EP1299642B1 - Hydraulic turbomachine - Google Patents

Abstract

The invention relates to a hydraulic turbomachine which is used to convert energy. The aim of the invention is to provide a hydraulic turbomachine which exclusively uses the flow output, affected by atmospheric pressure (pL), of a water column which rises towards a rotor disk (3) in a suction chamber (1), making it available to a consumer in the form of end energy (EN). The inventive hydraulic turbomachine is provided with an annular water circuit flowing in a radial direction with respect to the axis of a generator (6). Said circuit comprises a conducting chamber (7) and is coaxially arranged inside a tub-shaped flow chamber (8) around the axis of the generator (6) in a container (9). The rotor disk (3) rotates horizontally in relation to the axis and the energy difference between supplied and discharged energy on the rotor disk (3) corresponds to the sum of the energy provided by the atmospheric pressure (pL) and the energy provided by the drive motor (Em). The generator (6) is used to make the energy provided by the drive motor (5) available once again.

Description

The invention relates to a hydraulic flow machine for Energy conversion for the energy supply of energy consumers of any kind.

From Fritz Dietzel, turbines, pumps and compressors; 1st edition 1980, 195-199 and 260-261, as well as from Dubbel, Volume II, 13th edition 414-415 hydraulic turbomachines such as centrifugal pumps known, which are characterized by a fixed suction tube, that on the one hand into the center of an impeller rotating to Saugrohrachse with radially from the center to the outer diameter of the impeller extending vane channels and on the other hand in a water reservoir leads to a certain by means of the impeller Water quantity / time unit from the water reservoir to a certain To bring delivery height. The drive power of a pump is needed to set the impeller in rotation, the atmospheric Air pressure the water column in the suction pipe and from there into the impeller suppressed. In this case, the water from the flow direction in the suction pipe in the direction of flow in the impeller are deflected. By means of the Torque on the impeller and the centrifugal force must be the water within the blade channels of the impeller from that in the center of the Impeller existing smaller rotational speed on the am Outer diameter required circulation and exit velocity accelerated and transported. The required Acceleration forces must be provided by the drive of the pump Will be provided. When leaving the paddle wheel that hits Water on a fixed stator of the pump or in a Spiral housing, whereby the exit velocity of the water at Impeller outlet is converted into pressure energy. The water is going out the spiral housing into a discharge nozzle, in which it on his Drive power of the impeller from the delivery and the Delivery volume of the water / per unit time and of the Energy losses determined. An essential feature of conventional centrifugal pump is that for in the impeller inflowing flow, the drive power of the engine is not in Claimed. The drive motor accelerates this into the Impeller inflowing water on the exit velocity of the the impeller flowing water. Due to the centrifugal force of the impeller circulating water creates a negative pressure compared to the pressure of prevails at the suction tube entrance. The resulting overpressure on the Intake manifold inlet lets the water rise in the intake manifold and into the Impeller flow. Part of the total head of the centrifugal pump However, not from the performance of the drive motor, but from the Overpressure on the intake manifold.

