EP4481188A1 - Dispositif de conversion d'énergie - Google Patents

Dispositif de conversion d'énergie Download PDF

Info

Publication number: EP4481188A1
Authority: EP; European Patent Office
Prior art keywords: fluid; turbine; conversion device; energy conversion; pressure vessel
Prior art date: 2023-06-23
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.): Pending

Application number

EP24183763.2A

Other languages

German (de)

English (en)

Inventor

Tobias Zeh

Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)

Individual

Original Assignee

Individual

Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)

2023-06-23

Filing date

2024-06-21

Publication date

2024-12-25

2024-06-21 Application filed by Individual filed Critical Individual

2024-12-25 Publication of EP4481188A1 publication Critical patent/EP4481188A1/fr

Status Pending legal-status Critical Current

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Classifications

- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B13/00—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates
- F03B13/06—Stations or aggregates of water-storage type, e.g. comprising a turbine and a pump
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2260/00—Function
- F05B2260/60—Fluid transfer

Definitions

the invention relates to an energy conversion device.
An energy conversion device in particular a fluid power plant device, with a fluid reservoir for storing a fluid, with a downpipe connected to the fluid reservoir, with a turbine connected downstream of the downpipe and intended to convert a kinetic energy of the fluid, which can be fed from the fluid reservoir via the downpipe to the turbine, into a rotational movement of an output shaft of the turbine, and with a generator intended to convert the rotational movement of the output shaft into electrical energy, has already been proposed.
the object of the invention is in particular to provide a generic device with improved properties in terms of efficiency.
the object is achieved according to the invention by the features of patent claim 1, while advantageous embodiments and further developments of the invention can be found in the subclaims.
the invention is based on an energy conversion device, in particular a fluid power plant device, with a fluid reservoir for storing a fluid, with a downpipe which is connected to the fluid reservoir, with a turbine which is connected downstream of the downpipe and is intended to convert a kinetic energy of the fluid which can be fed from the fluid reservoir via the downpipe to the turbine into a rotational movement of an output shaft of the turbine, and with a generator which is intended to convert the rotational movement of the output shaft into electrical energy.
an energy conversion device in particular a fluid power plant device, with a fluid reservoir for storing a fluid, with a downpipe which is connected to the fluid reservoir, with a turbine which is connected downstream of the downpipe and is intended to convert a kinetic energy of the fluid which can be fed from the fluid reservoir via the downpipe to the turbine into a rotational movement of an output shaft of the turbine, and with a generator which is intended to convert the rotational movement of the output shaft into electrical energy.
the energy conversion device has a pressure vessel, in particular designed differently from a housing of the turbine, in which a gas with an overpressure compared to the ambient air pressure, in particular of at least 0.2 bar, and the turbine are at least partially arranged.
An "energy conversion device” is preferably understood to mean a device that is intended to convert a potential energy (potential energy) of a fluid, preferably water, which is stored in a fluid reservoir, into electrical energy and/or thermal energy.
the energy conversion device is preferably designed as a heat pump device that is intended to convert a potential energy of a fluid stored in a fluid reservoir into thermal energy that is intended for controlling the temperature of a system, for example a heating system.
the energy conversion device is preferably intended for permanent operation.
the energy conversion device designed as a heat pump device is intended to convert a potential energy of the fluid into electrical energy and to use the electrical energy generated at the same time to recycle the fluid into the fluid reservoir, with the thermal energy generated thereby being intended for controlling the temperature of a system.
the energy conversion device is designed as an energy storage device that is intended to convert the potential energy of a fluid stored in a fluid reservoir into electrical energy that is intended to be fed into an electrical network.
the energy conversion device is preferably designed for two-part operation. In a first operating state, the energy conversion device designed as an energy storage device is designed to convert the potential energy of the fluid into electrical energy. In a second operating state, the energy conversion device designed as an energy storage device is designed to use electrical energy to convey the fluid back into the fluid reservoir, i.e. to convert electrical energy into potential energy of the fluid.
an energy conversion device that is designed as an energy storage device is designed to be operated in a permanent mode, with the fluid from the fluid reservoir flowing through the turbine into the pressure vessel and the fluid being simultaneously conveyed back from the pressure vessel into the fluid reservoir via the return path.
the compression of the conveying gas designed as ambient air would "draw" energy from the environment, which is used to convey the fluid back into the fluid reservoir.
the fluid can be conveyed back using a particularly advantageously small amount of electrical energy, i.e. in an energy-efficient manner.
a "fluid reservoir” is preferably understood to mean a reservoir for a fluid that is intended to drive the turbine.
the fluid reservoir is designed as a reservoir that can hold a volume of a fluid.
the fluid reservoir can be designed as an open fluid reservoir or as a closed fluid reservoir.
the fluid reservoir designed as a closed fluid reservoir can be designed as a tank.
a fluid reservoir designed as a tank preferably has a capacity of at least 0.005 m 3 .
fluid reservoirs designed as tanks are also conceivable, which have a capacity of 0.1 m 3 , preferably 1 m 3 or more than 1.5 m 3 .
the fluid reservoir designed as an open fluid reservoir can be designed as a lake, for example a reservoir, in particular a mountain lake, which has a significantly larger capacity.
the energy conversion device has only one fluid reservoir. In principle, however, it would also be conceivable for the energy conversion device to have several fluid reservoirs, which are preferably coupled to one another.
the "fluid" for driving the turbine is designed as a liquid, preferably as an incompressible liquid.
the fluid for driving the turbine is designed as water.
the fluid for driving the turbine it would also be conceivable for the fluid for driving the turbine to be designed as another liquid, for example as a coolant. It would also be conceivable for the fluid to be designed as a coolant. It is equally conceivable for the fluid to be designed as an antifreeze or to be provided with an antifreeze.
the fluid reservoir is located above the turbine.
the fluid reservoir has a geodetic height compared to the turbine.
the fluid reservoir is designed to store a fluid is provided which is fed to the turbine for energy conversion.
the fluid reservoir can be of different sizes depending on the size of the energy conversion device.
the fluid reservoir can be designed as a fluid tank which is attached, for example, to a building or another structure.
a fluid reservoir designed as a fluid tank can, for example, have a capacity of 0.005 cubic meters to 2000 cubic meters.
the fluid reservoir can advantageously be designed as a reservoir.
the fluid reservoir is preferably designed as a large water reservoir, such as in particular a reservoir.
the fluid reservoir is preferably designed as a fluid tank.
the fluid reservoir can have different geodetic heights relative to the turbine for different designs of the energy conversion device.
the fluid reservoir preferably has a geodetic height of at least 5 m relative to the turbine.
the fluid reservoir preferably has a height of at least 5 m relative to the turbine.
a geodetic height at which the fluid reservoir is arranged relative to the turbine is, when designed as a heat pump device, a value of 7 m to 800 m, preferably 10 m to 600 m, and in a particularly advantageous design, 80 m to 200 m.
the fluid reservoir preferably has a height of at least 5 m relative to the turbine.
a geodetic height at which the fluid reservoir is arranged opposite the turbine is, in a design as an energy storage device, at a value of 10 m to 2000 m, preferably from 50 m to 1500 m and in a particularly advantageous design from 100 m to 1000 m.
a “downpipe” is preferably understood to mean a pipe through which a fluid can be supplied to a higher fluid reservoir of the turbine.
the downpipe can be formed from a single pipe or several individual pipes.
a diameter of the downpipe depends on a design of the energy conversion device and in particular depends on a size of a quantity of fluid to be supplied to the turbine during operation.
the downpipe preferably has a diameter of 0.5 - 5000 cm, particularly preferably 1 - 1000 cm and particularly advantageously 2 - 20 cm.
the downpipe is preferably designed as a single pipe.
the downpipe preferably has a diameter of 0.1 - 15 m, particularly preferably 1 - 10 m and particularly advantageously 2 - 5 m.
the diameter is dimensioned accordingly according to the flow requirement of the fluid to be pumped, so that in particular the friction losses between the fluid and the pipe are as low as possible.
a “turbine” is understood to mean a turbomachine that converts the kinetic energy of a flowing fluid into mechanical rotational energy that is output via an output shaft of the turbine.
the turbine preferably has several blade wheels that are arranged in at least one fluid stream of the fluid and that absorb the kinetic energy of the fluid by flowing around the fluid and convert it into rotational energy.
