustable buoyancy bodies 18 when the impeller 2 is positioned floating, for example, on a raft-shaped floating device 17 on a body of water. By varying the volume of the buoyant bodies 18, the impeller can dip deeper or less deeply into the reservoir 12.

As FIG. 1 shows, the spiral-shaped delivery channel 6 can comprise a cross-section which is substantially constant along its spiral longitudinal extent or a uniform cross-sectional area. The pressure effect arises in the spiral conveying channel 6 by the gravity of the water in the individual turns in a rotary driving of the impeller 2. As Fig. 7 illustrates, the delivery channel 6, when its inlet 7 is below the level 13, liquid or water on, which then pushes in a further rotation of the impeller 2 in the turns of the conveying channel 6 inward. While the inlet 7 is above the level 13 and the impeller is further rotated, air enters the delivery channel 6 until its inlet 7 again meets the level 13 and dips into the reservoir 12. This alternately creates water and air packets in the delivery channel 6, which then screw by the rotation of the impeller 2 inwardly to the pressure outlet 8 out. This creates a pulsating pressure-air-water mixture, which is pressed out via the central pressure outlet 8. As shown in FIG. 1, the pump shaft 5 may be formed as a hollow shaft which leads out axially from the impeller 2 and by means of a rotary joint 19 with a stationary, that is not co-rotating pressure line 20 may be connected.

As further shown in FIG. 1, the compressed air / pressure water mixture generated by the impeller 2 can be introduced into a turbomachine 21 with a turbine wheel 22 to drive said turbine wheel 22, the rotational energy generated thereby being supplied via a generator 23, for example into electrical Energy can be converted. The mentioned turbomachine 21 may in this case be designed, for example, in accordance with the document DE 10 2012 008 161 A1 or the document DE 10 2013 008 859, so that reference may be made to the two abovementioned documents with regard to the details of the training of the turbofan engine 21.

As shown in FIG. 1, the pressurized water forced out of the flow engine 21 can advantageously be returned to the compressed air component contained therein in order to drive a pressure turbine or water wheel 24, which can be coupled to the impeller shaft 5 to recover some of the energy.

As FIG. 2 shows, the turbine wheel 22 of the flow engine 21 can also be driven only by the compressed air component which is generated by the impeller 2. The said compressed air can in this case be directed to the turbine wheel 22, as explained in more detail, for example, the document DE 10 2012 008 161.

In order to separate the compressed air generated by the impeller 2 from the pressurized water also generated, the impeller 2, an air-water separator 25 may be arranged downstream, for example in the form of a hydraulic compressor, as shown in FIG. About the pressure line 20, the compressed air / pressurized water mixture is placed in a pressure vessel 26, which has at its upper side at the upper portion of a compressed air outlet 27 which is above the adjusting in the pressure vessel 26 level. The introduced pressurized water can be discharged via a outside the self-adjusting level and below the compressed air outlet 27 pressure water outlet 28 exit from the separator 25, wherein the pressure water discharge is preferably performed at a level corresponding to at least the level height in the downstream flow engine 21. Again, the pressurized water may be fed back to a pressure turbine 24 to recover a portion of the energy, said pressure turbine 24 may be rotatably coupled to the impeller axis 5.

As shown in FIG. 4, the driving device 3 for driving the pump impeller 2 may be basically different. For example, an electric motor 4 can be provided, which drives the impeller axis 5 and can be fed from a battery 29, which in turn can be supplied with electric current from a photovoltaic system 30 and / or a wind turbine 31 or from another power generation plant. As shown in FIG. 4, a hydraulic power device 32 can feed the said battery 29 via a generator. Depending on availability requirements, the electric motor 4 may also be fed directly, that is, omitting the aforementioned battery 29, from the mentioned power generation plants.

In place of the electric motor 4 shown, if necessary, a direct mechanical drive of the pump impeller 2 may be provided, for example by a mechanical coupling with a wind turbine or a hydropower wheel or in a similar manner with a mechanical energy generator.

In the embodiment according to FIG. 4, the compressed air / pressurized water mixture produced by the impeller 2 drives a pressure turbine 33 or a water wheel, which can be coupled to a generator 23. Fig. 5 shows an alternative in which the compressed air-pressurized water mixture is guided in a different way through the pressure turbine 33 and is out there on the outlet side up to the level of the reservoir level 13.