Next are water turbines, z. B. Francis turbines; known in hydroelectric power plants. The hydropower plants use the energy of dammed water by means of water turbines to generate electricity in generators. The performance of these turbines increases directly with the drop height and amount of water. The height of the fall is achieved by the damming of flowing waters, for example, of large rivers. The energy conversion takes place in the blades of guide and impellers of the turbine. The water flowing to the guide vanes is first accelerated in the guide vanes to the entry speed in the impeller. An increase in the speed of the water is achieved in that the outlet cross-sections of the guide vanes are narrowed by corresponding angular design with respect to the inlet cross sections of the guide vanes. The influence of the supplied flow energy on the impeller blades causes a torque on the turbine shaft. This is the working capacity of a water flow driving the turbine wheel. The described hydropower plants are localized and require considerable investment costs. Due to the seasonal water supply of different sizes, the available amount of water can fluctuate very strongly, which in turn has a great influence on the amount of energy available or to be dispensed to the consumer.
EP 0 545 280 A1 also discloses a drive device with a turbine fixedly arranged on a rotatable shaft, which can be acted upon by a liquid, in particular water, and set into rotary motion together with the shaft, characterized in that the shaft is vertical is arranged that on the shaft this concentrically surrounding a conically upwardly flared tube is fixed and which has an overflow in the upper edge with an underneath, fixed collecting container for overflowing liquid, and that the turbine via at least one outgoing from the collecting container Downpipe is acted upon from below with the liquid.
DE 196 47 476 A1 discloses a pneumatic hydraulic centrifugal drive for all types of energy movement and power generation, characterized in that record by a rotor with one or more integrated chambers / tanks water, oil or other liquids and centrifuged by acceleration / compacted and in a pressurized housing presses, wherein the housing in which the rotor is driven is under atmospheric pressure or gas pressure and filled with water or other liquids. The chambers of the rotor are filled via the rotor axis with liquid and thrown by the rotational movement of the rotor to the outside, whereby centrifugal forces arise, which throw the water through the arranged on the chambers nozzles from the rotor in the pressurized housing, at the bottom itself collects the water and a turbine is supplied, which returns the water to a power generator and at the same time in the rotor axis.
The above-described solutions are based on the basic principle of buoyancy of a water column in the center about a rotating axis, from where the liquid is guided radially in a turbine wheel and forced by centrifugal forces to the outside, the disadvantages described above occur.
The hydraulic turbomachine described in WO 00/29747 can not eliminate these disadvantages, since in this solution, the water is not supplied to the suction chamber with a trough-shaped guide, the centrifugal force does not form a balance of forces with the atmospheric pressure at the exit of the hub and the engine Water in the hub must accelerate to exit velocity.
The invention is therefore an object of the invention to provide a hydraulic fluid flow machine that uses only due to the atmospheric air pressure acceleration of the flow circuit of a rising in a suction chamber to an impeller water column and provides as final energy to a consumer.
The object is achieved by a hydraulic turbomachine with the characterizing features of claim 1.

The trough-shaped flow space according to the invention of the hydraulic fluid machine inside a closed container, which at the same time contains the water supply required for the function of the machine has the great advantage, in contrast to previous solutions, that only the pressure energy of the atmospheric air pressure, reduced by all losses, is delivered as final energy to a consumer.
Particularly noteworthy is that can act through an opening between the two inner guide walls in front of the inlet of the suction chamber within the trough-shaped flow space of the atmospheric pressure on the water level and arranged between the flow space and container compensating pipe allows the adjustability of the water level in the trough-shaped flow space. The height of the water level in the container by known methods such as manually through a window or appropriately arranged float or sensors that trigger a signal upon reaching a determinable level and optimally determined by a the application conditions adapted water inlet and outlet system. The atmospheric air pressure exerts a pressure on the water level in the trough-shaped flow space and causes, due to the force balance generated by the impeller, the water is accelerated in the suction chamber, via the guide vanes in the horizontally about the axis of the generator rotating impeller and from this is passed into the Leitraum, where it can be deflected and fed back to the suction chamber.
The speed energy of the exit velocity of the water from the impeller adds to the pressure energy of the atmospheric Luftrucks and by cross-sectional constriction in the vane area, the water is accelerated again to the required inlet velocity into the impeller.

It is also advantageous that the drive motor, the impeller in a certain speed, which exceeds the speed of rotation of the Water in the impeller generated centrifugal force at the outlet openings of the Impeller generates a pressure that the back pressure to the Outlets corresponds and this is directed against, whereby an equilibrium of forces arises at the impeller outlet.

Is particularly advantageous, according to claim 2, the structural design of the trough-shaped flow space coaxial about the axis of the Generator in a container with a required water supply is arranged. The outer guide wall of the trough-shaped Flow space forms together with two inner guide walls a suction chamber and a Leitraum, between which on the axis of the generator and horizontally rotating about this axis Impeller is guided with impeller blades, taking all components together form the annular water cycle.

The constructive connection of the outer guide wall with the inner Guide walls of the flow space, according to claim 3, supported the function of the turbomachine according to the invention advantageous

A second variant of the hydraulic according to the invention Turbomachine, according to claim 4, provides that at one, by a desired lower flow velocity in the guide and suction chamber conditional, reduced exit velocity of the water from the Impeller in place of the vanes one with the impeller horizontally around the Axis of the generator rotating accelerating wheel is provided which the missing speed energy for the Entry speed of water into the impeller with the Drive motor compensates and the ingress of atmospheric air prevented in the suction chamber.

