US20150136351A1 - System for storing and outputting thermal energy having a heat accumulator and a cold accumulator and metho for the operation thereof - Google Patents
System for storing and outputting thermal energy having a heat accumulator and a cold accumulator and metho for the operation thereof Download PDFInfo
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- US20150136351A1 US20150136351A1 US14/394,094 US201314394094A US2015136351A1 US 20150136351 A1 US20150136351 A1 US 20150136351A1 US 201314394094 A US201314394094 A US 201314394094A US 2015136351 A1 US2015136351 A1 US 2015136351A1
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- heat
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- accumulator
- fluid energy
- thermal fluid
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- 238000000034 method Methods 0.000 claims abstract description 34
- 238000007599 discharging Methods 0.000 claims abstract description 28
- 239000002918 waste heat Substances 0.000 claims abstract description 10
- 239000012530 fluid Substances 0.000 claims description 76
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 claims description 6
- 239000000284 extract Substances 0.000 claims description 5
- 238000001816 cooling Methods 0.000 claims description 4
- 229910021529 ammonia Inorganic materials 0.000 claims description 3
- 239000007789 gas Substances 0.000 description 17
- 239000003570 air Substances 0.000 description 16
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 9
- 230000008901 benefit Effects 0.000 description 6
- 239000007788 liquid Substances 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000004364 calculation method Methods 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000007613 environmental effect Effects 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 239000012080 ambient air Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000004146 energy storage Methods 0.000 description 1
- 239000011810 insulating material Substances 0.000 description 1
- 238000012821 model calculation Methods 0.000 description 1
- 239000011148 porous material Substances 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
- F01K3/12—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having two or more accumulators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
Definitions
- the invention relates to a plant for storing and releasing thermal energy with a heat accumulator and a cold accumulator, wherein the heat accumulator can release the stored energy to a first line in a discharging circuit for a working medium at a suitable release point.
- the following units are interconnected in the specified sequence by means of this first line: a first thermal fluid energy machine (especially a pump) which is operated as a working machine, a release point (for example a heat exchanger) for heat from the heat accumulator, and a second thermal fluid energy machine (for example a steam turbine) which is operated as a power machine.
- the described arrangement of the units in the discharging circuit makes it possible for the energy which is stored in the heat accumulator to be released to the working medium and for the second thermal fluid energy machine which is operated as a power machine to be used for driving an electric generator, for example.
- a charging circuit is conversely required and can be selectively put into effect by means of the first line or by means of another line.
- the invention also relates to a method which is implemented by the described plant.
- the terms power machine and working machine are used within the scope of this application so that a working machine absorbs mechanical work in order to fulfill its purpose.
- a thermal fluid energy machine which is used as a working machine is therefore operated as a compressor or fluid compression machine.
- a power machine performs work, wherein a thermal fluid energy machine for performing the work converts the thermal energy which is made available in the working gas.
- the thermal fluid energy machine is therefore operated as a motor.
- thermal fluid energy machine constitutes a generic term for machines which can extract thermal energy from a working fluid—a working gas such as air or steam within the context of this application—or can feed thermal energy to this. Both heat energy and cold energy are to be understood by thermal energy.
- Thermal fluid energy machines also referred to as fluid energy machines for short in the following text
- Hydrodynamic thermal fluid energy machines the impellers of which allow a continuous flow of the working gas, can preferably also be used. Axially acting turbines or compressors are preferably used.
- An object of the invention is to disclose a plant for storing and releasing thermal energy of the type specified in the introduction (for example conversion of mechanical energy into thermal energy with subsequent storage or conversion of the stored thermal energy into mechanical energy) and to disclose a method for its operation, by means of which a comparatively high level of efficiency with at the same time a justifiable cost of the constructional units being used is possible.
- the cold accumulator being able to release the stored cold to a second line at a suitable release point, wherein the second line forms a closed circuit.
- the following units are interconnected in the specified sequence by means of the second line: downstream of said release point for the cold stored in the cold accumulator (that is to say the point at which the cold accumulator can release the stored cold to the second line), provision is made for a third thermal fluid energy machine (for example a pump) which is operated as a working machine, a heat source is then provided and then a thermal fluid energy machine (for example a steam turbine) which is operated as a power machine.
- a third thermal fluid energy machine for example a pump
- a thermal fluid energy machine for example a steam turbine
- Media which in comparison to the temperature level of the cold accumulator have a higher temperature level are suitable as the heat source.
- the environment of the plant for example flowing water
- the waste heat or residual heat of another process is utilized, wherein the temperature level of this process lies above the ambient temperature.
- This process can be a gas turbine circuit, for example. If the gas for this is delivered in liquid form and has first of all to be evaporated, this process can be used for charging the cold accumulator, for example.
- Other configurations are explained in more detail below. To be named among these is especially the thermal energy accumulator, as has already been explained in the introduction.
- thermodynamic fluid energy machines In the first line and in the second line, provision is made in each case for a working medium which conducts a thermodynamic process in the circuit for energy storage or energy generation.
- this can be gaseous or liquid.
