• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A compressed air storage power plant having a compressed air reservoir, with an electrical input / output circuit, with compression and expansion means having a piston pump which is switchable between a pumping operation and a generator operation, and with a solenoid having a core, the closed loop with two parallel straight core parts are wound around the coils, wherein between the straight core parts, a magnetically conductive bridge for amplifying the radially emerging from the core component of the induction is arranged.
    公开号:AT518150A1
    申请号:T50004/2016
    申请日:2016-01-05
    公开日:2017-07-15
    发明作者:Ing Dr Techn Alexander Schneider Dipl
    申请人:Ing Dr Techn Alexander Schneider Dipl；
    IPC主号:
    专利说明:

    The invention relates to a compressed air storage power plant with a compressed air reservoir, with an electrical input / output circuit, with compression and expansion means having a piston pump, which is switchable between a pumping operation and a generator operation, and with electromagnetic means having a core which is a closed loop with two parallel straight core parts forms around the coils are wound. Such a compressed air storage power plant is known from WO 2014/169312 Al.
    In order to stop climate change, renewable energy sources should receive a higher share in the energy mix. The problem is that the energy supply of sun and wind is not at the same time as the energy demand. Economic energy storage is not available in sufficient quantity. Therefore, calorific power plants and nuclear power plants are still in use to provide "control energy." There is therefore a need to increase the share of renewable energy and reduce the dependency on calorific and nuclear power plants as "control energy" or "balancing energy" ,
    It is known to store compressed air and heat for storing electrical energy. Earlier compressed air storage power plants use geologically suitable underground cavities; They are therefore limited in the choice of location, but also in terms of maximum working pressure. Advantageously, therefore, artificially manufactured compressed air storage, such as according to WO 2014/169312 Al, which allow a much higher working pressure. This makes the energy density higher, the construction more compact and the choice of location easier. Previously proposed compressed air storage power plants do not or only partially store the heat generated during compression, and therefore, in generator operation, they must absorb heat from outside, e.g. by burning gases, so that the generator does not freeze. The efficiencies of such prior compressed air storage power plants are therefore too low to play an important economic role in the "energy transition".
    EP 2 450 549 A2 describes a pressure stage heat storage power plant or energy storage method for temporary storage of energy in the form of pressure energy in a compressible medium and in the form of heat energy. This technique allows higher thermodynamic efficiency than previous methods, such as e.g. DE 2 636 417 A1, DE 2 541 501 A1, DD 118455 A1, DE 2 536 447 B2, DE 2 615 439 A1, DE 3 428 041 A1, EP 364 106 B1, US Pat. No. 4,630,436, US Pat. No. 4,523,432 and US Pat. No. 4,765,142 , This higher efficiency is to be achieved by a flexible arrangement of a plurality of compressors, a plurality of heat exchange devices and a plurality of expansion devices, which can be connected independently by numerous pipes independently. The advantage here is to prove the possibility that the number of compression devices can not be equal to the number of expansion devices. In contrast to a comparable arrangement with only one compression stage and one expansion stage, the efficiency is to be increased by the multi-stage arrangement with intermediate heat exchangers. The expansion and compression is assumed to be an adiabatic process, the multi-stage arrangement of heat exchangers and the possibility of feeding in surplus energy from outside should minimize temperature losses or energy losses. The disadvantage here is the higher complexity of the system, which increases the cost of construction and operation. The economy of such a system is u.a. dependent on the availability of excess (heat) energy. The system described in EP 2 489 840 A1 should be evaluated similarly, with an isothermal process being sought here. The heat energy is not stored but exchanged with the environment. The maximum accumulator pressure is 300 bar. If no external heat source is available during unloading, the efficiency is limited to 70%. This limits the choice of location and the stored energy density. In view of the considerable effort required to set up the plant in relation to the power and the amount of stored energy, the profitability is questionable.