It should also be emphasized, according to claim 5, that only the pressure energy introduced by the atmospheric air pressure, reduced by all occurring energy losses, from the generator as Final energy can be supplied to a consumer and by the Drive motor introduced energy through the generator back to the Drive motor is traceable. This is ensured by the fact that the Energy difference between supplied energy at the inlet openings and discharged energy at the outlet openings of the impeller of the Sum of the atmospheric air pressure introduced and corresponds to the energy introduced by the drive motor and as Torque is transferred from the impeller to the generator.

Finally, the amount of energy to be delivered is the inventive hydraulic turbomachine of the constructive sizes of individual components and by measuring the drive power for the energy supply in the start phase of the plant and to compensate for the determined conditional losses, the yield of final energy in the hydraulic turbomachine with guide vanes is greater than when using the accelerator, because by the accelerator additional energy losses are recorded.

The advantages of the hydraulic turbomachine according to the invention exist, due to the structural design and the so guaranteed optimization of space requirements in the absolute Adaptability to local conditions and Performance requirements, associated low investment and Maintenance costs and a long service life. The machine works absolutely independent of day or seasons, allows one Cost-effective energy storage, is through the use of the atmospheric pressure as secondary energy absolute environmentally friendly and produces no waste. It does not need any Water gradient, no natural and / or jammed water source and is thus not localized.

Fig. 1

einen Schnitt durch die hydraulische Strömungsmaschine mit Leitschaufeln und ohne Beschleunigungsrad,

Fig. 2

einen Schnitt A-B aus Fig.1,

Fig. 3

einen Teilschnitt C- D aus Fig.1,

Fig. 4

einen Ausschnitt Z aus Fig.3,

Fig. 5

die Energiebilanz der erfindungsgemäßen hydraulischen Strömungsmaschine mit Leitschaufeln,

Fig. 6

einen Schnitt durch die hydraulische Strömungsmaschinen ohne Leitschaufeln mit Beschleunigungsrad,

Fig. 7

einen Schnitt E- F aus Fig.6,

Fig. 8

einen Teilschnitt G- H aus Fig.6,

Fig. 9

einen Ausschnitt W aus Fig.8,

Fig. 10

eine Energiebilanz der hydraulischen Strömungsmaschine mit Beschleunigungsrad.

The invention will be described below with reference to two embodiments. The drawings show in

Fig. 1

a section through the hydraulic fluid machine with vanes and without accelerator,

Fig. 2

a section AB of Figure 1,

Fig. 3

a partial section C-D of Figure 1,

Fig. 4

a section Z of Figure 3,

Fig. 5

the energy balance of the inventive hydraulic fluid machine with vanes,

Fig. 6

a section through the hydraulic turbomachinery without vanes with accelerator,

Fig. 7

a section E-F of Figure 6,

Fig. 8

a partial section G-H of Figure 6,

Fig. 9

a section W from FIG.

Fig. 10

an energy balance of the hydraulic fluid machine with accelerator.