- the fluid energy machines have to be optimized to the medium in each case. If this medium is delivered in liquid form then the choice of a pump is especially advantageous.
- hydrodynamic fluid energy machines In the case of supply in the gaseous state, hydrodynamic fluid energy machines (turbocompressors) are preferably used.
- the heat accumulator and the cold accumulator which are provided in the plant can be used independently of each other in two discharging circuits. As a result of this, it is especially made possible to be able to utilize the waste heat of the discharging circuit which is operated with the heat accumulator in the discharging circuit which is operated with the cold accumulator. As a result of this, the yields of the energy stored in the heat accumulator and in the cold accumulator is advantageously increased, as a result of which the overall efficiency of the plant can be increased.
- the heat source consists of a first heat exchanger which can extract heat from the first line and is arranged between the third fluid energy machine and the fourth fluid energy machine.
- This arrangement and principle of operation of the first heat exchanger make it possible, as already indicated, that the waste heat of the discharging circuit formed by the first line can be used in the discharging circuit formed by the second line.
- This temperature level is higher than that of the environment, as a result of which the yield of the release or discharge of the cold accumulator can be advantageously increased.
- the release point for the heat accumulator is formed by a fifth heat exchanger which can feed heat to the first line and which is connected into a circuit formed by a fourth line.
- the following units are interconnected: the fifth heat exchanger, a tenth thermal fluid energy machine which is operated as a working machine, and the heat accumulator.
- the heat accumulator is not incorporated directly into the discharging circuit of the first line but is connected to this via a heat exchanger (fifth heat exchanger).
- This heat exchanger is connected in a circuit to the heat accumulator 14 by means of the fourth line.
- the fluid energy machine in this case circulates the working medium in the fourth line so that the energy stored in the heat accumulator 14 can be introduced into the heat exchanger.
- the advantage of this constructional form is that different working media can be used in the first line and in the fourth line.
- the fifth heat exchanger is especially advantageously designed as a waste heat steam generator, for example. Such heat exchangers are frequently also referred to as waste heat boilers or as HRSGs (heat recovery steam generators).
- the waste heat steam generator is advantageously operated with water so that steam turbines which are current in the market can be used for generating mechanical energy in the circuit formed by the first line.
- the heat accumulator 14 can be operated via the fourth line with air, for example, as working medium. This has the advantage that heat accumulators of larger volume can also be inexpensively produced, since possible leaks in the circuit do not constitute a hazard to the environment.
- the waste heat steam generator (that is to say the fifth heat exchanger) and the second thermal fluid energy machine can advantageously also have a plurality of pressure stages. These pressure stages are formed by corresponding pressure stages—which are interconnected by lines in each being provided both in the heat exchanger and in the fluid energy machine. As a result of this, the yield, and therefore the efficiency, of the discharging process can be advantageously further increased.
- the release point for the cold stored in the cold accumulator consists of a third heat exchanger which can release heat to the second line and is incorporated into a cooling circuit formed by a third line.
- the following units are interconnected: the third heat exchanger, a fifth thermal fluid energy machine which is operated as a working machine, and the cold accumulator.
- the fluid energy machine circulates the working medium in the third line.
- the cold energy stored in the cold accumulator is released via the third heat exchanger to the second line where work can be performed via the fourth fluid energy machine.
- This separation of the circuits via the second line and the third line also has the advantage that the circuit which is formed via the second line can be kept as small as possible.
- ammonia for example, can be used as working medium and put into operation under the high technical safety requirements which are associated therewith.
- air for example, can be used as working medium. This is especially advantageous if the cold accumulator has a large volume on account of the capacity requirements.
- Yet another embodiment of the invention provides that provision is made in the second line between the third thermal fluid energy machine and the first heat exchanger for a fourth heat exchanger which enables a heat input from the environment of the plant into the second line.
- the cold accumulator has a temperature level which lies below the atmospheric ambient conditions. Therefore, heat from the environment can be fed to the working medium in a first step before the heat which is made available in the heat accumulator or in the residual heat of the discharging circuit in the heat accumulator is utilized in a second step.
- the environmental heat is therefore additionally made available to the process, as a result of which the efficiency of the plant can be improved.
- Another object specified in the introduction is also achieved by means of a method for storing and releasing thermal energy via a heat accumulator and a cold accumulator, wherein during the discharging cycle the heat accumulator releases the stored energy to a first line in a discharging circuit for a working medium.
- the following units are arranged in the specified sequence via a first line and are subjected to throughflow of the working medium in this sequence: a first thermal fluid energy machine (especially a pump) which is operated as a working machine, a release point for heat from the heat accumulator, and a second thermal fluid energy machine (especially a steam turbine) which is operated as a power machine.
- the achieving of the object specifically lies in the fact that the cold accumulator releases the stored cold to a second line, wherein the second line forms a closed circuit in which the following units are operated in the specified sequence via the second line: a third thermal fluid energy machine (especially a pump), which is operated as a working machine, downstream of said release point for the cold stored in the cold accumulator, a heat source, and a fourth thermal fluid energy machine, especially a steam turbine, which is operated as a power machine.