    In order to save as far as possible all the heat generated during the compression and to fully utilize it again during expansion, a compressed air storage power plant has been proposed in WO 2014/169312 Al, which has a piston machine as its core, which works both as a pump and as a generator tet and the liquid piston has, which are driven inductively in the pumping operation, are also known from DE 19 728 199 Al, which discloses a compressor for refrigeration systems, in which a magnetic fluid is driven by an electromagnet or a permanent magnet. On the other hand, according to WO 2014/169312 A1, the pistons consist of an electrically and thermally highly conductive liquid, e.g. a gallium-indium-tin alloy, and the "cylinders" are communicating vessels containing the liquid Also, unlike the DE 19 728 199 Al, the magnetic flux is increased by a magnetic core, which in particular has the shape of a closed loop A current flow is induced in the liquid piston and the associated Lorentz force is used for driving, which allows higher power densities than in the piston engine according to DE 19 728 199 A1, which can not be used as a power plant.
    In US 2,258,415 A a compressor for refrigeration systems is described, which contains liquid piston, which are driven by induction. This compressor works with mercury as an electrically conductive liquid, which is however poisonous. The compressor has a U-shape, but the magnetic core according to the US 2,258,415 A is not parallel to the U-shape designed as a closed loop, but it is perpendicular to this. It is also disadvantageous that the current which must run perpendicular to the magnetic field in order to move the piston fluid is not induced by the primary magnetic field in the piston fluid but is generated externally via a secondary transformer coil and fed via lateral electrodes into the liquid piston , This has the disadvantage that the superposition of secondary injected current and primary induced current causes a phase shift between the magnetic field and the total current, which affects the operation of the machine. To minimize this interference, the poles of the magnet and the electrodes must be divided into several parallel segments. To effect a pendulum movement of the liquid piston in the U-shaped vessel, a complex circuit is necessary, which reverses the current flow through the coils of the two legs. Furthermore, the principle of US 2,258,415 A is suitable for use as a cooling unit, but not for storing energy.
    According to WO 2014/169312 A, compressed air in generator operation drives the pistons, the pistons overcoming the resistance of an excitation voltage and performing electrical work on the terminals of the coil winding in the manner of a magnetohydrodynamic (MHD) generator. A classic MHD generator has a low efficiency because a hot fluid or plasma flows through a channel, with much of the heat energy not being used. An improved form of the MHD generator is disclosed in US 3,517,229 A, which in some respects discloses the fluid power (turbo) equivalent to, for example, WO 2014/169312 A1. However, US 3,517,229 A gives no indication as to whether and how the heat generated during compression is temporarily stored and used in power generation. However, it is desirable to store the heat generated during the compression and to use it during the discharge, so that both processes proceed approximately isothermally:
    Due to the continuous circulation of the piston liquid, an advantageous heat exchange takes place between the displacement of the engine and the heat accumulator, which effectively dissipates the heat generated during the compression and prevents the icing of the generator during the expansion. This allows a high efficiency. Only a storage power plant with efficiencies of 90 percent or more is economically feasible on the electricity market under today's conditions.
    US 2008/072597 A1 discloses a piston pump with pistons of an electrically conductive liquid which emits electrical energy in a MHD generator. It is a Stirling process that contains no mechanical moving parts except the liquid piston. The process is simple and robust, it allows the conversion of heat into electrical energy. However, it remains unclear how electrical energy can be quickly stored with high power and quickly removed from storage with high performance. Therefore, this technique is not suitable for the construction of a storage power plant.
    WO 2008/139267 A1 discloses a system for storing electrical energy in the form of compressed air, wherein liquid pistons are used for compression / expansion. The Kolbenflüs fluid is not electrically conductive and is not driven inductively, but conventionally with a hydraulic pump, which in turn is connected to an electric motor / generator. In order to make the compression / expansion as isothermal, the piston liquid is pressed from above in many thin rays similar to a shower in the hydraulic cylinder. As a result, the compressed / expanding air is effectively cooled or heated. The disadvantage here appears to be the fact that the heat generated during compression is not stored, but is discharged by means of heat exchangers to the ambient air, to which also a fan is provided which consumes energy. As a result, the efficiency depends on the ambient temperature. In summer, the heat dissipation during compression is more complex, in winter, the heat input during expansion is more complex. Overall, the mechanical complexity and thus the construction costs appear high in relation to the power density of the system, on the one hand because the process must run slowly to be isothermal, and on the other hand, because the volume of the system must be large.