the turbine it would be conceivable for the turbine to be acted upon by a fluid stream from only one nozzle for propulsion.
the turbine has several nozzles that direct several fluid streams onto the turbine, in particular turbine wheels of the turbine.
the turbine is designed as a Pelton turbine.
the turbine it would also be conceivable for the turbine to be designed as a Kaplan turbine, a Francis turbine, or another turbine that appears appropriate to the person skilled in the art.
a “generator” is preferably understood to mean an electrical machine that is intended to convert kinetic energy, in particular rotational energy, into electrical energy.
the generator can be designed, for example, as an alternating current generator or as a direct current generator.
a "pressure vessel” is preferably understood to mean a sealable vessel in which the pressure can be maintained.
the pressure vessel is preferably designed to be pressure-tight.
the pressure vessel preferably has only at least one fluid inlet opening, through which a fluid can flow into the pressure vessel via the downpipe at an inlet pressure, and at least one fluid outlet opening through which a fluid can be led out of the pressure vessel.
the fluid inlet opening is preferably arranged below a maximum fluid filling level of the pressure vessel.
a fluid inlet opening above the fluid filling level is also conceivable.
the fluid outlet opening is arranged below a minimum fluid filling level in the pressure vessel.
all openings in the pressure vessel i.e.
all openings for fluid lines or power lines are arranged below the minimum fluid filling level.
all fluid inlet openings, fluid outlet openings and openings through which, for example, power cables are led into the pressure vessel are arranged below the minimum fluid filling level.
the pressure vessel can thereby advantageously be sealed against the escaping of the pressurized gas.
the pressure vessel is designed to maintain a pressure of 0.2 bar to 200 bar.
a "gas” is preferably understood to mean a pure gas or a gas mixture.
the gas or gas mixture preferably has a lower density than ambient air.
the gas or gas mixture is preferably not designed as ambient air.
An "overpressure in the pressure vessel” is to be understood as a pressure in the pressure vessel that is higher than the ambient pressure prevailing immediately outside the pressure vessel.
the overpressure in the pressure vessel is preferably in a range of 0.2 bar to 200 bar compared to the ambient pressure prevailing immediately outside the pressure vessel.
the overpressure in the pressure vessel is particularly dependent on a geodetic height at which the fluid reservoir is arranged above the pressure vessel.
the pressure vessel is constantly under the overpressure.
the pressure vessel is under the overpressure when the energy conversion device is ready for operation.
the pressure vessel is under excess pressure during operation of the turbine arranged in the pressure vessel. In particular, the excess pressure in the pressure vessel prevails not only during a specific operating state of the energy conversion device, for example a switched-off state of the energy conversion device, but in particular continuously during an operational state.
the turbine is at least partially arranged in the pressure vessel should preferably be understood to mean that preferably a main part, particularly preferably the entire turbine, is completely arranged in the pressure vessel, but in an alternative embodiment it is also conceivable that only a part of the turbine, for example only a turbine outlet, is arranged in the pressure vessel and a remaining part of the turbine is connected to the pressure vessel and/or is integrated into a downpipe.
the turbine is operated in the pressure vessel under excess pressure.
"Provided” should in particular be understood to mean specially designed and/or equipped.
the fact that an object is intended for a specific function should in particular be understood to mean that the object fulfills and/or carries out this specific function in at least one application and/or operating state.
the fluid in the pressure vessel is advantageously pressurized and pressed out of the pressure vessel through a fluid outlet, whereby the fluid is pressed in a return path in the direction of the fluid reservoir. This can advantageously improve the efficiency of returning the fluid to the fluid reservoir.
the gas has a density of less than 1.2 kg/m 3 , in particular that it is in the form of helium.
density of a gas is preferably understood to mean a density of the gas measured under laboratory conditions.
a gas with a density of less than 1.2 kg/m 3 is preferably in the form of helium.
the gas is in the form of hydrogen, illuminating gas, methane, ammonia.
the gas consists of a gas mixture of different gases. This makes it possible to provide an advantageously high overpressure in the pressure vessel, whereby a Frictional resistance for a turbine arranged in the pressure vessel is advantageously small. By using a corresponding gas, the friction of the turbine in the pressure vessel under excess pressure can be advantageously reduced and thus the efficiency of the energy conversion device can be advantageously increased.
the turbine be designed as a Pelton turbine.
a "Pelton turbine” is preferably understood to mean a free-jet turbine that has at least one turbine wheel with several turbine blades, which is driven by a fluid jet flowing out of at least one nozzle. This allows the turbine to be designed particularly advantageously with a high degree of efficiency.
the energy conversion device has a return path via which the fluid can be conveyed from the pressure vessel back into the fluid reservoir, and has a compressor and/or mixing unit which is intended to mix the fluid to be returned in the return path with a compressed conveying gas.
a "return path" should preferably be understood to mean a part of the energy conversion device which is intended to convey a fluid, in particular that which was used to drive the turbine, from the pressure vessel back into the fluid reservoir.
the return path is preferably free of a fluid pump device, for example a water pump, which pumps the fluid directly back into the fluid reservoir.
the return path is preferably at least partially formed from a heat-conducting material, for example copper.
the return path is preferably formed largely from a heat-conducting material.
a “compressor and/or mixing unit” is preferably understood to mean a unit that has at least one compressor unit or one mixing unit, but preferably comprises both a compressor unit and a mixing unit.
a “compressor unit” is preferably understood to mean a unit that is intended for compressing and conveying a gas, in particular a conveying gas.
the compressor unit is preferably designed as a compressor.
the compressor unit is preferably designed to compress a conveying gas to a pressure of 0.1 bar to 250 bar. Depending on a delivery head over which the fluid to be conveyed must be conveyed, the compressor unit is designed to convey the conveying gas to a different pressure.
the compressor unit can preferably be driven by means of an electric motor.
the compressor unit in principle, it would also be conceivable for the compressor unit to be driven in a different way. For example, it would be conceivable for the compressor unit to be driven by a rotational movement generated by the turbine. A direct drive of a drive shaft of the compressor by the output shaft of the turbine would be conceivable. In principle, it would also be conceivable for the drive shaft of the compressor to be driven indirectly by a gear, for example by a planetary gear. It would also be conceivable for the compressor unit to be arranged in the pressure vessel.
the conveying gas is preferably in the form of air, in particular as ambient air. It would also be conceivable for the conveying gas to be in the form of a gas or gas mixture.
a “mixing unit” is preferably understood to mean a unit that is intended to mix two fluids, in particular the fluid to be returned in the form of a liquid, and a conveying gas.
the mixing unit is intended to set a ratio of two volume flows, in particular the volume flow of the fluid to be returned and the volume flow of the conveying gas.
the mixing unit is intended to mix the fluid to be returned in the form of a liquid and the conveying gas in such a way that a defined amount of fluid to be conveyed and a defined amount of conveying gas emerge alternately at at least one outlet of the mixing unit.
the mixing unit is intended to mix the volume flows of the fluid to be returned and the conveying gas in such a way that separate volumes of the fluid to be returned and the conveying gas are each output alternately at an outlet.
the fluid to be returned in the form of a liquid and the conveying gas are not miscible in the sense that they form a single fluid.
the mixing unit is not intended to to form a homogeneous fluid or emulsion from the fluid to be returned and the conveying gas.
the mixing unit preferably has at least one mixing valve for mixing the fluid to be returned with the conveying gas. In principle, it is also conceivable for the mixing unit to have several mixing valves connected in parallel for mixing the fluid to be returned with the conveying gas.
a mixing valve of the mixing unit can preferably be designed as a simple 3/2-way valve, as a rotary valve, as a rotation valve, or as another valve that appears appropriate to the person skilled in the art, which has at least one inlet for the fluid to be conveyed, at least one inlet for the conveying gas, and at least one outlet for the mixture of the fluid to be conveyed and the conveying gas.
the mixing valve is intended to alternately output a defined volume of fluid to be returned and a defined volume of conveying gas from its outlet. This allows the fluid to be conveyed to be conveyed particularly easily and efficiently by the conveying gas along the conveying path to the higher fluid reservoir.
the conveying gas rises in the return section, it expands due to the decreasing pressure.
the fluid to be conveyed is advantageously conveyed more easily.
the conveying gas cools down and absorbs thermal energy from the environment, in particular from the outside through the return section.