- FIGS. 1 and 2 show an exemplary embodiment of the plant according to the invention in the operating states of a charging process ( FIG. 1 ) and discharging process ( FIG. 2 ) in each case as block schematic diagrams, and
- FIG. 3 shows another exemplary embodiment of the plant according to the invention in the operating states of a charging process and discharging process as a block schematic diagram.
- thermal charging and discharging processes of thermal accumulators 12 , 14 , 16 shall be explained in more detail.
- Shown first of all in FIG. 1 is a two-stage charging process which functions according to the principle of a heat pump. Shown here is an open charging circuit which, however, as indicated by dash-dot lines, could be closed using an optionally provided heat exchanger 17 b .
- the states in the working gas, which in the case of the exemplary embodiment of FIG. 1 consists of air, are represented in each case in circles on lines 30 , 31 . At the top on the left, the pressure in bars is indicated. At the top on the right, the enthalpy in KJ/Kg is indicated.
- T 2 is the temperature at the compressor exit
- T 1 is the temperature at the compressor inlet
- ⁇ c is the isentropic efficiency of the compressor
- ⁇ is the pressure ratio (in this case 15:1)
- K is the compressibility, which in the case of air is 1.4.
- the isentropic efficiency ⁇ c can be assumed to be 0.85 in the case of a compressor.
- the heated working gas now passes through the heat accumulator 14 where the main part of the available thermal energy is stored.
- the working gas is cooled to 20° C., whereas the pressure is maintained at 15 bar.
- the working gas is then expanded in two series-connected stages 35 a , 35 b of a seventh fluid energy machine 35 so that it arrives at a pressure level of 1 bar.
- the working gas is cooled to 5° C. after the first stage and cooled to ⁇ 100° C. after the second stage.
- the basis for this calculation is also the formula specified above.
- a water separator 29 In the part of the third line 31 which connects the two stages of the seventh fluid energy machine 35 a , 35 b in the form of a high-pressure turbine and a low-pressure turbine, provision is additionally made for a water separator 29 . After a first expansion, this enables the air to be dried so that the air moisture which is contained in this in the second stage 35 b of the seventh fluid energy machine 35 does not lead to icing of the turbine blades.
- the expanded and therefore cooled working gas extracts heat from the cold accumulator 16 and is heated to 0° C. as a result.
- cold energy is stored in the cold accumulator 16 and can be utilized during a subsequent energy generation.
- the heat exchanger 17 b has to be provided for the case of a closed charging circuit.
- the working gas can be reheated to an ambient temperature of 20° C., as a result of which heat is extracted from the environment and made available to the process.
- Such a measure can naturally be dispensed with if the working gas is drawn directly from the environment since this already has ambient temperature.
- the compressed air is directed through the additional heat accumulator 12 , wherein the flow direction, corresponding to the indicated arrows, runs exactly opposite to the charging circuit which is formed by the third line 31 .
- the air After the air has been brought from ambient pressure (1 bar) and ambient temperature (20° C.) by the compressor to 4 bar and a temperature of 188° C., the air is cooled again to 20° C. by means of the additional heat accumulator 12 .
- the air is then expanded in two steps by means of the stages 37 a , 37 b of a ninth fluid energy machine 37 which operates as a turbine.
- the additional line 30 which connects the two stages 37 a , 37 b for a water separator 29 which functions in the same way as that which is located in the third line 31 .
- this has a temperature of ⁇ 56° C. at ambient pressure (1 bar).
- the additional circuit of the additional line 30 is to be of a closed design, provision therefore has to be made for a heat exchanger 17 c so that the air can be heated from ⁇ 56° C. to 20° C. by heat absorption from the environment.
- the circuits of the third line 31 and of the additional line 30 are set in operation independently of each other. Therefore, the sixth and seventh fluid energy machines are mechanically coupled via the shaft 21 having a motor M1 and the eighth and ninth fluid energy machines are mechanically coupled via the other shaft 21 having a motor M2.
- the electric energy can first drive the motor M2 in order to charge the additional heat accumulator 12 .
- the heat accumulator 14 and the cold accumulator 16 can then be charged by operation of the motor M1 and simultaneous discharging of the additional heat accumulator 12 .
- the additional heat accumulator 12 can then also be recharged by operation of the motor M2.
- the plant is now operated with a discharging circuit which is realized by means of a first line 40 .
- the line 40 constitutes a closed circuit.
- Water is evaporated and superheated by means of the additional heat accumulator 12 , the heat accumulator 14 and optionally by means of a further heat source 41 , e.g. district heat, via a heat exchanger 42 , and so makes its way via the line 40 (valves C and D are closed) to a third thermal energy machine 43 .
- This is constructed in two stages consisting of a high-pressure turbine 43 a and a low-pressure turbine 43 b which are passed through one after the other.
- the high-pressure turbine is supplied with steam of a pressure p h .
- the cold energy stored in the cold accumulator 16 is not made directly available to the circuit formed by the first line 40 but via a first heat exchanger 51 .