    The present invention now provides a compressed air storage power plant as described above, which is characterized in that between the straight core parts, a magnetically conductive bridge for amplifying the radially emerging from the core component of the induction is arranged. It is further advantageous if the bridge is formed of soft magnetic material, and / or if the bridge has an auxiliary winding.
    It is also beneficial if a gap is left between the bridge and the core. In this case, it is also expedient if there is a phase shift between the induction in the gap and the secondary current circulating around the core; and further, when the phase shift between the induction in the gap and the secondary current drives the piston to a pumping motion. It is also advantageous here if the piston is formed by a magnetizable piston fluid for enhancing the induction, and it is also advantageous if magnetic nanoparticles are contained in the piston fluid. In addition, it is advantageous if the piston is accelerated not only by induction, but also by a (compressed air) spring, because by the thus occurring introduction of reactive power and the active power is maximized.
    With the invention, i.a. Achieves the following advantages: 1. An increase in radial induction or piston force by inserting the bridge with or without additional winding (s) 2. Achieving an improved pumping motion through optimal phase shift between induction and secondary current. 3. An amplification of the radial induction or the piston force by a magnetizable piston fluid. 4. Optimization of pump performance through additional mechanical reactive power (increasing the kinetic energy of the piston and introducing a spring to store potential energy).
    Conveniently, all mechanically fixed parts except the coils, the core and a magnetic valve control are made of electrically non-conductive material, e.g. Ceramic, designed to minimize eddy current losses and re-magnetization losses; Similarly, the suspension of the machine, the frame, from such an electrically non-conductive material, in particular ceramic, be made.
    For the voltage delivery, an electrical capacitor may be provided, and this is preferably designed as a plate capacitor with comb-shaped interlocking plates, which by a suitable dielectric, e.g. Ceramic, glass or plastic, while keeping at a distance, that for the capacitor, a dielectric strength of 220 kV is achieved, wherein in conjunction with the coils a Resonanzfreguenz of e.g. 50 hertz is obtained.
    The present compressed air storage power plant is simple in construction, since the core is at the same time engine, compressor, expander and generator. It is also easy to operate, with no wear components except for the valves. Assuming that all processes run without loss, it is possible to bring the thermodynamic efficiency arbitrarily close to 100%, but at the expense of power consumption or output. The liquid piston with circulation of the piston fluid improves the heat transfer between the compressed air in the displacement and the surroundings of the displacement. Compression / expansion is not a purely adiabatic process but a polytropic process. By suitable fine tuning of the piston stroke as a function of the accumulator pressure (for example, by changing the total amount of piston fluid in the system or by supply / discharge of hydraulic fluid from / to the outside), the residence time of the compressed air in the displacement can be arbitrarily changed. Each differential volume element of the amount of air to be compressed / expanded can be compressed / expanded not once, but n times before it is released into the memory or into the environment. The higher the value for n is selected, i. the longer the gas lingers in the displacement, the more often it can exchange heat with fresh, circulated piston fluid. The greater the value chosen for n, the more the polytropic characteristic of an isotherm approaches. Isothermal compression and expansion is known to be equivalent to 100% efficiency. The higher the value for n, the lower the energy exchange between displacement and environment per piston stroke, the lower the "yield" of stored compressed air per piston stroke, the longer it takes for the accumulator to be charged / discharged Value for n, there is a high proportion of thermodynamic "reactive power", which oscillates in the system between the piston back and forth, or oscillates between maximum pressure energy in the gas (air) and maximum kinetic energy in the piston back and forth. The heat transfer / efficiency can also be improved by increasing the piston area in relation to the piston stroke. The present design allows fine tuning of some parameters to set the optimal operating point in terms of maximum economy. The optimal compromise between performance and efficiency is also determined by the prices on the power exchange. It is possible to adjust the optimal operating point each time the electricity price changes.
    The invention will be explained below with reference to the drawing and with reference to preferred embodiments, to which it should not be limited, however. In the drawing show:
    Fig. 1 is a schematic representation of a compressed air storage power plant of known type;
    Fig. 1A is an associated electrical equivalent circuit diagram;
    2 schematically shows the piston machine ("induction pump") of this compressed-air storage power plant with its peripheral components displacement controller and heat exchange circuit.