energy, in particular thermal energy is extracted from the conveying gas as it cools down due to the volume work.
the energy extracted from the environment is therefore used to convey the fluid back and is then converted into potential energy, then into mechanical energy, and then into electrical energy by the turbine.
the energy conversion device can therefore preferably extract energy, in particular thermal energy, from the environment and at least partially convert it into electrical energy.
a return path has a compressor and/or mixing unit which has a mixing valve which is provided for mixing the fluid to be returned with the compressed conveying gas.
the fact that the mixing valve is provided for mixing the fluid to be returned, which is in the form of a liquid, preferably water, with the conveying gas is to be understood as that a defined volume of fluid to be returned and a defined volume of conveying gas flow alternately in a line downstream of the mixing valve.
the downstream line preferably has such a small diameter that the conveying gas cannot flow past the upwardly leading line.
the pressurized conveying gas is intended to convey the fluid to be conveyed, which is in the form of a liquid, upwards in the line downstream of the mixing valve using its buoyancy force.
the pressurized conveying gas is intended to fill as much of the line diameter as possible and to act according to the principle of so-called plug flow, piston flow or umbrella bubble flow.
the pressurized conveying gas is intended to expand as it rises in the upwardly directed line due to the falling pressure and thereby accelerate the conveyance of the fluid in the form of a liquid.
the return section can therefore be designed particularly advantageously for returning the fluid to be returned.
a return line has a compressor and/or mixing unit that has a mixing valve that is intended to mix the fluid to be returned and a compressed conveying gas in a mixing ratio that is in a range from 30:1 to 1:30.
the mixing valve is particularly preferably intended to mix the fluid to be returned and the compressed conveying gas in a mixing ratio in a range from 20:1 to 1:20, preferably in a range from 10:1 to 1:10 and particularly preferably in a range from 5:1 to 1:5.
the mixing valve is intended to mix the fluid to be returned and the compressed conveying gas in a mixing ratio of 1:1. This allows the fluid to be conveyed by means of the conveying gas to be particularly advantageous.
the energy conversion device has a compressor and/or mixing unit which has a mixing valve whose mixing ratio is variably adjustable.
the fact that the mixing ratio is "variably adjustable” should preferably be understood to mean that the mixing ratio of the mixing valve can be changed by an adjustment mechanism, preferably during operation, within a defined range.
the mixing ratio is preferably adjustable in a range from 30:1 to 1:30.
the adjustment mechanism can preferably be operated manually by a
the system can be set either manually or automatically. This allows the fluid to be returned in a particularly advantageous manner and adapted to external environmental influences.
a return path has several individual lines that are connected downstream of a mixing valve and are fed by it.
the several individual lines of the return path that are connected downstream of the mixing valve are all connected in parallel to one another.
the individual lines of the return path are at least partially, preferably largely and particularly preferably completely made of an advantageously heat-conducting material, such as in particular copper or a material with a comparable thermal conductivity.
the return path has a different number of individual lines depending on the amount of fluid to be conveyed per minute, the number of which is determined when designing the energy conversion device.
the return path preferably has at least 10 individual lines, preferably at least 50 individual lines and particularly preferably more than 100 individual lines.
the return path it would also be conceivable for the return path to have several mixing valves, with a bundle of parallel-connected individual lines each being connected downstream of a mixing valve. At least 10 individual lines are preferably connected downstream of a mixing valve. A maximum of 100 individual lines are preferably connected downstream of a single mixing valve. This preferably makes it possible to provide a return path in which a mixture of the fluid to be returned, which is in the form of a liquid, and the conveying gas can be conveyed particularly advantageously and in large volumes.
each individual line would be conceivable for individual lines to split into several individual lines along their course, preferably in an upper third.
each individual line would be conceivable for each individual line to split into two or three further individual lines in an upper third.
each of the split individual lines it would be conceivable for each of the split individual lines to split into one or two further individual lines in an upper quarter of the return path.
the individual lines can have the same inner diameter as the other individual lines.
the multiple individual lines each have an inner diameter that is smaller than 100 mm.
the inner diameter of the individual lines determines a flow cross-section that allows a fluid flowing through the individual lines, in particular the fluid from the fluid to be returned and the conveying gas is available for flow.
An inner diameter is preferably less than 80 mm, more preferably less than 50 mm and in advantageous embodiments less than 20 mm.
an inner diameter of the individual lines is selected depending on a quantity of fluid to be conveyed per minute, a conveying head and a pressure in the pressure vessel.
the inner diameter of the individual lines is preferably 6 mm, for example.
the individual lines can therefore be advantageously designed so that a conveying gas and a fluid to be conveyed in the form of a liquid can flow separately and the conveying gas cannot flow past the fluid to be conveyed in the form of a liquid.
the electrical generator driven by the turbine is arranged inside the pressure vessel.
This allows the pressure vessel to be designed to be pressure-tight in an advantageously simple and cost-effective manner, since no moving parts, such as in particular a rotating shaft, have to be led out of the pressure vessel and sealed with complex seals.
the generator has electrical lines that are led out of the pressure vessel below a minimum fluid filling level.
a "minimum fluid filling level” should preferably be understood as a level to which the fluid to be returned in the pressure vessel is at least during proper operation. This makes it advantageously easy to seal an outlet point from which the electrical lines are led out of the pressure vessel and thus advantageously easy to seal the pressure vessel.
the return line has a compressor and/or mixing unit which has a compressor which is provided for compressing a compressed conveying gas and is connected upstream of a mixing valve.
a conveying gas provided for conveying the fluid to be returned can advantageously be pressurized for conveying before it is mixed with the fluid.
the return path has a heat exchanger which is arranged between a compressor unit and a mixing valve and is intended to extract thermal energy from a compressed conveying gas.
a "heat exchanger” should preferably be understood as a device is intended to transfer thermal energy from at least a first volume flow to at least a second volume flow.
the heat exchanger is intended to extract thermal energy from a first volume flow, in particular the compressed conveying gas, and to transfer this thermal energy to a further volume flow, preferably water, for storage or further transfer.
the heat exchanger is designed as a separate component downstream of the compressor unit. In principle, it would also be conceivable for the heat exchanger to be at least partially integrated into the compressor unit. It would be conceivable for the compressor unit to form an integrated heat exchanger. As a result, heat generated during compression of the conveying gas can be advantageously extracted from the conveying gas and used.
the return path has a heat exchanger which is arranged in an upper third of the return path and which, in at least one operating state, is intended to supply thermal energy to the flowing conveying gas.
An "upper region” is to be understood as a region facing the fluid reservoir.
the upper region is preferably formed by an upper third, preferably an upper quarter, particularly advantageously an upper fifth of the return path, which faces the fluid reservoir.
thermal energy is supplied to the conveying gas which has expanded in the return path and is thereby cooled via the heat exchanger so that the conveying gas can continue to expand.
thermal energy is only supplied to the conveying gas via the heat exchanger in the upper region of the return path, in particular, if thermal energy absorbed from the environment of the return path is not sufficient for the conveying fluid to expand sufficiently to convey the fluid to be conveyed.
the heat exchanger in the upper third of the return path can be supplied with the thermal energy that was extracted from the fluid flow by the heat exchanger immediately downstream of the compressor.
a method for operating an energy conversion device wherein in one method step a fluid from a pressure vessel is pumped through a pressure prevailing in the pressure vessel and is conveyed back into the fluid reservoir by mixing it with a pressurized conveying gas. This allows the fluid in liquid form to be conveyed back into the fluid reservoir particularly efficiently.
thermal energy generated during compression of a conveying gas is extracted from the compressed conveying gas for further use. This allows heat generated during compression of the conveying gas to be used advantageously.
the Figures 1 and 2 show a schematic representation of an energy conversion device 10a according to the invention.
the Figures 1 and 2 show an energy conversion device 10a according to the invention in a first embodiment.
the energy conversion device 10a is designed as a fluid power plant device.
the energy conversion device 10a is designed as a heat pump device.