- the first heat exchanger 51 is part of a circuit which is formed by a second line 52 .
- This circuit itself serves for energy generation which can be produced via a fourth fluid energy machine 53 in the circuit of the second line 52 .
- the fourth fluid energy machine 53 is connected to a generator G via a shaft 54 .
- the fourth fluid energy machine 53 also additionally drives a fifth fluid energy machine 55 which is used as a compressor (more about this below).
- the cold energy from the cold accumulator 16 is therefore primarily used for energy generation in the circuit formed by the second line 52 (for example by means of a Rankine cycle with ammonia).
- the circuit formed by the first line 40 profits only indirectly from this cold energy.
- the circuit formed by the second line 52 profits from the heat energy which is introduced into this process via the first heat exchanger. The improvement of the overall efficiency of the plant is to be explained by this.
- the cold energy from the cold accumulator 16 can be fed again to the second line 52 via a circuit formed by a third line 56 indirectly via a third heat exchanger 57 .
- the third heat exchanger 57 is provided in the second line.
- a third fluid energy machine in the form of a pump 58 follows after this, as seen in the flow direction.
- Environmental heat for example from a flowing medium, can also be fed via a fourth heat exchanger 59 into the working fluid of the second line 52 before this passes through the first heat exchanger 51 .
- the cold energy from the cold accumulator 16 is fed via the third line to the third heat exchanger 57 .
- this circuit which is formed by the third line 56 provision is also made for the fifth fluid energy machine which effects a circulation of the working fluid in the third line.
- the drive is carried out directly by means of the fourth fluid energy machine 53 via the shaft 54 .
- this circuit which is formed by the third line 56 could even be omitted and instead of the third heat exchanger 57 the cold accumulator 16 is provided directly in the second line 52 . This is indicated by dash-dot lines.
- the second line 52 in the cold accumulator 16 would be connected directly to a passage system which brings about a surface enlargement in the cold accumulator 16 (more about this below).
- valve D By operating the valves C and D, the efficiency of the plant can be improved in the specified operating states.
- the valve D lies in a first bypass line 46 , by means of which the high-pressure turbine 43 a can be bypassed when the valve D is opened.
- This operating state is advisable if the temperature in the heat accumulator 14 is no longer adequate in order to superheat the steam under high pressure conditions. The latter can be caused as a result of a partial discharging or charging of the heat accumulator 14 which is not yet complete.
- the heat accumulator 14 is completely emptied, whereas the additional heat accumulator 12 has already been charged.
- This state can arise, for example, if additional energy could be made available by means of the wind power plant 22 only for a short time, but then an over-demand for electric energy is to be covered.
- the valve C can also be connected to a second bypass line 47 in addition to the valve D.
- the heat accumulator 14 is bypassed by the bypass line 47 so that the additional heat accumulator 12 can be emptied via the low-pressure turbine 43 b . Therefore, thermal energy is already available in the plant and can be converted into electric energy by means of the generator G with satisfying efficiency.
- the cold accumulator 16 is still not charged either since this is charged together with the heat accumulator 14 .
- a condenser 45 is therefore operated via the valve F.
- FIG. 3 Shown in FIG. 3 is another embodiment of the plant in its general view as a block schematic diagram. Unlike in FIGS. 1 and 2 , a unitary presentation has been chosen in this case.
- the circuits formed by the second line 52 and by the third line 56 are designed similar to FIG. 2 in the main.
- FIG. 3 Shown in FIG. 3 , however, is a simpler system for charging the cold accumulator 16 and the heat accumulator 14 than in FIG. 1 .
- the heat accumulator 14 is charged by means of an open circuit which is realized by the line 60 .
- ambient air is fed to a compressor 61 via said line 60 , passes through a heat exchanger 62 where the air is heated to 480° C. and this heat is released to the heat accumulator 14 when passing through it.
- a line 63 also passes through the heat exchanger 62 , forming the circuit by means of which the cold accumulator 16 is cooled.
- the working medium in the line 63 After the working medium in the line 63 has passed through the cold accumulator 16 , this is compressed from ambient conditions to 25 bar via a compressor 64 and heated to 514° C., passes through the heat exchanger 62 , and is then expanded again to 1.1 bar via a turbine 65 . The temperature drops to ⁇ 121° C. in the process. The working medium in the cold accumulator 16 then absorbs heat again and as a result cools this.
- the compressor 64 and the turbine 65 are seated on a shaft 66 and can additionally be driven by means of a motor M which is connected to this shaft 66 .
- the heat accumulator 14 is not incorporated directly into the circuit formed by the first line 40 . Rather, a further circuit is formed by a fourth line 67 , in which circuit there is passage through the following units at a constant pressure of approximately 1 bar.
- the working medium for example air
- the heat exchanger 68 releases the heat to the first line 40 and is cooled to 91° C. (more about this below).
- Working medium then passes through the fourth line 67 to the first heat exchanger 51 so that the residual heat, which was not released to the first line via the fifth heat exchanger 68 , can be released to the second line 52 .