    Fig. 3 shows schematically this piston machine ("induction pump") enlarged and without peripheral components;
    4 shows a cross section through the soft magnetic core, the coil winding and the inner and the outer air gap of this piston machine, along the line IV-IV in Fig. 3.
    5 shows a cross section through the soft magnetic core, the displacement and the planetary gear that device of the reciprocating engine, which switches between pumping operation and generator operation, according to the line V-V in Fig. 3.
    FIG. 6 is an illustration similar to FIG. 3 of an improved reciprocating engine or induction pump; FIG.
    Fig. 7 is a view like Fig. 6, but illustrating the magnetic fluxes;
    FIG. 8 is a phasor diagram of currents or magnetic fluxes belonging to FIG. 7; FIG.
    FIG. 9 shows a three-phase variant in a representation similar to FIG. 7; FIG.
    Fig. 10 is an associated vector diagram of the electrical voltages.
    Fig. 11 is an associated phasor diagram of the magnetic fluxes;
    12 and 13 show the field line of the magnetic fluxes in a first quarter period, the Lorentz force acting from right to left (as shown in the drawing); FIGS. 14 and 15 show the field line course of the magnetic fluxes in the second quarter period, with the Lorentz force now acting more from left to right;
    16 and 17 show the field line course of the magnetic fluxes in the third quarter period, the Lorentz force again acting from right to left;
    FIGS. 18 and 19 show the field line course of the magnetic fluxes in the fourth quarter period, the Lorentz force again acting from left to right;
    20 and Fig. 21 are schematic representations of a compressed air storage power plant in different operating positions.
    In Fig. 1, an example of a known compressed air storage power plant 100 with a function of a compressor and expander piston pump 200 is shown schematically: A heat insulating layer 1 surrounds a (artificial) compressed air reservoir 2 and a heat-storing liquid 3, which, for. consists of water. The piston pump 200 is immersed in the liquid and surrounded on all sides by this.
    From an electrical point of view, there is an R-L-C parallel resonant circuit; see. Fig. 1A. At external terminals 4 as input and output circuit, a 220 kV AC voltage U is applied. The capacitance C is formed by a capacitor 5 disposed outside the heat-insulating layer 1. The capacitor 5 is designed as a layered plate capacitor with a dielectric strength significantly higher than 220 kV. The plates of the capacitor 5 are connected so that the poles of the capacitor 5 mesh in a comb-like manner and the dielectric fills a meandering space between the electrodes. The inductance L is formed by a coil-shaped winding 6 of the Kol benpumpe 200. The electrical resistance R is given by the mechanical work that is done in the compression of the air. The inductance L of the coil 6 and the capacitance C of the capacitor 5 are dimensioned so that the frequency corresponds to the frequency frequency of 50 hertz (or possibly 60 hertz, for example in the US, or any other chosen operating frequency).
    The compressed air storage power plant 100 thus operates without voltage conversion directly with 220kV AC voltage at the input / output 4, for which it is favorable if all parts, in particular the coil winding 6, are carefully double insulated and waterproof.
    The compressed air flows through a pressure pipe 7 between the piston pump 200 and the compressed air reservoir 2. In order to optimize the heat exchange, the pressure pipe 7 is designed meandering within the heat accumulator 3. A pipe 8 connects the piston pump 200 with the ambient air.
    In order to minimize the noise emission, the pipe 8 leading to the outside can be coated on the inside with a sound-damping material. In addition, the heat storage 3 and the thermal insulation 1 at the same time act as sound insulation.
    In Fig. 2, the known piston pump 200 together with its peripheral components is shown schematically. A pressure transducer 9 reduces the working pressure of the compressed air (pressure pipe 7) proportional to the pressure of a hydraulic fluid 10, which passes the pressure on two diaphragm springs 11. The diaphragm springs 11 divide a disc-shaped body 12 into an inner (middle) portion 13 and two outer portions 14 (right and left of the middle portion 13).