the energy conversion device 10a designed as a heat pump device is intended to provide thermal energy.
the thermal energy provided by the energy conversion device 10a is preferably intended to be supplied to a further device, for example a heating circuit.
the energy conversion device 10a is attached to a building 12a, for example.
the building 12a here has a height of 140 meters, for example. In principle, it is also conceivable that the building 12a has a different height.
the energy conversion device 10a has a fluid reservoir 14a for storing a fluid 100a.
the fluid 100a is provided for operating the energy conversion device 10a.
the fluid 100a is preferably designed to be approximately incompressible.
the fluid 100a is designed as a liquid.
the fluid 100a is designed as water.
the fluid 100a designed as a liquid is designed as a cold protection agent or as water mixed with a cold protection agent.
the fluid reservoir 14a is designed as a tank.
the fluid reservoir 14a designed as a tank is arranged on a roof of the building 12a.
the fluid reservoir 14a designed as a tank is preferably arranged at least at a reservoir height of 145 m in the building.
the fluid reservoir 14a has a capacity of 0.2 m 3 . In principle, it would be conceivable for the fluid reservoir to have a capacity of 0.1 m 3 to 1 m 3 .
the fluid reservoir 14a has a fluid outlet 16a.
the fluid 100a designed as a liquid can exit the fluid reservoir 14a through the fluid outlet 16a.
the fluid reservoir 14a has a fluid inlet 18a.
the fluid 100a designed as a liquid can be pumped back into the fluid reservoir 14a through the fluid inlet 18a.
the energy conversion device 10a has a downpipe 20a.
the downpipe 20a is connected to the fluid reservoir 14a.
the downpipe 20a is connected to the fluid outlet 18a of the fluid reservoir 14a.
the fluid 100a can flow out of the fluid reservoir 14a via the downpipe 20a.
the downpipe 20a runs in the vertical direction.
the downpipe 20a does not necessarily have to run parallel to the vertical direction.
the downpipe 20a leads from the reservoir height to an area located below in the vertical direction.
the fluid 100a which is in the form of a liquid, flows through the downpipe 20a purely due to the acceleration of gravity, i.e. in particular the force of gravity.
the downpipe 20a is preferably designed as a single line.
the downpipe 20a is preferably formed from a pressure-resistant pipe. However, the downpipe 20a can also have several individual lines. In principle, it would also be conceivable for the energy conversion device 10a to have further downpipes 20a that lead away from the fluid reservoir
the energy conversion device 10a has a fluid valve 94a that is arranged in the downpipe 20a.
the fluid valve 94a is preferably arranged at an upper end region of the downpipe 20a facing the fluid reservoir 14a.
the fluid valve 94a is provided for controlling a volume flow of fluid 100a that flows out of the fluid reservoir 14a through the downpipe 20a.
the fluid valve 94a is provided for closing and opening the downpipe 20a.
the fluid valve 94a has a closed state in which the fluid valve 94a closes the downpipe 20a.
the fluid valve 94a has an open state in which the fluid valve 94a releases a flow cross section of the downpipe 20a and a fluid 100a can flow from the fluid reservoir 14a via the downpipe 20a.
the fluid valve 94a is continuously adjustable. A flow rate of the fluid valve 94a can be continuously adjusted between the closed position and the completely open position.
the energy conversion device 10a has a turbine 22a.
the turbine 22a is connected downstream of the downpipe 20a.
the turbine 22a is intended to convert a kinetic energy of the fluid 100a, which is fed from the fluid reservoir 12a via the downpipe 20a to the turbine 22a, into a rotational energy.
the turbine 22a is arranged vertically below the fluid reservoir 14a.
the turbine 22a is arranged in a basement of the building 12a.
the turbine 22a is 145 meters measured vertically arranged below the fluid reservoir 14a.
the vertical distance between the turbine 22a and the fluid reservoir 14a forms the geodetic height that the fluid 100a stored in the fluid reservoir 14a has relative to the turbine 22a.
the turbine 22a is designed as a free jet turbine.
the turbine 22a is preferably designed as a Pelton turbine.
the turbine 22a has a turbine wheel 24a with several blade wheels 26a.
the blade wheels 26a are preferably each formed by two approximately hemispherical half-blades that are separated from one another by a sharp edge.
the turbine 22a has an output shaft.
the output shaft is connected to the turbine wheel 24a and can be driven by it.
the turbine 22a has at least one nozzle 28a, which is intended to direct the fluid 100a in a jet onto the blade wheels 26a of the turbine 22a.
the nozzle 28a is aligned tangentially to a circumference of the turbine wheel 24a.
the nozzle 28a is intended to direct the fluid 100a, which flows from the downpipe 20a, at a high speed onto the blade wheels 26a of the turbine 22a, thereby driving the turbine wheel 24a.
the turbine 22a has several nozzles 28a aligned tangentially to the circumference of the turbine wheel 24a.
the turbine 22a it would also be conceivable for the turbine 22a to be designed as another turbine, for example as another free jet turbine.
the energy conversion device 10a has a pressure vessel 30a.
the pressure vessel 30a is different from a housing of the turbine 22a.
the pressure vessel 30a is intended to collect the fluid 100a after it has driven the turbine 22a.
the pressure vessel 30a forms a closed interior.
the pressure vessel 30a is preferably formed in two parts.
the pressure vessel 30a has a lower shell 32a and an upper shell 34a.
the lower shell 32a forms only a lower part of the pressure vessel 30a.
the lower shell 32a preferably extends only below a minimum fluid filling level 36a of the pressure vessel 30a.
a connection region in which the upper shell 34a is connected to the lower shell 32a is arranged below the minimum fluid filling level 36a.
the pressure vessel 30a is preferably formed from a metal, for example from a steel. In principle, it would also be conceivable that the pressure vessel 30a is made of a different material, such as a fiber-reinforced plastic.
the pressure vessel 30a has a capacity of 0.2 m 3. In principle, it would be conceivable that the Pressure vessel 30a has a capacity of 0.1 m 3 to 0.5 m 3 .
the exact size of the pressure vessel 30a is particularly dependent on a size of the entire energy conversion device 10a, in particular on a geodetic height of the fluid reservoir 14a relative to the turbine 22a and a volume of fluid 100a that is to be passed through per minute. For the exemplary embodiment, it would be conceivable, for example, that 450 liters per minute flow from the fluid reservoir 14a into the pressure vessel 30a and thereby drive the turbine 22a.
the pressure vessel 30a has a fluid inlet 38a.
the downpipe 20a is guided into the pressure vessel 30a through the fluid inlet 38a.
a fluid 100a can pass through the downpipe 20a into the pressure vessel 30a through the fluid inlet 38a.
the fluid inlet 38a is preferably arranged below a fluid filling level 36a, preferably below a minimum fluid filling level 36a.
the fluid 100a under pressure from the fluid reservoir 14a via the downpipe 20a can flow through the fluid inlet 38a into the pressure vessel 30a to the turbine 22a.
a nozzle 28a of the turbine 22a to be arranged directly at the fluid inlet 38a of the pressure vessel 30a and for the fluid inlet 38a to be arranged at a height of the turbine 22a.
the pressure vessel 30a has a fluid outlet 40a.
a fluid 100a collected in the pressure vessel 30a can be discharged from the pressure vessel 30a through the fluid outlet 40a.
the fluid outlet 40a is arranged in a bottom area of the pressure vessel 30a.
the fluid outlet 40a is arranged below the minimum fluid filling level 36a.
the fluid outlet 40a to be arranged in a bottom of the pressure vessel 30a.
the fluid 100a collected in the pressure vessel 30a is pressed out of the pressure vessel 30a through the fluid outlet 40a. All lines that lead into the pressure vessel 30a are arranged below the minimum fluid level.
the pressure vessel 30a is provided to be provided with an overpressure in an operating state.
the pressure vessel 30a is under an overpressure in an operating state.
the pressure vessel 30a is under an overpressure that is higher than the immediate ambient air pressure.
the pressure vessel 30a is under the overpressure that is higher than the immediate ambient air pressure.
Ambient air pressure increased overpressure.
the pressure vessel 30a is under the increased overpressure compared to the immediate ambient air pressure.
the overpressure in the pressure vessel 30a is 3 bar.
the overpressure that is maintained in the pressure vessel 30a is particularly dependent on a geodetic height at which the fluid reservoir 14a is arranged above the turbine 22a.
the overpressure in the pressure vessel 30a is intended to press the fluid 100a collecting in the pressure vessel 30a out of the pressure vessel 30a through the fluid outlet 16a.
the overpressure in the pressure vessel 30a is preferably 22% lower than a fluid pressure of the fluid 100a in the downpipe 20a at the level of the turbine 22a.
the fluid pressure of the fluid 100a in the downpipe 20a must be greater than the overpressure in the pressure vessel 30a, so that the fluid 100a can flow from the downpipe 20a through the nozzle 28a into the pressure vessel 30a, in particular onto the impellers 26a of the turbine 22a.
the overpressure can be between 0.2 bar and 100 bar above the ambient pressure.
a gas 102a is arranged in the pressure vessel 30a.
the gas 102a is designed as a compressed gas that is intended to generate a pressure in the pressure vessel 30a.
the gas 102a has a density of less than 1.2 kg/m 3 .
the gas 102a preferably has a density of about 0.1785 kg/m 3 .
the gas 102a is preferably designed as helium.
the gas 102a can be designed as pure helium or as a helium mixture. In principle, it would also be conceivable for the gas 102a to be designed as another gas or gas mixture that has a density of less than 1.2 kg/m 3 .
a frictional resistance within the pressure vessel 30a for moving parts, such as in particular for the turbine wheel 24a, can be advantageously kept low despite the increased pressure.