Fig.1 and Fig.3 show an embodiment of the invention Hydraulic fluid machine with vanes 2, which with a annular water circuit according to the invention with a radial, to a Axle 6 'of a generator 6, extending flow direction is equipped. The annular water circuit consists of the suction chamber 1 with Suction chamber inlet 1 'and suction chamber outlet 1 ", in the area of Saugraumausgangs 1 "arranged vanes 2, the impeller 3 with Impeller blades 3 ', arranged on the inner diameter D1 Inlet openings 3 "and arranged on the outer diameter D2 Outlet openings 3 '"and a Leitraum 7 with inlet opening 7' and Outlet opening 7 ", within a trough-shaped Flow space 8 coaxially about the axis 6 'of the generator 6 in one Container 9 is arranged, wherein the impeller 3 between the suction chamber 1 and the Leitraum 7 horizontally to the axis 6 'rotates and the transition from the guide vanes 2 to the impeller 3 preferably by a non-contact seal 24 is sealed according to Figure 4. Of the trough-shaped flow space 8 consists of a, in a container. 9 arranged non-positively, outer guide wall 8 ', with a inner guide wall 8 "forms the suction chamber 1 and over in the Suction chamber 1 arranged vanes 2 with the outer Guide wall 8 'is connected and with an inner guide wall 8 "'forms the Leitraum 7 and guide webs 17 with the outer Guide wall 8 'is connected. Between the two inner ones Guide walls 8 "and 8 '" is in the inner bottom area of the trough-shaped flow space 8 an opening arranged. Furthermore is located in this floor area, a water level 4 ', the for example, via a compensating pipe 10 to the container 9 is adjustable. Furthermore, the container 9 is preferably with two container chambers 12 and 13 equipped. When starting the machine is from the For example, higher arranged container chamber 13 preferably via a directional control valve 14, water 4 filled in the container 9, whereby the Air from the suction chamber 1 and the Leitraum 7 and from the impeller. 3 is displaced. After reaching the required speed or after Completion of the startup process is now in the container 9 excess Water 4 via the preferably second directional control valve 14 in the Container chamber 12 passed. If the water level is too low 4 'in the Container 9 or in the flow chamber 8 is 4 of the water Container chamber 12 via, for example, a check valve 15 and a Pump 16 pumped into the container chamber 13 and from there via the first Directional valve 14 back to the container 9 back to the water level 4 'back to the level required for the function of the machine was reduced. For the detection and regulation of the water level 4 ' in the container 9 conventionally known methods are provided as the manual detection through a viewing window and its manual Regulation or detection via a float or sensor and by these triggered electrical signals to the directional control valves 14. The Generator 6 is arranged outside of the container 9 so that he for example via a coupling 22 and a bearing 23 with the axis 6 ' is connected, wherein on the, in the container 9 vertically protruding Axial part as a transmission element 20, 21 preferably one Pulley 20 is arranged via a belt 21 with a second pulley 20 on the axis of the also outside the Container 9 arranged drive motor 5 are interconnected. At the, in the container 9 vertically projecting in the free end of the axis 6 ', the impeller 3 is arranged on another bearing 23 so that it can rotate horizontally about the axis 6 '. In the container 9 is coaxial the axis 6 'of the flow space 8 is arranged, in which the circular Water circulation is installed, whereby the the floor area of the Flow space 8 opposite opening between the suction chamber. 1 and Leitraum 7 through the horizontally about the axis 6 'rotating impeller. 3 is covered. The drive motor 5, which requires for the starting process is, drives the impeller 3 and compensates for part of the losses of Energy conversion into the impeller 3. About the impeller 3 is the Generator 6 driven. This generates the circulating in the impeller 3 Water 4 a centrifugal force Fz. The centrifugal force Fz in turn creates a Pressure pz at the outlet openings 3 '"of the impeller 3, the atmospheric pressure equals pL and this counteracted is, whereby the entry of air into the impeller 3 is prevented. to same time arises due to the centrifugal force Fz at the inlet openings 3 " of the impeller 3, a negative pressure. The emerging from the impeller 3 Water 4 flows at a defined speed c2 in the Leitraum 7, is deflected by the shape and again the suction chamber. 1 fed. Here is the height of the maintenance of centrifugal force Fz in the impeller 3 required entry speed c1 of the water. 4 in the impeller 3 depending on a circulation speed cu1 am Inner diameter D1 and a circulation speed cu2 am Outer diameter D2 of the water 4 in the rotating impeller 3. The Circulation speeds cu1 and cu2 are in turn determined by the Centrifugal force Fz of the water 4 in the impeller 3 determined. The Entry speed c1 the water 4 in the impeller 3 must be in the suction chamber 1 can be accelerated back to the required size.

This is achieved by, according to Figure 2, the outlet cross sections of Guide vanes 2 in the suction chamber 1 by corresponding angle versions be narrowed relative to the inlet cross sections of the guide vanes 2 and according to the continuity equation one Speed increase of the water 4 is achieved. For this Speed increase must pressure energy into speed energy being transformed. Due to, by the centrifugal Fz in the Impeller 3 at the inlet openings 3 "generated negative pressure is this Pressure energy from the atmospheric air pressure pL in the suction chamber 1 issued. After entering the water 4 in the impeller 3 is the Speed increase by the shape of the impeller blades 3 'again converted into pressure. This pressure generates a torque on the impeller 3. Through this torque, the energy from the impeller 3 to the Generator 6 delivered. The energy difference between supplied Energy at the inlet openings 3 "and dissipated energy to the Outlet openings 3 '"of the impeller 3 corresponds to the of atmospheric air pressure pL and that of the drive motor 5 introduced energy EM. Thus, the pressure energy of the atmospheric air pressure pL converted in to the occurring Energy losses of the turbine Etv, the propulsion engine Emv and the Generator's EGV reduced, final energy EN.