As shown in FIG. 6, the impeller 2 may be received in a pump housing 34. Advantageously, one at a bottom region of the pump Wheel housing 34 provided inlet opening 35 may be provided, whose upper edge extends substantially at the level of the level 13 of the reservoir 12, so that the full cross section and the full immersion depth of the impeller 2 is available or maintained. As the left partial view of FIG. 6 shows, the pressure line 20 can be led away from the designed as a hollow shaft pump shaft 5 and thus the pressure outlet 8 up to provide the pressurized air compressed air mixture above the level 13 and to request there.

As shown in Fig. 7, however, may alternatively be provided a downward going away leading pressure line 20 to provide the pressurized air-compressed air mixture below the Pumpenradachse 5 and optionally. Also below the level 13 of the reservoir 12 and request, for example supply oxygen to an oxygen-poor body of water by means of the compressed air and to circulate the water in the reservoir 12.

As shown in FIG. 8, the turbomachine 1 can in this case be arranged or mounted or positioned on a floating device 17. Said floating device 17 may be designed, for example, in the manner of a raft or a pontoon and may comprise floating bodies or buoyancy bodies 18 which may carry a platform 36 or a support base on which the impeller 2 is mounted.

Advantageously, said buoyancy bodies 18 may be made variable with regard to their effective buoyancy volume, in order to be able to vary the floating height of the platform 36 and thus the immersion depth of the impeller 2.

As shown in FIG. 8, a photovoltaic system 30 can be arranged on the floating device 17 in order to be able to supply the drive device 3 for driving the impeller 2 with energy independently even on a larger body of water. As a comparison of FIGS. 9 and 10 shows, the impeller 2 may be single-channeled and comprise only one delivery channel in only one pumping chamber, cf. Alternatively, a plurality of pumping chambers 37 can be arranged directly next to one another and graduated in terms of their diameter, so that one, two, three or more pumping chambers become active depending on the depth of immersion. Advantageously, the plurality of pump chambers 37 and the pressure outlets 8 of the spiral delivery channels 6 provided therein may open into a common pressure outlet or a common pump shaft 5 designed as a hollow shaft, in order to convey via a rotary joint 19 into a common pressure line 20.

As shown in FIG. 1 1, a plurality of impellers 2 may be spaced from each other and arranged on a common impeller axis 5. The pumping chambers 37 formed in said pumping wheels 2 may each comprise a helical conveying channel 6 which opens into the common pumping wheel axis 5 designed as a hollow shaft in order to convey via a pivoting joint 19 into a common pressure line 20.

FIG. 12 shows the adjustment of the immersion depth of a pump wheel 2 via a storage device 16, which may comprise a height-adjustable storage plate 38.

As shown in FIG. 13, the turbomachine 1 or the wheel 2 previously described as a pumping wheel can be used not only as a pressure generator, but also - as it were in fluidic reversal - as a rinsing and / or cleaning device and / or water distributor.

In particular, pressurized water can also be conducted in the reverse direction through the conveying channel 6 described above, that is, introduced through the central pressure outlet 8 and discharged through the edge-side inlet 7.

Advantageously, in this case the wheel 2 or the conveying channel 6 can be assigned a rotary control device, by means of which the angular position of the lasses 7 (which acts as an outlet here) can be adjusted to control the position and / or direction of the discharged pressurized water can.

As shown in Fig. 13, the wheel 2 may be provided with the spiral conveying channel 6 in a water basin 39 and / or rinse and clean said water basin 39. For example, said tank 39 in the filled state can form the reservoir 12 in which the turbomachine 1 operates in the pumping operation described above in order to obtain pressurized water and compressed air. If the water basin 39 is drained, the same turbomachine 1 can be used as a cleaning or flushing device.

As shown in FIG. 14, the delivery channel 6 may also have a polygonal, polygonal contouring or configuration. The delivery channel 6 extends here also spirally, but not with a harmonic, continuous curvature, but in the form of a polygon with straight sections, which are connected to each other if necessary. Rounded corners or join each other. For example, the octagonal, overall spiral-shaped design of the conveying channel 6 shown in Fig. 14 may be provided, in which the circumferential channel walls extend straight and may be formed by flat metal strips.

In particular, the impeller 2 and / or the delivery channel 6 may be composed of segmental design of several segments, which can be produced by the polygonal and / or polygonal design of the conveying channel 6 in a simple manner.