    Below two legs of the piston pump 200 are two small circulation pumps 15. These circulation pumps 15 drive a piston liquid to be described later through a heat exchanger circuit which continues the right and left legs of the piston pump 200 in a straight line down through the circulation pumps 15 leads and then branches into two lines: A branch leads from below through the outer Be rich 14 of the disc-shaped body 12 upwards. The other branch leads through a helical heat exchanger 16 upwards. Above the two bodies 12 and 16, the two lines or branches unite to form a line which at a lower vertex 17 of the piston pump 200 enters the center again in the latter.
    In Fig. 3, the piston pump 200 is shown enlarged without peripheral components: It has a soft magnetic core 18 in the form of a cut torus, in two parallel parts, namely cylinder parts 18A, 18B are inserted. The core 18 is constructed so that eddy current losses are minimal, e.g. in the form of parallel insulated mumetal wires or layered transformer sheets. The core 18 is also constructed so that the magnetic flux becomes maximum and the magnetic resistance becomes minimum, i. e.g. without joints or air gaps in the direction of the magnetic flux. The cylindrical parts 18A, 18B of the core 18 are wound with insulated wire to form the coils 6. Between the core 18 and the coils 6 is in each case an annular gap 19. The two coils 6 are connected by a U-shaped tube 20 which surrounds the magnetic core 18 concentrically. The air space 19 between the U-shaped connected coils 6 and the core 18 is divided by a partition wall 21 in an inner, closer to the core 18 gap 22 and an outer, located closer to the bobbin gap 23; see. also Fig. 4. These two columns 22 and 23 represent two concentric communicating vessels.
    Between the parallel parts 18A, 18B of the core 18 above the bobbin 6 is a switching device 24 with two servomotors 25, each driving a disc 27 via a respective planetary gear 26, see. also Fig. 5; each disc 27 carries in the center of a frusto-conical projection 28 and on the outside a thread which slides in an internal thread of the housing of the switching device 24.
    The gap 19 between the coils 6 and the core 18 (see Fig. 3) is filled with the thermally and electrically conductive liquid, e.g. Galinstan, filled. At rest, the liquid level in both legs of the communicating tubes (corresponding to the core parts 18A, 18B) is the same.
    One end of a coil 6 is connected to one end of the other coil 6 so that the two coils 6 together form a single winding around the magnetic core 18. The magnetic fluxes of the connected coils 6 through the core 18 always run in the same direction, either clockwise or counterclockwise. At the two terminals 4 (Figure 1) an AC voltage of 220 kV with a frequency of e.g. 50 hertz invested. This alternating voltage induces a magnetic field and an associated magnetic flux in the core 18 of the piston pump 200, the direction of which reverses at the same frequency (e.g., 50 times per second), alternately clockwise and counterclockwise.
    The change of the magnetic flux in the core 18 in turn induces an electrical alternating voltage running annularly around the core 18 and linked to the core 18 in the electrically conductive liquid located in the gap 19. The electrical current I 2 associated therewith in this liquid induces a magnetic field which is opposite to the magnetic field in the core 18. When the magnetic field in the core 18 is in the clockwise direction, the magnetic field generated by the electric current in the liquid runs counterclockwise and vice versa. An equal Lorentz force is applied to each differential volume element of the liquid, which is equal to the product of induced current I2 and the radial component of the induction. This causes a laminar flow in the communicating vessel without vortex, whereby the liquid rises in one leg, while it lowers in the other leg. This system thus acts as a piston pump or piston machine with a liquid piston.
    The resulting heat during compression is thereby dissipated or necessary heat during generator operation is supplied by the fact that the piston liquid is continuously circulated during operation and driven through the heat exchanger 16. The continuous circulation of the piston fluid in a circuit prevents the same molecules from being always at the boundary between the piston and the air. The revolution of
    Piston liquid is achieved in that the filled with electrically conductive liquid gap 19 is divided by the concentric partition wall 21 in the two concentric columns 22, 23, see. 3 and 4. These gaps 22, 23 are connected only at the upper end of the displacement 29 of both "pistons" so that the piston fluid can pass from the inner gap 22 into the outer gap 23 (and vice versa) Pumping operation heated (or cooled in the generator mode) piston volume is exchanged during each work period (eg 50 times per second) by the circulation pump 15. The small circulating pump 15 works by induction sucking the piston liquid from the outer gap 23 down, drives It continuously re-flows through the heat exchangers 12, 16 and then into the inner gap 22 from the lower vertex 17. The circulating pump 15, unlike the main pump, is designed so that the piston fluid flows in one direction only and not back and forth This requires a phase shift of 0 or 180 degrees between current and induction, and the resulting Lorentz force will always act in the same R In the flow direction along the x-axis of a Cartesian coordinate system, electrodes are to be arranged along the y-axis and the air gap of a magnetizable toroid along the z-axis.