a gas 102a with a density of less than 1.2 kg/m 3 to generate the overpressure in the pressure vessel 30a a frictional resistance between the rotating turbine wheel 24a and its impellers 26a and the surrounding gas 102a can be kept low even at a high overpressure in the pressure vessel 30a.
the efficiency of the turbine 22a can be advantageously increased, in particular by reducing the flow resistance of the turbine wheel 24a, in particular also at increased pressure. Flow losses at the turbine 22a due to increased flow resistance as a result of the excess pressure in the pressure vessel 30a can thereby be advantageously minimized.
the energy conversion device 10a has a gas reservoir 42a.
the gas reservoir 42a is designed as a gas tank in which the gas 102a is stored.
the gas reservoir 42a is connected to the pressure vessel 30a via a supply line 44a.
a gas inlet 46a, via which the supply line 44a is led into the pressure vessel 30a, is arranged below the minimum fluid filling level 36a.
a valve (not shown in detail) that can be opened to change the pressure in the pressure vessel 30a in order to let a gas 102a into the pressure vessel 30a or to let it escape from it.
the valve In a closed state, the valve is sealed and no gas 102a can escape from the pressure vessel 30a via the supply line 44a.
the energy conversion device 10a it would also be conceivable for the energy conversion device 10a not to have a gas reservoir 42a that is permanently connected to the pressure vessel 30a, but rather for the pressure vessel 30a to be filled with the gas 102a only during assembly and for gas 102a to be refilled into the pressure vessel when the pressure falls below a required overpressure in the form of maintenance.
the energy conversion device 10a has a generator 48a.
the generator 48a is designed as an electrical generator.
the generator 48a is intended to convert a rotational movement of the output shaft of the turbine 22a into electrical energy.
the generator 48a is arranged in the pressure vessel 30a.
the generator 48a is preferably connected directly to the output shaft of the turbine 22a.
the generator 48a has electrical lines 50a through which an electrical current generated by the generator 48a can flow.
the electrical lines 50a of the generator 48a are led out of the pressure vessel 30a below the minimum fluid filling level 36a.
the energy conversion device 10a has a return path 52a.
the return path 52a is provided to return the energy collected in the pressure vessel 30a Fluid 100a back into the fluid reservoir 14a.
the return section 52a is intended to convey the fluid 100a over the geodetic height at which the fluid reservoir 14a is arranged above the pressure vessel 30a.
the return section 52a is designed free of a liquid pump.
the return section 52a does not have a pump that pumps the fluid 100a directly back into the fluid reservoir 14a.
the return section 52a is intended to convey the fluid 100a from the pressure vessel 30a into the fluid reservoir solely by means of the pressure in the pressure vessel 30a and a pressurized conveying gas 104a.
the return section 52a is intended, for example, to convey 450 liters per minute from the pressure vessel 30a back into the fluid reservoir 14a.
the return path 52a has a first line section 54a.
the first line section 54a is connected directly to the pressure vessel 30a.
the first line section 54a is connected to the fluid outlet 40a of the pressure vessel 30a.
the first line section 54a is preferably formed by a single line.
the first line section 54a is designed, for example, as a pipe or a hose.
the return path 52a has a compressor and mixing unit 56a.
the compressor and mixing unit 56a is intended to provide a compressed conveying gas 104a.
the conveying gas 104a is designed as ambient air.
the compressor and mixing unit 56a has a compressor 58a.
the compressor 58a is designed as a compressor.
the compressor 58a designed as a compressor is intended to suck in and compress ambient air.
the compressor 58a is intended to convert the ambient air into a compressed conveying gas 104a.
the compressor 58a is intended to compress the ambient air into a conveying gas 104a with a pressure of 3 bar.
the compressor 58a compresses the conveying gas 104a to a pressure of 3 bar.
the pressure to which the compressor 58a compresses the conveying gas 104a depends on a geodetic height over which the fluid 100a must be conveyed from the pressure vessel 30a into the fluid reservoir 14a. Depending on the geodetic height at which the fluid reservoir 14a is arranged above the pressure vessel 30a, the pressure to which the compressor 58a must bring the conveying gas 104a can be between 0.2 bar and 100 bar.
the compressor and mixing unit 56a has a conveying gas line 60a.
the conveying gas line 60a is connected to an outlet of the compressor 58a.
the conveying gas line 60a is intended to guide the pressurized conveying gas 104a away from the compressor 58a.
the compressor 58a is preferably electrically driven.
the compressor 58a is preferably driven by the current generated by the generator 48a of the turbine 22a.
the compressor 58a is supplied with an electrical current via the lines 50a of the generator 48a.
the compressor 58a to be driven by the rotational movement of the turbine 22a itself via a mechanical coupling.
the compressor and mixing unit 56a is designed to mix the fluid 100a to be returned with the compressed conveying gas 104a.
the compressor and mixing unit 56a has a mixing valve 62a.
the mixing valve 62a is designed to mix the fluid 100a to be returned with the compressed conveying gas 104a.
the mixing valve 62a is arranged between the first line section 54a of the return section 52a and the conveying gas line 60a.
the mixing valve 62a is designed as a 3/2-way valve.
the mixing valve 62a has a first fluid inlet 64a for the fluid 100a to be returned.
the first line section 54a is connected with its second end to the first fluid inlet 64a of the mixing valve 62a.
the mixing valve 62a has a second fluid inlet 66a.
the conveying gas 104a is fed into the mixing valve 62a via the second fluid inlet 66a.
the conveying gas line 60a of the compressor and mixing unit 56a is connected to the second fluid inlet 66a of the mixing valve 62a.
the compressor 58a is connected upstream of the mixing valve 62a.
the mixing valve 62a has a fluid outlet 68a.
the fluid outlet 68a is provided for the outflow of a mixture of the fluid 100a to be conveyed and the conveying gas 104a.
the fluid 100a mixed with the conveying gas 104a in the mixing valve 62a flows through the fluid outlet 68a.
a defined volume of fluid 100a and a defined volume of conveying gas 104a flow alternately through the fluid outlet 68a.
the mixing valve 62a is provided to mix the fluid 100a to be returned with the compressed conveying gas 104a.
the mixing valve 62a is provided to alternately fluidically connect the first fluid inlet 64a and the second fluid inlet 66a to the fluid outlet 68a.
the mixing valve 62a alternately supplies the fluid 100a from the first fluid inlet 64a to the fluid outlet 68a and the conveying fluid 104a from the second fluid inlet 66a to the fluid outlet 68a.
the mixing valve 62a has a first switching position in which the first fluid inlet 64a is fluidically connected to the fluid outlet 68a.
the mixing valve 62a has a second switching position in which the second fluid inlet 66a is fluidically coupled to the fluid outlet 68a.
the mixing valve 62a is provided to switch alternately back and forth between the first and second switching positions.
the mixing valve 62a it would also be conceivable for the mixing valve 62a to have a third switching position in which neither of the two fluid inlets 64a, 66a is coupled to the fluid outlet 68a and the mixing valve 62a is blocked.
the third switching position could be interposed between the first and second switching positions during operation.
the mixing valve 62a is provided to mix the fluid 100a to be returned and a compressed conveying gas 104a in a mixing ratio that is in a range from 30:1 to 1:30.
the mixing valve 62a is advantageously provided during operation to mix the fluid 100a to be returned and the compressed conveying gas 104a in a mixing ratio of 1:1.
the mixing valve 62a can preferably also be provided to mix the fluid 100a to be returned and the compressed conveying gas 104a in a different mixing ratio. For this purpose, in particular switching times of the first and second switching positions of the mixing valve 62a are varied.
the mixing valve 62a is preferably designed to be adjustable during operation.
the mixing valve 62a is preferably provided so that switching times for the first switching position and the second switching position can be adjusted, preferably in particular during operation.
the mixing valve 62a is provided so that the mixing ratio of the fluid 100a to be returned and the conveying gas 104a can be variably adjusted.
the mixing ratio can preferably be variably adjusted during operation in a range from 30:1 to 1:30. This is preferably achieved by varying switching times for the first and second switching positions of the mixing valve 62a.
a switching time for a switching position is designed in particular as a time in which the mixing valve 62a is in the corresponding switching position.
the return path 52a has a second line section 70a.
the second line section 70a is arranged between the mixing valve 62a and the fluid reservoir 14a.
the second line section 70a is arranged between the compressor and Mixing unit 56a and the fluid reservoir 14a.
the second line section 70a is provided for conveying the fluid 100a and the conveying gas 104a from the compressor and mixing unit 56a into the fluid reservoir 14a.
the mixture of fluid 100a to be conveyed and the conveying gas 104a flows from the compressor and mixing unit 56a into the fluid reservoir 14a via the second line section 70a.
the return section 52a has several individual lines 72a, 74a.
the individual lines 72a, 74a are connected downstream of the mixing valve 62a.
the individual lines 72a, 74a are fed by the mixing valve 62a.
the several individual lines 72a, 74a form the second line section 70a.
the return section 52a here has, for example, 84 individual lines 72a, 74a.