Figure 5 shows a scheme of the resulting energy balance for a Hydraulic turbomachine according to the invention with guide vanes 2 according to the first embodiment, wherein in addition to the already the factors influencing the water density, p, the efficiencies η the drive motor 5 and the generator 6, the suction chamber 1 and the Impeller 3 are taken into account.

FIGS. 6 and 8 show a second embodiment of the invention inventive hydraulic fluid machine with a Accelerator 11 and without vanes 2, which with a annular water circuit according to the invention with a radial, to a Axle 6 'of a generator 6, extending flow direction is equipped. The annular water cycle is different from that of the first one Embodiment in that instead of the guide vanes. 2 between the suction chamber 1 and the impeller 3, an accelerator 11 is arranged with the impeller 3 about the axis 6 'of the generator 6, wherein the bottom of the flow area 8 opposite lying opening between the suction chamber 1 and Leitraum 7 through the horizontally about the axis 6 'rotating accelerator 11 and the Impeller 3 is covered and the transition from the Saugraumausgang 1 "to the acceleration wheel 11 according to Figure 9 by a non-contact Seal 24 is sealed. This embodiment is preferred then used when the water in the Leitraum 7 and the suction chamber. 1 should have a low flow rate. The circulation speed cu2 of the water 4 in the impeller 3 is then too low to prevent penetration of the atmospheric air pressure pL in the suction chamber 1 to avoid. The acceleration wheel 11 with inlet openings 11 'on Inner diameter D3 and outlet openings 11 "on the outer diameter D4 takes over in this case the additional acceleration of the Suction chamber 1 leaking water 4 from the inlet velocity c3 on the exit velocity c4 and the required Entry speed c1 of the water 4 in the impeller 3. In this additional acceleration of the water 4 in the accelerator 11th also increases a circulation speed cu3 at the inner diameter D3 to a peripheral speed cu4 at the outer diameter D4 of Acceleration wheel 11. The orbital velocities cu3 and cu4 of the Water 4 in the accelerator 11 generate in this case, the Centrifugal force Fz, which by the apparent from Fig.7 blade assembly and Form in the accelerator wheel 11 and the impeller 3 is supported. The Energy required for this is supplied by the drive motor 5. Of the Energy amount is, however, by the larger torque output of the Impeller 3 to the generator 6 the drive motor 5 again for Provided. As a result, the services to be transferred in Drive motor 5, in the impeller 3 and in the generator 6 larger. Furthermore the power transmission of the acceleration wheel 11 still comes added. The energy losses increase significantly, causing the final energy EN to be given off from the atmospheric air pressure pL introduced and from the generator 6 a consumer available can be made is less than when running with Guide vanes 2.

10 shows a schematic of the resulting energy balance for a inventive hydraulic fluid machine without vanes 2 with an accelerator 11 after the second Embodiment, in addition to those already listed Influence factors the water density p, the efficiencies η of the Drive motor 5 and the generator 6 of the suction chamber 1, the impeller 3, and the accelerator 11 are taken into account.

List of used reference numbers

1

suction chamber,

1'

Saugraumeingang,

1"

Saugraumausgang,

2

vanes,

2 '

Leitschaufelausgang,

3

Wheel,

3 '

Impeller blades,

3 '

Inlet openings,

3 ''

Outlet openings

4

Water,

4 '

Water level

5

Drive motor,

6

Generator,

6 '

Axis of the generator,

7

directing space,

7 '

Leiraumeingang,

7 "

Leitraumausgang,

8th

Flow space,

8th'

outer guide wall,

8th"

inner guide wall,

8th'"

inner guide wall

9

Container,

10

Balance pipe,

11

accelerating wheel,

11 '

Inlet openings of the accelerator wheel,

11 "

Outlet openings of the accelerator wheel,

12

Container chamber,

13

Container chamber,

14

Way valve,

15

Check valve,

16

Pump,

17

Guide webs,

18

Guide webs,

19

Guide webs,

20

Pulley,

21

Belt,

22

Clutch,

23

Camp,

24

Poetry,

D1

Inner diameter of the impeller,

D2

Outer diameter of the impeller,

D3

Inner diameter of the accelerator wheel,

D4

Outer diameter of the accelerator wheel,

c1

Entrance speed into the impeller,

c2

Exit velocity from the impeller,

c3

Entrance speed into the acceleration wheel,

c4

Exit velocity from the accelerator wheel,

CU1

Rotational speed at the inlet of the impeller,

cu2

Rotational speed at the exit of the impeller,

cu3

Rotational speed at the entrance of the accelerator wheel,

CU4

Rotational speed at the output of the accelerator wheel,

u1

Rotational speed at D1 of the impeller,

u2

Rotational speed at D2 of the impeller,

u3

Rotational speed at D3 of the accelerator wheel,

u4

Rotational speed at D4 of the accelerator wheel,

w

Flow velocity of the water at the blade wall,

α1

Entry angle on the impeller.