    The compressed heated air is guided in the pressure pipe 7 through the heat accumulator 3, so that they can give off their heat. Conversely, the air flowing in from the compressed air accumulator 2 can absorb heat from the heat accumulator 3 before it relaxes and cools down in the displacement of the system which then functions as a generator.
    In order to keep the power consumption during pumping (charging) constant, the volume of the displacement is controlled in a conventional manner. At low working pressure (for example, 100 bar), the piston liquid level is low, the capacity is thus large. At high working pressure (for example, 1000 bar), the piston fluid level is high, the displacement is thus small. The regulation of the displacement volume is carried out by acting as a volume regulator body 12, which is separated in the interior by the two diaphragm springs 11 as mentioned in the middle (inner) region 13 and the two äuße ren region 14 (see Fig .. 2). The diaphragm springs 11 bulge out when the pressure rises in the central region 13. In this area 13 is the hydraulic fluid 10, the pressure of which is adjusted by means of the pressure transducer 9 proportional to the working pressure. In the outer regions 14 of the disc-shaped body 12 is the piston liquid, which is partially displaced from the regions 14 when the diaphragm springs 11 bulge and thereby reduce the volume in the region 14. If the working pressure increases, piston fluid is forced from the space 14 through the opening 17 into the gap 19, thereby reducing the displacement. The spring characteristic and the dimensions of the diaphragm springs 11 are preferably selected so that the displacement is regulated with the working pressure so that the absorbed power is constant in the pumping operation.
    The system can thus work as a pump or as a generator. In the pumping operation, electrical energy is expended to perform a compression work in the displacement above the liquid level. In this case, the trapped air in the displacement is compressed until the pressure is higher than the pressure in the compressed air reservoir 2. This opens a pressure valve above the piston fluid against the force of a spring, and the compressed air flows through the pressure pipe 7 into the compressed air reservoir 2. In pumping operation, the pressure difference alone is sufficient to open said pressure valve, whereby the pressure in the displacement overcomes the force of the spring, which closes the pressure valve again after the cycle. While air is being compressed in one "cylinder", fresh air is drawn in from the outside in the other cylinder, as the resulting negative pressure in the displacement of the other cylinder there opens the mammal valve against the force of the spring.
    In generator mode, an excitation voltage is applied to the terminals 4 from the outside. This excitation voltage can be provided by the network with which the subject compressed air storage power plant operates in a combined mode. In the event of a power failure, the excitation voltage can be generated by a stand-alone conventional system (e.g., diesel generator plus transformer).
    With regard to the general mode of operation of the system, reference may moreover be made to WO 2014/169312 A1 for the sake of simplicity.
    The reactive power remains in the system. It shuttles between capacitance and inductance. From the outside, only the equivalent resistance active power is supplied or delivered from the equivalent voltage source active power.
    In order to minimize the eddy current losses and the core loss losses, all the mechanically fixed parts except the coil windings 6 and 15 of the magnetic core 18 and the electromagnetic valve controller are made of electrically non-conductive material (e.g., ceramics). This also includes not shown in the drawing mechanical support or suspension of the machine. The suspension can alternatively be made of wood and brick masonry.
    The system described is a heat engine. The thermodynamic cycle has polytropic compression, isobaric compression, isochronous pressure change, and isobaric expansion.
    During the discharge of the compressed air reservoir 2 during generator operation, the working pressure in the compressed air reservoir 2 decreases continuously. In order to keep the power constant in generator operation, the working pressure - e.g. throttled down to a fixed value (e.g., 100 bar) by means of a throttle valve not shown in the drawing. The quadrangle that passes through the cyclic process in generator mode always has the same shape.