the return section 52a it would also be conceivable for the return section 52a to have a different number of individual lines 72a, 74a.
the number of individual lines 72a, 74a depends in particular on a volume of fluid 100a to be returned per minute in an operation. It is preferably conceivable for a number of individual lines 72a, 74a that the return section 52a has to be between 20 and 1000.
a number of individual lines 72a, 74a that is significantly larger would also be conceivable, for example 600 individual lines 72a, 74a.
Fourteen of the individual lines 72a, 74a are each combined to form a bundle and guided together in a pipe element 76a, 78a, 80a, 82a, 84a, 86a.
the fourteen individual lines 74a, 76a combined to form a bundle are each surrounded by one of the six pipe elements 76a, 78a, 80a, 82a, 84a, 86a shown as an example in this exemplary embodiment and are held together by this.
the individual lines 72a, 74a each have an inner diameter that is smaller than 100 mm.
the individual lines 72a, 74a preferably have an inner diameter of 6 mm.
the inner diameter of the individual lines 72a, 74a is preferably selected to be so small that a conveying gas 104a flowing in the individual lines 72a, 74a does not come into contact with the fluid 100a to be returned, which is in the form of a liquid and is flowing in front of it. can flow past.
the inner diameter of the individual lines 72a, 74a is selected such that a surface tension of the fluid 100a to be returned, which is designed as a liquid, prevents the conveying gas 104a in the individual lines 72a, 74a from flowing past the fluid 100a.
the return path 52a in particular the line sections 54a, 70a, are made of a thermally conductive material.
the return path 52a, in particular the line sections 54a, 70a, are preferably made of copper.
the individual lines 72a, 74a are made of a material that conducts heat well, in particular copper.
the return path 52a has a heat exchanger 88a.
the heat exchanger 88a is integrated into the compressor and mixing unit 56a.
the heat exchanger 88a forms part of the compressor and mixing unit 56a.
the heat exchanger 88a is arranged between the compressor 58a and the mixing valve 62a.
the heat exchanger 88a is intended to extract thermal energy from the compressed conveying gas 104a.
the conveying gas 104a compressed by the compressor 58a is heated by the compression in the compressor 58a.
the compressed conveying gas 104a heated by the compression flows through the conveying gas line 60a to the mixing valve 62a.
the heat exchanger 88a is arranged on the conveying gas line 60a.
the heat exchanger 88a is provided to extract thermal energy, in particular heat, from the conveying gas 104a flowing in the conveying gas line 60a.
the heat exchanger 88a has a heat transport medium.
the heat transport medium is provided to extract thermal energy from the compressed conveying gas 104a flowing in the conveying gas line 60a.
the heat transport medium is provided to supply the thermal energy to another system.
the heat exchanger 88a is provided to supply the thermal energy extracted from the conveying gas 104a to another system, in particular a heating system.
the heating system can be designed as a heating system 90a of the building 12a.
the heating system 90a can be provided, for example, to provide a hot water supply and/or the provision of heating energy for the building 12a.
the heating system 90a is preferably designed as a heating system for building 12a known from the prior art.
the return line 52a has a further heat exchanger 98a.
the heat exchanger 98a is integrated into the return line 52a.
the heat exchanger 98a is in an upper region of the return path 52a, which faces the fluid reservoir 14a.
the heat exchanger 98a is provided to supply thermal energy to the fluid mixture flowing through the return path 52a, in particular to the conveying fluid.
the heat exchanger 98a is preferably supplied with thermal energy from the first heat exchanger 88a.
the heat exchanger 98a is preferably only switched on in an operating state in which thermal energy that can be transferred from the environment to the conveying gas is no longer sufficient to heat the conveying gas 104a sufficiently so that it can expand to convey the fluid 100a to be conveyed.
the heat exchanger 98a can supply additional thermal energy to the conveying gas 104a, which is required for volume work, i.e. for expanding the conveying gas 104a and thus for conveying the fluid 100a to be conveyed.
the energy conversion device 10a has a control and regulating unit 92a.
the control and regulating unit 92a is provided for operating the energy conversion device 10a. A method for operating the energy conversion device 10a will be briefly described below.
the control and regulating unit 92a controls the energy conversion device 10a.
the control and regulating unit 92a uses the fluid valve 94a to regulate a flow of fluid 100a that is fed from the fluid reservoir 14a via the downpipe 20a to the turbine 22a.
the fluid 100a exits the nozzle 28a of the turbine 22a at the end of the downpipe 20a and hits the impellers 26a of the impeller 26a.
the fluid 100a in the area of the nozzle 28a has a high pressure and flows at a high speed onto the blade wheels 26a of the turbine wheel 24a.
the pressure of the fluid 100a at the nozzle 28a is greater than the pressure in the pressure vessel 30a, which is formed by the pressurized gas 102a arranged therein.
the jet of fluid 100a emerging from the nozzle 28a drives the turbine 22a and thus the generator 48a.
the generator 48a In the operating state, the generator 48a generates an electrical current through the rotation of the turbine 22a.
the electrical current can be fed to an energy storage unit or used directly to drive the compressor 58a.
the fluid 100a After driving the turbine 22a, the fluid 100a collects at a bottom of the pressure vessel 30a in which the turbine 22a is arranged. Due to the excess pressure in the pressure vessel 30a, the fluid 100a is pressed through the fluid outlet 40a into the first line section 54a.
the fluid 100a is pushed upwards in the return path 52a by the pressure of 3 bar in the interior of the pressure vessel 30a.
the compressor 58a is driven, preferably by means of the electrical current generated by the generator 48a of the turbine 22a.
the compressor 58a sucks in ambient air and compresses it to form a compressed conveying gas 104a.
the compressed conveying gas 104a is discharged via the conveying gas line 60a of the compressor and mixing unit 56a.
the heat exchanger 88a extracts thermal energy from the conveying gas 104a flowing in the conveying gas line 60a.
the thermal energy extracted by the heat exchanger 88a is fed to the heating system 90a.
the mixing valve 62a of the compressor and mixing unit 56a mixes the fluid 100a flowing from the first line section 54a and the pressurized conveying gas 104a flowing from the conveying gas line 60a.
the fluid 100a and the conveying gas 104a are mixed in a mixing ratio of 1:1 by the mixing valve 62a.
a defined volume of fluid 100a and an equal volume of conveying gas 104a flow alternately from the fluid outlet 68a of the mixing valve 62a.
the mixing ratio of the mixing valve 62a can be adjusted by means of the control and regulating unit 92a.
the mixture of pressurized fluid 100a and the pressurized conveying gas 104a flows into the second line section 70a into the individual lines 72a, 74a.
a volume of fluid 100a and a volume of conveying gas 104a flow alternately.
the fluid 100a flows with pockets of conveying gas 104a enclosed in between.
the fluid 100a and the conveying gas 104a flow in the return section 52a leading upwards in the direction of the fluid reservoir 14a in the individual lines 72a, 74a.
the pressure in the pressure vessel 30a acting on the fluid 100a to be returned pushes the fluid 100a to a defined height.
the conveying gas 104a which is enclosed between volumes of fluid 100a, pushes the fluid 100a upwards in the individual lines 72a, 74a of the second line section 70a due to its buoyancy.
the conveying fluid 104a cannot flow past the fluid 100a to be conveyed, which is in the form of a liquid, due to the narrow inner diameter of the individual lines 72a, 74a.
the conveying gas 104a expands as it rises in the individual lines 72a, 74a due to the decreasing pressure.
the incompressible fluid 100a to be conveyed does not expand.
the fluid 100a to be conveyed is compressed the further up in the Individual lines 72a, 74a of the second line section 70a are conveyed more quickly by the expansion of the conveying gas 104a.
the fluid 100a is conveyed back into the fluid reservoir 14a by the expanding and rising conveying gas 104a in the individual lines 72a, 74a. There, the fluid 100a is collected again and can be fed back to the turbine 22a via the downpipe 20a, whereby the process described above is repeated.
the conveying gas 104a flowing in the return section 52a relaxes due to the decreasing pressure as it rises in the direction of the fluid reservoir 14a.
the temperature of the conveying gas 104a drops further.
the individual lines 72a, 74a of the second line section 70a of the return section 52a can be used for cooling.
heat exchangers could be integrated into the second line section, which supply thermal energy to the conveying gas 104a flowing in the individual lines 72a, 74a and can thus, for example, supply an air conditioning system for the building 12a with cool air.
the conveying gas 104a in the return section 52a expands because the pressure on the individual conveying gas bubbles decreases towards the top and/or volume work is performed. As a result, the conveying gas 104a cools down. If the conveying gas 104a cools down below the temperature of the fluid 100a to be conveyed, heat is exchanged between the fluid 100a to be conveyed and the conveying gas 104a. Heat is also exchanged via the material of the individual lines 72a, 74a of the return section 52a if the conveying gas 104a and/or the fluid 100a to be conveyed is colder than the environment outside the return section 52a. Energy, in particular thermal energy, is therefore transferred. Thus, when volume work is performed, i.e.
the conveying gas 104a it would also be conceivable for the conveying gas 104a to be formed as a coolant instead of from ambient air.