- the working medium in the further process can be cooled further via a condenser 69 , wherein the condenser 69 is also a heat exchanger which is provided in the first line 40 (more about this below).
- the working medium Via a tenth fluid energy machine 70 in the form of a type of circulating pump, the working medium then makes its way again into the heat accumulator 14 where this is reheated.
- the fourth line 67 can also be designed as an open circuit in which the part of the line between the condenser 69 and the tenth fluid energy machine 70 which is detailed by the dash-dot line is omitted.
- the first line 40 forms a circuit by means of which electric current can be generated by a generator G via a shaft 71 .
- one circuit is operated with water, wherein the fifth heat exchanger 68 is operated as a multi-stage waste heat steam generator with a high-pressure stage 68 a and a low-pressure stage 68 b (Rankine cycle).
- the water is fed at ambient temperature by means of a feed pump 44 a at 5.5 bar first of all into the low-pressure stage 68 b of the fifth heat exchanger 68 .
- a part of the water leaves this low-pressure stage 68 b at 4.1 bar and 145° C. in order to be fed (as steam) to the low-pressure stage 43 b of the second thermal fluid energy machine.
- Another part of the water is fed in the liquid state by means of a second feed pump 44 b , to the high-pressure stage 68 a of the fifth heat exchanger 68 and leaves this as steam at 80 bar and 459° C. in order to be fed to the high-pressure stage 43 a of the second thermal fluid energy machine 43 .
- Both the fourth and the second thermal fluid energy machines drive a shaft 71 which is connected to a generator G. After expansion of the steam to 0.03 bar at 24° C., this is fed again via the condenser 69 to the feed pump 44 a.
- the construction of the heat accumulator 14 , of the cold accumulator 16 and of the additional heat accumulator in the case of the plant in the figures is the same in each case and is shown in more detail in FIG. 1 by means of a detailed enlargement based on the cold accumulator 16 .
- a container the wall 24 of which is provided with an insulating material 25 which has large pores 26 .
- FIGS. 1 to 3 can also be combined with each other so that further exemplary embodiments result from this.
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Abstract
Description
- This application is the US National Stage of International Application No. PCT/EP2013/056549 filed Mar. 27, 2013, and claims the benefit thereof. The International Application claims the benefit of European Application No. EP12164473 filed Apr. 17, 2012. All of the applications are incorporated by reference herein in their entirety.
- The invention relates to a plant for storing and releasing thermal energy with a heat accumulator and a cold accumulator, wherein the heat accumulator can release the stored energy to a first line in a discharging circuit for a working medium at a suitable release point. In the discharging circuit, the following units are interconnected in the specified sequence by means of this first line: a first thermal fluid energy machine (especially a pump) which is operated as a working machine, a release point (for example a heat exchanger) for heat from the heat accumulator, and a second thermal fluid energy machine (for example a steam turbine) which is operated as a power machine. The described arrangement of the units in the discharging circuit makes it possible for the energy which is stored in the heat accumulator to be released to the working medium and for the second thermal fluid energy machine which is operated as a power machine to be used for driving an electric generator, for example. For storing the thermal energy in the heat accumulator and in the cold accumulator, a charging circuit is conversely required and can be selectively put into effect by means of the first line or by means of another line. The invention also relates to a method which is implemented by the described plant.
- The terms power machine and working machine are used within the scope of this application so that a working machine absorbs mechanical work in order to fulfill its purpose. A thermal fluid energy machine which is used as a working machine is therefore operated as a compressor or fluid compression machine. Compared with this, a power machine performs work, wherein a thermal fluid energy machine for performing the work converts the thermal energy which is made available in the working gas.
- In this case, the thermal fluid energy machine is therefore operated as a motor.
- The term “thermal fluid energy machine” constitutes a generic term for machines which can extract thermal energy from a working fluid—a working gas such as air or steam within the context of this application—or can feed thermal energy to this. Both heat energy and cold energy are to be understood by thermal energy. Thermal fluid energy machines (also referred to as fluid energy machines for short in the following text) can be designed as piston machines, for example. Hydrodynamic thermal fluid energy machines, the impellers of which allow a continuous flow of the working gas, can preferably also be used. Axially acting turbines or compressors are preferably used.
- The principle specified in the introduction is described according to WO 2009/044139 A2, for example. In this case, piston machines are used in order to implement the method which is described above. According to U.S. Pat. No. 5,436,508, moreover, it is known that by means of the plants for storing thermal energy which are specified in the introduction over-capacities can also be temporarily stored when wind energy is being utilized for producing electric current in order to retrieve this again when required.
- An object of the invention is to disclose a plant for storing and releasing thermal energy of the type specified in the introduction (for example conversion of mechanical energy into thermal energy with subsequent storage or conversion of the stored thermal energy into mechanical energy) and to disclose a method for its operation, by means of which a comparatively high level of efficiency with at the same time a justifiable cost of the constructional units being used is possible.