The aforementioned polygonal segments which are angled relative to one another and form the circumferential wall of the conveying channel 6 can, similar to the previously described embodiments, be seated between two end walls 9 and 10 of the impeller 2 or be accommodated therebetween. As FIG. 15 shows, the impeller 2 can be accommodated in an impeller housing 34 which can have an air supply 40 on an upper side. The drive of the impeller 2 can be moved relative to the pump axle 5, for example, by a belt stage upwards, so that the drive means 3 and / or the electric motor 4 is located well above the top of the impeller 2, see. Fig. 15.

As shown in FIG. 16, said impeller housing 34 may also be designed to be closed, with an interior of the impeller housing 34 communicating with the reservoir 12 only via an intake line 41. The compressed air generated by the impeller 2 and the pressure water also generated is, as described above, conveyed away via a connected by a rotary joint 19 pressure line 20, wherein the discharge can be done up here, see. Fig. 16.

Even in the embodiment shown in FIG. 16, the impeller 2 only partially submerges in the liquid reservoir present in the impeller housing 34, cf. the registered inside the housing level 13a.

Claims

claims

Turbomachine for the production of compressed air and pressurized water, comprising an impeller (2) comprising at least one spiral conveying channel (6) having an inlet (7) at an outer edge portion of the pump impeller (2) and an inner portion of the pump impeller (2 ) has a pressure outlet (8), wherein the impeller (2) partially below and partially above the level (13) of a reservoir (12) is arranged, so that the inlet (7) of the conveying channel (6) during rotation of the impeller (2) cyclically dips into the reservoir (12) and emerges from it.

Turbomachine according to the preceding claim, wherein the conveying channel (6) is formed continuously and without interruption.

3. Turbomachine according to one of the preceding claims, wherein the conveying channel (6) engages catchy and fork-free from the inlet (7) to the pressure outlet (8).

4. Turbomachine according to one of the preceding claims, wherein the conveying channel (6) from the inlet (7) to the pressure outlet (8) has a constant cross-sectional area.

5. Turbomachine according to one of claims 1 to 3, wherein the conveying channel (6) has a cross-sectional area which decreases continuously, in particular steadily, from the inlet (7) to the pressure outlet (8).

6. Turbomachine according to one of the preceding claims, wherein the conveying channel (6) has a continuously curved course.

7. Turbomachine according to one of claims 1 to 5, wherein the conveying channel (6) has a polygonal, polygonal course and is composed in segmental construction of a plurality of interconnected channel segments.

8. Turbomachine according to one of the preceding claims, wherein the conveying channel (6) is formed lying in a plane and has a plurality of intermeshing winding sections.

9. Turbomachine according to one of claims 1 to 7, wherein the conveying channel has a slope in the manner of a screw flight and the inlet (7) and the pressure outlet (8) are mutually axially spaced in the direction of Pumpenrad- axis (5).

10. Turbomachine according to one of the preceding claims, wherein the impeller (2) has only one conveying channel (6).

11. Turbomachine according to one of claims 1 to 9, wherein the impeller (2) has a plurality of conveying channels (6).

12. Turbomachine according to one of the preceding claims, wherein a plurality of impellers (2) and / or a plurality of pumping chambers (37) are provided and arranged on a common impeller axis (5).

13. Turbomachine according to the preceding claim, wherein the plurality of pump wheels (2) and / or a plurality of pumping chambers (37) have different diameters, in particular with respect to their diameter are stepped to each other.

14. Turbomachine according to one of the preceding claims, wherein an adjusting device (14) for adjusting the depth of immersion of the impeller (2) is provided in the reservoir (12).

15. Turbomachine according to the preceding claim, wherein the adjusting device (14) has a height adjustment device (15) for height adjustment of the impeller (2) relative to a support base.

16. Turbomachine according to one of the two preceding claims, wherein the adjusting means (14) comprises a storage device (16) for damming the reservoir (12) and / or adjusting the level (13).

17. Turbomachine according to one of the three preceding claims, wherein the adjusting device (14) has a floating device (17) with Auftriebskör- pern (18) whose buoyant effective volume is variable, wherein the impeller (2) mounted on said floating device (17) is.

18 turbomachine according to the preceding claim, wherein on the floating device (17) a photovoltaic system and / or a wind turbine for supplying energy to the drive means of the impeller (2) is provided.

19. Turbomachine according to one of the preceding claims, wherein the pressure outlet (8) of the impeller (2) is led out coaxially to the impeller axis (5) from the pump impeller (2) and formed by the impeller shaft formed as a hollow shaft (5).

20. Turbomachine according to the preceding claim, wherein a hinge (20) for connecting the pressure outlet (8) with a pressure line (20) is provided.