the conveying gas 104a formed as a coolant evaporates, a particularly large amount of thermal energy could be transferred from the environment before or after the mixing valve 62a, since the conveying gas 104a formed as a coolant cools down considerably and thus a temperature gradient between the conveying gas 104a and the environment is very high. This would have a particularly positive effect on the volume work, i.e. on the expansion of the conveying gas 104a, and thus improve the conveying of the fluid 100a to be conveyed.
the pressure vessel 52a with the components arranged therein to be arranged not in a basement of a building 12a, but at the bottom of a shaft provided for the energy conversion device. It would be conceivable for a shaft to be provided that is installed underground. The shaft is preferably arranged directly underground beneath the building 12a, or next to the building 12a. The shaft is preferably more than 10 meters, preferably more than 50 meters deep. In principle, it would also be conceivable for the shaft to be more than 100m deep.
the compressor and mixing unit 56a is arranged together with the pressure vessel 52a at the bottom of the shaft.
the mixing valve 62a is arranged at the bottom of the shaft.
the compressor 58a is also preferably arranged together with the pressure vessel 52a at the bottom of the shaft. It would be advantageous if the pressure vessel 52a, the compressor and mixing unit 52a, i.e. the mixing valve 62a and/or the compressor 58a were designed as an assembly module that can be lowered into the shaft together.
the corresponding lines, i.e. the return line 52a, as well as the downpipe 20a and electrical lines 50a are routed in the shaft to the corresponding components, i.e. the pressure vessel 52a and the compressor and mixing unit 52a.
the Figures 3 and 4 show a second embodiment of the energy conversion device according to the invention.
the energy conversion device 10b is designed as a fluid power plant device.
the energy conversion device 10b is designed as an energy storage device.
the energy conversion device 10b designed as an energy storage device is intended to store energy in the form of potential energy of a fluid 100b in a fluid reservoir 14b and convert it into electrical energy when required.
the energy conversion device 10b is attached to a mount 96b, for example.
the energy conversion device 10b has the fluid reservoir 14b for storing the fluid 100b.
the fluid 100b is provided for operating the energy conversion device 10b.
the fluid 100b is preferably designed to be approximately incompressible.
the fluid 100b is designed as a liquid.
the fluid 100b is designed as water.
the fluid reservoir 14b is designed as a reservoir.
the fluid reservoir 14b designed as a reservoir is arranged on the mountain 96b.
the fluid reservoir 14b designed as a reservoir is preferably arranged on the mountain at a reservoir height of at least 2000 m.
the fluid reservoir 14b designed as a reservoir has, for example, a capacity of 10,000 m 3 .
the fluid reservoir 14b has a fluid inlet 18b.
the fluid 100b in the form of a liquid can be conveyed back into the fluid reservoir 14b through the fluid inlet 18b.
the energy conversion device 10b has a downpipe 20b.
the downpipe 20b is connected to the fluid reservoir 14b.
the downpipe 20b is connected to the fluid outlet 18b of the fluid reservoir 14b.
the fluid 100b can flow out of the fluid reservoir 14b via the downpipe 20b.
the energy conversion device 10b has a fluid valve 94b, which is arranged in the downpipe 20b.
the energy conversion device 10b has a turbine 22b.
the turbine 22b is connected downstream of the downpipe 20b.
the turbine 22b is intended to convert a kinetic energy of the fluid 100b, which is fed from the fluid reservoir 14b via the downpipe 20b to the turbine 22b, into a rotational energy.
the turbine 22b is arranged vertically below the fluid reservoir 14b.
the turbine 22b is arranged in a basement of the building 12b.
the turbine 22b is arranged 2000 meters below the fluid reservoir 14b, measured vertically.
the energy conversion device 10b has a pressure vessel 30b.
the pressure vessel 30b is different from a housing of the turbine 22b.
the pressure vessel 30b is intended to collect the fluid 100b after it has driven the turbine 22b.
the pressure vessel 30b forms a closed Interior.
the pressure vessel 30b has a capacity of 100 m 3. In principle, it would be conceivable for the pressure vessel 30b to have a capacity of 30 m 3 to 1000 m 3.
the exact size of the pressure vessel 30b is dependent in particular on a size of the entire energy conversion device 10b, in particular on a geodetic height of the fluid reservoir 14b relative to the turbine 22b and a volume of fluid 100b that is to be passed through per minute.
the pressure vessel 30b is intended to be provided with an overpressure in an operating state.
the pressure vessel 30b is under an overpressure in an operating state.
the pressure vessel 30b is under an overpressure that is higher than the immediate ambient air pressure.
the overpressure in the pressure vessel 30b is 40 bar.
the overpressure can be between 10 bar and 200 bar above the ambient pressure.
a gas 102b is arranged in the pressure vessel 30b.
the gas 102b has a density of less than 1.2 kg/m 3 .
the gas 102b preferably has a density of about 0.1785 kg/m 3 .
the gas 102b is preferably in the form of helium.
the energy conversion device 10b has a gas reservoir 42b.
the energy conversion device 10b has a generator 48b.
the generator 48b is designed as an electrical generator.
the generator 48b is intended to convert a rotational movement of the output shaft of the turbine 22b into electrical energy.
the generator 48b is arranged in the pressure vessel 30b.
the generator 48b has electrical lines 50b through which an electrical current generated by the generator 48b can flow.
the electrical lines 50b of the generator 48b are led out of the pressure vessel 30b below a minimum fluid filling level 36b.
the energy conversion device 10b has a return path 52b.
the return path 52b is provided to convey the fluid 100b collected in the pressure vessel 30b back into the fluid reservoir 14b.
the return path 52b is provided to convey the fluid 100b over the geodetic height at which the fluid reservoir 14b is arranged above the pressure vessel 30b.
the return path 52b is designed free of a liquid pump.
the return path 52b has a first line section 54b.
the first line section 54b is connected directly to the pressure vessel 30b.
the return path 52b has a compressor and mixing unit 56b.
the compressor and mixing unit 56b is intended to provide a compressed conveying gas 104b.
the conveying gas 104b is designed as ambient air.
the compressor and mixing unit 56b has a compressor 58b.
the compressor 58b is designed as a compressor.
the compressor 58b is intended to compress the ambient air to a conveying gas 104b with a pressure of 40 bar.
the compressor 58b compresses the conveying gas 104b to a pressure of 40 bar.
a conveying gas line 60b is connected to an outlet of the compressor 58b.
the conveying gas line 60b is intended to guide the pressurized conveying gas 104b away from the compressor 58b.
the compressor and mixing unit 56b is provided to mix the fluid 100b to be returned with the compressed conveying gas 104b.
the compressor and mixing unit 56b has a mixing valve 62b.
the mixing valve 62b is provided to mix the fluid 100b to be returned with the compressed conveying gas 104b.
the mixing valve 62b is arranged between the first line section 54b of the return section 52b and the conveying gas line 60b.
the mixing valve 62b is provided to mix the fluid 100b to be returned and a compressed conveying gas 104b in a mixing ratio that is in a range from 30:1 to 1:30.
the mixing valve 62b is provided in operation to mix the fluid 100b to be returned and the compressed conveying gas 104b in a mixing ratio of 1:1.
the return path 52b has a second line section 70b.
the second line section 70b is arranged between the mixing valve 62b and the fluid reservoir 14b.
the second line section 70b is arranged between the compressor and mixing unit 56b and the fluid reservoir 14b.
the return path 52b has several individual lines 72b, 74b.
the individual lines 72b, 74b are connected downstream of the mixing valve 62b.
the individual lines 72b, 74b are fed by the mixing valve 62b.
the return path 52b has 1000 individual lines. It is preferably conceivable that a number of individual lines 72b, 74b, which the return path 52b has, is between 600 and 100,000. In principle, depending on the size of the energy conversion device 10b, a number of individual lines that is significantly larger would also be conceivable, for example 1,000,000 individual lines 72b, 74b.
the individual lines 72b, 74b each have an inner diameter that is smaller than 100 mm.
the individual lines 72b, 74b have an inner diameter of 20 mm.
the energy conversion device 10b designed as an energy storage device has a control and regulating unit 92b.
the control and regulating unit 92b is intended to operate the energy conversion device 10b.
a method for operating the energy conversion device 10b will be briefly described below. In particular, the differences in the method compared to the first embodiment will be described. Essentially, operation of the energy conversion device 10b designed as an energy storage device is the same as for the first embodiment. The essential difference is that the potential energy of the fluid 100b is not to be converted into thermal energy, but into electrical energy. The electrical energy generated by the turbine 22b is intended to be fed into an energy network.
the energy conversion device 10b designed as an energy storage device is operated in a two-phase operation.
a first operating state electrical energy is generated by draining the fluid 100b from the fluid reservoir 14b into the pressure vessel 30b, in which the fluid 100b drives the turbine 22b. This electrical energy is fed into an electrical circuit.
a second operating state downstream of the first operating state, the fluid 100b is pumped back into the fluid reservoir 14b.
the compressor 58b is operated using electrical energy from a power grid and the fluid 100b is pumped back into the fluid reservoir 14b using the compressed conveying gas 104b.
a basic function is the same as in the first embodiment.