- This object is achieved according to aspects of the invention by means of the plant specified in the introduction by the cold accumulator being able to release the stored cold to a second line at a suitable release point, wherein the second line forms a closed circuit. In this circuit, the following units are interconnected in the specified sequence by means of the second line: downstream of said release point for the cold stored in the cold accumulator (that is to say the point at which the cold accumulator can release the stored cold to the second line), provision is made for a third thermal fluid energy machine (for example a pump) which is operated as a working machine, a heat source is then provided and then a thermal fluid energy machine (for example a steam turbine) which is operated as a power machine. Media which in comparison to the temperature level of the cold accumulator have a higher temperature level are suitable as the heat source. If the cold accumulator in the charged state has a temperature level which lies below the ambient conditions, the environment of the plant (for example flowing water) can be utilized as the heat source. It is especially advantageous, however, if the waste heat or residual heat of another process is utilized, wherein the temperature level of this process lies above the ambient temperature. This process can be a gas turbine circuit, for example. If the gas for this is delivered in liquid form and has first of all to be evaporated, this process can be used for charging the cold accumulator, for example. Other configurations are explained in more detail below. To be named among these is especially the thermal energy accumulator, as has already been explained in the introduction.
- In the first line and in the second line, provision is made in each case for a working medium which conducts a thermodynamic process in the circuit for energy storage or energy generation. In this case, this can be gaseous or liquid. The fluid energy machines have to be optimized to the medium in each case. If this medium is delivered in liquid form then the choice of a pump is especially advantageous. In the case of supply in the gaseous state, hydrodynamic fluid energy machines (turbocompressors) are preferably used.
- It is the fundamental idea of the invention that the heat accumulator and the cold accumulator which are provided in the plant can be used independently of each other in two discharging circuits. As a result of this, it is especially made possible to be able to utilize the waste heat of the discharging circuit which is operated with the heat accumulator in the discharging circuit which is operated with the cold accumulator. As a result of this, the yields of the energy stored in the heat accumulator and in the cold accumulator is advantageously increased, as a result of which the overall efficiency of the plant can be increased.
- According to one advantageous embodiment of the invention, it is provided that the heat source consists of a first heat exchanger which can extract heat from the first line and is arranged between the third fluid energy machine and the fourth fluid energy machine. This arrangement and principle of operation of the first heat exchanger make it possible, as already indicated, that the waste heat of the discharging circuit formed by the first line can be used in the discharging circuit formed by the second line. This temperature level is higher than that of the environment, as a result of which the yield of the release or discharge of the cold accumulator can be advantageously increased.
- Another embodiment of the invention provides that the release point for the heat accumulator is formed by a fifth heat exchanger which can feed heat to the first line and which is connected into a circuit formed by a fourth line. In this circuit, the following units are interconnected: the fifth heat exchanger, a tenth thermal fluid energy machine which is operated as a working machine, and the heat accumulator. With this is provided a configuration in which the heat accumulator is not incorporated directly into the discharging circuit of the first line but is connected to this via a heat exchanger (fifth heat exchanger). This heat exchanger is connected in a circuit to the
heat accumulator 14 by means of the fourth line. The fluid energy machine in this case circulates the working medium in the fourth line so that the energy stored in theheat accumulator 14 can be introduced into the heat exchanger. The advantage of this constructional form is that different working media can be used in the first line and in the fourth line. The fifth heat exchanger is especially advantageously designed as a waste heat steam generator, for example. Such heat exchangers are frequently also referred to as waste heat boilers or as HRSGs (heat recovery steam generators). The waste heat steam generator is advantageously operated with water so that steam turbines which are current in the market can be used for generating mechanical energy in the circuit formed by the first line. Theheat accumulator 14, however, can be operated via the fourth line with air, for example, as working medium. This has the advantage that heat accumulators of larger volume can also be inexpensively produced, since possible leaks in the circuit do not constitute a hazard to the environment. - The waste heat steam generator (that is to say the fifth heat exchanger) and the second thermal fluid energy machine can advantageously also have a plurality of pressure stages. These pressure stages are formed by corresponding pressure stages—which are interconnected by lines in each being provided both in the heat exchanger and in the fluid energy machine. As a result of this, the yield, and therefore the efficiency, of the discharging process can be advantageously further increased.
- According to a specific embodiment of the invention, it is provided that the release point for the cold stored in the cold accumulator consists of a third heat exchanger which can release heat to the second line and is incorporated into a cooling circuit formed by a third line. In this cooling circuit, the following units are interconnected: the third heat exchanger, a fifth thermal fluid energy machine which is operated as a working machine, and the cold accumulator. The fluid energy machine circulates the working medium in the third line. In this way, the cold energy stored in the cold accumulator is released via the third heat exchanger to the second line where work can be performed via the fourth fluid energy machine. This separation of the circuits via the second line and the third line also has the advantage that the circuit which is formed via the second line can be kept as small as possible. In this system, ammonia, for example, can be used as working medium and put into operation under the high technical safety requirements which are associated therewith. In the third line, air, for example, can be used as working medium. This is especially advantageous if the cold accumulator has a large volume on account of the capacity requirements.