    By appropriate choice of design and / or operating parameters, the heat transfer between the displacement 29 and the environment can be varied so that the polytropic compression / expansion process more or less approximates an isothermal process and thereby the efficiency of the system more or less can be improved. A higher efficiency can i.a. with a lower performance / longer charge cycles or vice versa.
    6 now shows an improved variant of the induction pump 200 with extended straight sections. Below the electric coil 6, there is a bridge 64 between the two straight sections which, like the core 18, is made of a soft magnetic material (e.g., laminated transformer sheet). Like the coils 6, the bridge 64 also leaves a gap to the core 18 through which the piston fluid can flow. The bridge 64 forces a stray magnetic flux leaving the core 18 in the straight section in the radial direction, passes through the bridge 64 and penetrates in the opposite straight portion of the core 18 in the radial direction. Only this radial component, with the secondary current I2 (see Fig. 8) running tangentially around the core 18, causes a Lorentz force that is axial, i. parallel to the axis of the magnetic core 18, acts. Figs. 7 and 8 show the direction of the now three magnetic fluxes. The flux through the primary winding Φ1 is split into the flux Φ2 through the core 18 and the leakage flux Φ3 through the bridge 64. Fig. 8 shows the associated phasor diagram of the electrical currents and the magnetic fluxes, where Ii stands for the primary current and N for the winding number of the coil 6. The first and fourth Maxwell equation can be satisfied in this arrangement only if the vector diagram has the form shown qualitatively. There is one component of leakage flux Φ3 which is at right angles to the secondary current I2 pointer, i. which has a phase shift of 90 degrees to I2. The product of the two, the Lorentz force, therefore changes the sign in each quarter period, so it is twice positive and twice negative in each period. A sinusoidal voltage with the frequency f at the primary side therefore causes a periodic Lorentz force on the piston with the frequency 2f. The bridge 64 thus effects two things: 1. an increase of the radial induction and 2. the production of a 90 degree phase shift between (a component) of the induction and the secondary current, which causes a pumping movement.
    9 illustrates a three-phase variant. Here, the bridge 64 is vertically disposed and wrapped with an auxiliary winding 65 to amplify the magnetic flux Φ3 through the bridge 64. The three phases of the three-phase current are denoted by U1, U2 and U3 in FIGS. 9 and 10, the resulting magnetic fluxes in FIG. 11 and 12 to 15 with Φ1, Φ2 and Φ3. The phasor diagram of the electrical voltages is shown in FIG. The phasor diagram of the magnetic fluxes is shown in FIG. The main winding 6 consists of two identical bobbins, which are wound in the same direction and together form an inductance at which the voltage U1-U2 drops. In the middle between the two bobbins 6, the auxiliary winding 65 is connected. At this point is the zero point N of the three phases.
    At the free end of the auxiliary winding 65, the third phase U3 is connected. The voltage U1-U2 induces a magnetic flux Φ1-Φ2 as shown in Figs. 11 and 12, with a small portion of this flux (Φ1-Φ2) flowing through the bridge 64 and the greater part through the outer ring where it flows I2 induced. The voltage U3 induces a magnetic flux Φ3, as shown in FIGS. 11 and 13. The operation shown in Fig. 9 is further enhanced by the introduction of the auxiliary winding 65 and the use of three-phase current. Figs. 12 to 19 show the field lines of the magnetic fluxes for each quarter period. The 90 degree phase rotation between the main flow (Φ1-Φ2) and the tributary flow ((Φ1-Φ2) + Φ3) causes the sign of Lorentz force on the piston to reverse every quarter-period. A sinusoidal voltage with the frequency f at the primary side causes in this design a periodic Lorentz force on the piston with the frequency 2f.
    Further enhancement of the effect is possible if the piston fluid is made magnetizable, i. a relative permeability greater than 1 is generated, e.g. by adding magnetizable nanoparticles in the piston fluid ("ferrofluid").