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Engine Equipment That Uses Special Cycles (AREA)

EP24183763.2A 2023-06-23 2024-06-21 Dispositif de conversion d'énergie Pending EP4481188A1 (fr)

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DE102023116632.8A DE102023116632A1 (de)	2023-06-23	2023-06-23	Energieumwandlungsvorrichtung

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EP0055054A2 (fr) *	1980-12-18	1982-06-30	Dale R. Bervig	Méthode et dispositif fluidique pour la production d'énergie
US20130043681A1 (en) *	2011-08-18	2013-02-21	Luis Manuel Rivera	Methods and systems forhydroelectric power generation

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JP2017096244A (ja) *	2015-11-26	2017-06-01	久知竹林	浮力発電機
DE202023100781U1 (de) *	2023-02-17	2023-03-06	Heizkraftwerk Altenstadt GmbH & Co. KG	Kleinspeicherkraftwerke zur Energiespeicherung

2023
- 2023-06-23 DE DE102023116632.8A patent/DE102023116632A1/de active Pending
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- 2024-06-21 EP EP24183763.2A patent/EP4481188A1/fr active Pending

Patent Citations (3)

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DE372326C (de) *	1922-04-22	1923-03-26	Adam Thierauf	Turbinenanlage
EP0055054A2 (fr) *	1980-12-18	1982-06-30	Dale R. Bervig	Méthode et dispositif fluidique pour la production d'énergie
US20130043681A1 (en) *	2011-08-18	2013-02-21	Luis Manuel Rivera	Methods and systems forhydroelectric power generation

Also Published As

Publication number	Publication date
DE102023116632A1 (de)	2024-12-24

Publication	Publication Date	Title
DE102010010701A1 (de)	2011-09-08	Energiespeichersystem
DE10160916A1 (de)	2003-07-03	Strömungsrohr und Wasserkraftwerk mit einem solchen Strömungsrohr
EP4481188A1 (fr)	2024-12-25	Dispositif de conversion d'énergie
DE10234568A1 (de)	2004-02-19	Verfahren zur konvektiven Energiegewinnung und Vorrichtungen zur Durchführung des Verfahrens
DE2917240A1 (de)	1980-09-04	Hydraulisches kuehlverfahren und vorrichtung zur durchfuehrung desselben
DE102017006100B4 (de)	2021-03-25	Pumpspeicherkraftwerk
DE10049372A1 (de)	2002-04-11	Anlage zur Übertragung und Umwandlung von Energie durch Wasserkraft
WO2021078929A1 (fr)	2021-04-29	Dispositif de production d'energie
DE822871C (de)	1951-11-29	Verfahren und Vorrichtung zur annaehernd isothermen Verdichtung von Luft oder Gas sowie zur annaehernd isothermen Entspannung derselben
DE202017003375U1 (de)	2017-08-10	Pumpspeicherkraftwerk
DE2402557A1 (de)	1975-07-24	Kraftmaschine
DE1189665B (de)	1965-03-25	Druckwasser-Kernreaktor
DE102010040765A1 (de)	2011-06-22	Einrichtung zur Bereitstellung von Heizwärme oder zur Erzeugung von Klimakälte und Einrichtung zur Bereitstellung von Elektroenergie, sowie Verfahren zur Bereitstellung von Heizenergie, Verfahren zur Erzeugung von Kälteenergie und Verfahren zur Erzeugung von Bewegungsenergie und/oder Elektroenergie
DE69928764T2 (de)	2006-08-31	Zyklon ejektions pumpe
DE2746746A1 (de)	1978-04-20	Versorgungseinrichtung fuer taucher
EP0001410B1 (fr)	1981-01-28	Système pour le stockage d'énergie thermique
DE2304783A1 (de)	1974-08-08	Waermekraftanlage
DE102009043356A1 (de)	2011-04-07	Drehstromgeneratorantrieb
AT527260A1 (de)	2024-12-15	Vorrichtung mit einer Wärmekraftmaschine und einer damit antreibbaren Pumpe
DE102016212777A1 (de)	2018-01-18	Passiv-aktiver Wärmeübertrager
DE3812928A1 (de)	1989-11-02	Energieerzeugungsvorrichtung (waermeschleuder 2 mit kreisprozess)
DE102015009975A1 (de)	2017-02-02	Hydrostirling-Maschine
DE102010044876B4 (de)	2022-10-13	Anlage zur Erzeugung elektrischer Energie aus Wasserkraft
DE102007012932A1 (de)	2008-09-18	Verfahren und Kraftwerk zur nachhaltigen Nutzung von Energie mittels eines Generators
DE413290C (de)	1925-05-08	Turbinenanlage mit einem Hauptregler ueblicher Bauart und einem hydraulischen Bremsregler

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