α2

Exit angle on the impeller,

α3

Entrance angle to the accelerator wheel,

α4

Exit angle at the accelerator wheel,

β1

Blade angle at the entrance of the impeller,

β2

Blade angle at the exit of the impeller,

β3

Blade angle at the output of the accelerator wheel,

β4

Blade angle at the entrance of the accelerator wheel,

pL

atmospheric pressure,

ρ

Density of water,

Fz

centrifugal,

pz

Centrifugal force,

η

efficiency,

em

Energy of the drive motor,

etv

Loss turbine,

emc

Loss of drive motor,

Ebv

Loss of acceleration wheel,

Egv

Loss generator,

EN

Final energy.

Claims (5)

1. A hydraulic turbo-machine, comprising a shaft (6'), a suction chamber (1), guide vanes (2) and a rotating rotor (3) having rotor blades (3') that are filled with water (4), a drive motor (5) and a generator (6), a ring-shaped water cycle having a direction of flow that runs radially to an axis (6') of the generator (6), a guide chamber (7), a flow chamber (8), that are situated coaxially around the axis (6') of the generator (6) in a container (9), characterized in that the flow chamber (8) is tub-shaped and in front of a suction chamber inlet (1') of the suction chamber (1) and provided with an opening in which the water level (4') to the container (9) can be regulated,
   wherein in the guide chamber (7) the water (4) emitted from the turbine (3) may be guided via a guide chamber outlet (7") of the guide chamber (7) to the suction chamber inlet (1') and fed back to the suction chamber (1),
   wherein the drive motor (5) keeps the turbine (3) rotating at a certain speed in order to achieve an equilibrium of forces between the atmospheric air pressure as a centripetal force and the centrifugal force at outlets (3"') of the rotor (3),
   and wherein an energy difference arises between energy fed in at inlet ports (3") and energy led away at the outlet ports (3"') of the turbine (3), which corresponds to the sum of the pressure energy of the atmospheric air pressure (pL) introduced at the suction chamber inlet (1') and an introduced energy (EM) of the drive motor (5), and which is transferable from the turbine (3) to the generator (6) as torque.
2. Hydraulic turbo-machine according to Claim 1, characterized in that the tub-shaped flow chamber (8) comprises an outer guide wall (8'), which with an inner guide wall (8") encloses the suction chamber (1) with guide vanes (2), and with an inner guide wall (8"') encloses the guide chamber (7), the turbine (3) being situated and rotating between the suction chamber (1) with guide vanes (2) and the guide chamber (7), which together form the ring-shaped water circuit.
3. Hydraulic turbo-machine according to Claim 2, characterized in that the inner guide wall (8") is connected by the guide vanes (2) to the outer guide wall (8') and the inner guide wall (8"') is connected by guide ties (17) to the outer guide wall (8'),
   or wherein the inner guide wall (8") is connected by guide ties (18) to the outer guide wall (8') and the inner guide wall (8"') is connected by guide ties (19) to the outer guide wall (8').
4. Hydraulic turbo-machine according to Claim 1, characterized in that at a reduced emition speed (c2) of the water (4) from the turbine (3), instead of the guide vanes (2) an acceleration wheel (11) compensates for the lack of speed energy for the entry speed (c1) of the water (4) into the rotor (3) by means of the drive motor (5), where the acceleration wheel (11) rotates with the rotor (3) horizontally around the axis (6') of the generator (6).
5. Hydraulic turbo-machine according to Claim 1, characterized in that the energy (EM) introduced by the drive motor (5) may be routed back to the drive motor (5) by the generator (6), and exclusively the pressure energy of the atmospheric air pressure (pL) introduced into the suction chamber (1), reduced by occurred energy losses can be directed to a consumer by the generator (6) as final energy (EN).

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