    Further enhancement of the effect is achieved by the introduction of mechanical reactive power. The kinetic energy of the piston is Wkin = mv2 / 2. The change in kinetic energy over time is given by dWkin / dt = mv * dv / dt = v * F. The change in the kinetic energy of the piston over time is the product of the force acting on the piston and the speed of the piston. The electrical energy absorbed from the outside is greater when the piston does not convert all of its kinetic energy into stored energy at each stroke, but when some of its kinetic energy is converted into potential energy that gives the piston a pulse in the opposite direction accelerate him to a certain speed. The potential energy is to be stored in a spring, advantageously in a pneumatic spring 66, as shown in FIGS. 20 and 21. One possible construction including a pressure valve 67 and a suction flap 68 is shown in FIGS. 20 and 21. The suction flap 68 is closed by means of a spring 69. The force and the travel of the pneumatic spring 66 can be adjusted with the pressure level in a buffer 70, which is connected in parallel to the main memory 2 to a line 71, wherein shut-off valves 72, 73 are interposed.
    Another valve, main valve, is shown at 74 in Figs.
    In a connection 75 between the main memory 2 and the buffer 70, a control valve 76 is provided, and further shut-off valves 77 and 78 are arranged in the lines from the reservoirs 2 and from the supply line 79 to the displacement 80 (see Fig. 21) , The pressure valve or the valve body 67, which can be moved up and down according to the illustrations in FIGS. 20 and 21, is also provided with seals 81, wherein a further seal 82 is provided on a stepped support surface on the piston housing. The suction flap 68, which is shown in broken lines in the opened state in FIG. 20, establishes a connection of the displacement 80 with the ambient pressure 83 in this open state. In this open position of the suction flap 68 as shown in FIG. 20, the suction flap 68 abuts against the oblique underside of the valve body 67.
    权利要求:
    Claims (10)
    [1]
    Claims:
    A compressed air storage power plant having a compressed air reservoir, with an electrical input / output circuit, with compression and expansion means having a piston pump, which is switchable between a pumping operation and a generator operation, and with electromagnet means having a core, a closed loop with two parallel straight core parts are wound around the coils, characterized in that between the straight core parts, a magnetically conductive bridge for amplifying the radially emerging from the core component of the induction is arranged.
    [2]
    2. compressed air storage power plant according to claim 1, characterized in that the bridge is formed of soft magnetic material.
    [3]
    3. compressed air storage power plant according to claim 1 or 2, characterized in that the bridge has an auxiliary winding.
    [4]
    4. compressed air storage power plant according to one of claims 1 to 3, characterized in that between the bridge and the core, a gap is released.
    [5]
    5. Compressed-air storage power plant according to claim 4, characterized by a phase shift between an induction in the gap and a current around the core secondary current.
    [6]
    6. compressed air storage power plant according to claim 5, characterized in that the phase shift between the induction in the gap and the secondary current drives the piston to a pumping movement.
    [7]
    7. compressed air storage power plant according to one of claims 4 to 6, characterized in that the piston is formed by a magnetizable piston liquid to enhance the induction.
    [8]
    8. compressed air storage power plant according to claim 7, characterized in that magnetic nanoparticles are contained in the piston liquid.
    [9]
    9. compressed air storage power plant according to one of claims 1 to 8, characterized by a respective energy storage on one side of the piston displacement for storing potential energy to increase the pump power by additional mechanical reactive power.
    [10]
    10. Compressed-air storage power plant according to claim 9, characterized in that the energy store is formed by a spring, in particular compressed air spring.
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    同族专利:
    公开号 | 公开日
    EP3400642A1|2018-11-14|
    EP3790176A1|2021-03-10|
    AT518150B1|2019-04-15|
    WO2017117620A1|2017-07-13|
    EP3400642B1|2020-12-09|
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    法律状态:
    2021-09-15| MM01| Lapse because of not paying annual fees|Effective date: 20210105 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50004/2016A|AT518150B1|2016-01-05|2016-01-05|Compressed air energy storage|ATA50004/2016A| AT518150B1|2016-01-05|2016-01-05|Compressed air energy storage|
    EP17700883.6A| EP3400642B1|2016-01-05|2017-01-05|Compressed air energy storage plant|
    EP20204526.6A| EP3790176A1|2016-01-05|2017-01-05|Compressed air storage power plant|
    PCT/AT2017/060002| WO2017117620A1|2016-01-05|2017-01-05|Compressed air energy storage plant|
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