- Yet another embodiment of the invention provides that provision is made in the second line between the third thermal fluid energy machine and the first heat exchanger for a fourth heat exchanger which enables a heat input from the environment of the plant into the second line. In this case, consideration has to be given to the fact that the cold accumulator has a temperature level which lies below the atmospheric ambient conditions. Therefore, heat from the environment can be fed to the working medium in a first step before the heat which is made available in the heat accumulator or in the residual heat of the discharging circuit in the heat accumulator is utilized in a second step. The environmental heat is therefore additionally made available to the process, as a result of which the efficiency of the plant can be improved.
- Another object specified in the introduction is also achieved by means of a method for storing and releasing thermal energy via a heat accumulator and a cold accumulator, wherein during the discharging cycle the heat accumulator releases the stored energy to a first line in a discharging circuit for a working medium. In the discharging circuit, the following units are arranged in the specified sequence via a first line and are subjected to throughflow of the working medium in this sequence: a first thermal fluid energy machine (especially a pump) which is operated as a working machine, a release point for heat from the heat accumulator, and a second thermal fluid energy machine (especially a steam turbine) which is operated as a power machine.
- The achieving of the object specifically lies in the fact that the cold accumulator releases the stored cold to a second line, wherein the second line forms a closed circuit in which the following units are operated in the specified sequence via the second line: a third thermal fluid energy machine (especially a pump), which is operated as a working machine, downstream of said release point for the cold stored in the cold accumulator, a heat source, and a fourth thermal fluid energy machine, especially a steam turbine, which is operated as a power machine. By means of the method according to the invention, with which a plant of the type described above can be operated, the already explained advantages of an efficiency increase, and therefore an increase of efficiency of the running processes, are achieved.
- Further details of the invention are described below with reference to the drawing. The same or corresponding elements of the drawing are provided with the same designations in each case and are repeatedly explained only insofar as differences arise between the individual figures.
- In the drawing
-
FIGS. 1 and 2 show an exemplary embodiment of the plant according to the invention in the operating states of a charging process (FIG. 1 ) and discharging process (FIG. 2 ) in each case as block schematic diagrams, and -
FIG. 3 shows another exemplary embodiment of the plant according to the invention in the operating states of a charging process and discharging process as a block schematic diagram. - Based on a plant according to
FIGS. 1 and 2 , the thermal charging and discharging processes ofthermal accumulators FIG. 1 is a two-stage charging process which functions according to the principle of a heat pump. Shown here is an open charging circuit which, however, as indicated by dash-dot lines, could be closed using an optionally providedheat exchanger 17 b. The states in the working gas, which in the case of the exemplary embodiment ofFIG. 1 consists of air, are represented in each case in circles onlines - In the model calculation for the charging circuit of the
third line 31 according toFIG. 1 , the working gas at 1 bar and 20° C. makes its way into a (previously charged)additional heat accumulator 12 and leaves this at a temperature of 80° C. As a result of compression by means of the sixthfluid energy machine 34, working as a compressor, a pressure increase to 15 bar takes place and consequently also a temperature increase to 540° C. This calculation is based on the following formula -
T 2 =T 1+(T 2s −T 1)/ηc ; T 2s =T 1π(K-1)/K, - wherein
- T2 is the temperature at the compressor exit,
- T1 is the temperature at the compressor inlet,
- ηc is the isentropic efficiency of the compressor,
- π is the pressure ratio (in this case 15:1), and
- K is the compressibility, which in the case of air is 1.4.
- The isentropic efficiency ηc can be assumed to be 0.85 in the case of a compressor.
- The heated working gas now passes through the
heat accumulator 14 where the main part of the available thermal energy is stored. When being stored, the working gas is cooled to 20° C., whereas the pressure is maintained at 15 bar. The working gas is then expanded in two series-connectedstages fluid energy machine 35 so that it arrives at a pressure level of 1 bar. In this case, the working gas is cooled to 5° C. after the first stage and cooled to −100° C. after the second stage. The basis for this calculation is also the formula specified above. - In the part of the
third line 31 which connects the two stages of the seventhfluid energy machine water separator 29. After a first expansion, this enables the air to be dried so that the air moisture which is contained in this in thesecond stage 35 b of the seventhfluid energy machine 35 does not lead to icing of the turbine blades. - In the further process, the expanded and therefore cooled working gas extracts heat from the
cold accumulator 16 and is heated to 0° C. as a result. In this way, cold energy is stored in thecold accumulator 16 and can be utilized during a subsequent energy generation. If the temperature of the working gas at the outlet of thecold accumulator 16 and at the inlet of theadditional heat accumulator 12 is compared, then it becomes clear why theheat exchanger 17 b has to be provided for the case of a closed charging circuit. In this case, the working gas can be reheated to an ambient temperature of 20° C., as a result of which heat is extracted from the environment and made available to the process. Such a measure can naturally be dispensed with if the working gas is drawn directly from the environment since this already has ambient temperature. - So that preheating by means of the
additional heat accumulator 12 can be carried out when the charging circuit of thethird line 31 is being passed through, an additional circuit is put into effect by means of anadditional line 30 by means of which theadditional heat accumulator 12 can be charged. Theadditional heat accumulator 12 has to therefore be connected both to the charging circuit of thethird line 31 and to the additional circuit of theadditional line 30. A connection to thethird line 31 is effected by means of the valves A, whereas a connection to theadditional line 30 is ensured by opening the valves B. During passage through theadditional line 30, the air is first of all directed through an eighthfluid energy machine 36 which operates as a compressor. The compressed air is directed through theadditional heat accumulator 12, wherein the flow direction, corresponding to the indicated arrows, runs exactly opposite to the charging circuit which is formed by thethird line 31. After the air has been brought from ambient pressure (1 bar) and ambient temperature (20° C.) by the compressor to 4 bar and a temperature of 188° C., the air is cooled again to 20° C. by means of theadditional heat accumulator 12. The air is then expanded in two steps by means of thestages fluid energy machine 37 which operates as a turbine. In this case also, provision is made in theadditional line 30 which connects the twostages water separator 29 which functions in the same way as that which is located in thethird line 31. After expansion of the air via the ninthfluid energy machine 37, this has a temperature of −56° C. at ambient pressure (1 bar). In case the additional circuit of theadditional line 30—as shown by dash-dot lines—is to be of a closed design, provision therefore has to be made for aheat exchanger 17 c so that the air can be heated from −56° C. to 20° C. by heat absorption from the environment. - The circuits of the
third line 31 and of theadditional line 30 are set in operation independently of each other. Therefore, the sixth and seventh fluid energy machines are mechanically coupled via theshaft 21 having a motor M1 and the eighth and ninth fluid energy machines are mechanically coupled via theother shaft 21 having a motor M2. In the case of over-capacities of thewind power plant 22, the electric energy can first drive the motor M2 in order to charge theadditional heat accumulator 12. Theheat accumulator 14 and thecold accumulator 16 can then be charged by operation of the motor M1 and simultaneous discharging of theadditional heat accumulator 12. Theadditional heat accumulator 12 can then also be recharged by operation of the motor M2. If all the accumulators are fully charged, an effective discharging cycle for producing electric energy can be initiated (cf.FIG. 2 ). If the over-capacity of thewind power plant 22 should come to an end, however, without theadditional heat accumulator 12 being able to be charged, then the energy available in this can also be replaced by anotherheat source 41, or only theheat accumulator 14 is used (cf.FIG. 2 ). - According to
FIG. 2 , the plant is now operated with a discharging circuit which is realized by means of afirst line 40. Theline 40 constitutes a closed circuit. Water is evaporated and superheated by means of theadditional heat accumulator 12, theheat accumulator 14 and optionally by means of afurther heat source 41, e.g. district heat, via aheat exchanger 42, and so makes its way via the line 40 (valves C and D are closed) to a thirdthermal energy machine 43. This is constructed in two stages consisting of a high-pressure turbine 43 a and a low-pressure turbine 43 b which are passed through one after the other. The high-pressure turbine is supplied with steam of a pressure ph. For supplying the low-pressure turbine 43 b, steam with a lower pressure of p1 is sufficient. This pressure exists in the connectingline 40 between the high-pressure turbine 43 a and the low-pressure turbine 43 b or, in specified operating states, also exists in thebypass line 46 after opening of the valve D. The thirdfluid energy machine 43 drives a generator G via afurther shaft 21. This therefore generates electric current when required while thethermal accumulators - The cold energy stored in the
cold accumulator 16 is not made directly available to the circuit formed by thefirst line 40 but via afirst heat exchanger 51. Thefirst heat exchanger 51 is part of a circuit which is formed by asecond line 52. This circuit itself serves for energy generation which can be produced via a fourthfluid energy machine 53 in the circuit of thesecond line 52. The fourthfluid energy machine 53 is connected to a generator G via ashaft 54. The fourthfluid energy machine 53 also additionally drives a fifthfluid energy machine 55 which is used as a compressor (more about this below). The cold energy from thecold accumulator 16 is therefore primarily used for energy generation in the circuit formed by the second line 52 (for example by means of a Rankine cycle with ammonia). In this case, the circuit formed by thefirst line 40 profits only indirectly from this cold energy. At the same time, however, the circuit formed by thesecond line 52 profits from the heat energy which is introduced into this process via the first heat exchanger. The improvement of the overall efficiency of the plant is to be explained by this. - Downstream of the fourth fluid energy machine, the cold energy from the
cold accumulator 16 can be fed again to thesecond line 52 via a circuit formed by athird line 56 indirectly via athird heat exchanger 57. For this purpose, thethird heat exchanger 57 is provided in the second line. In the second line, a third fluid energy machine in the form of apump 58 follows after this, as seen in the flow direction. Environmental heat, for example from a flowing medium, can also be fed via afourth heat exchanger 59 into the working fluid of thesecond line 52 before this passes through thefirst heat exchanger 51. - As already indicated, the cold energy from the
cold accumulator 16 is fed via the third line to thethird heat exchanger 57. In this circuit which is formed by thethird line 56 provision is also made for the fifth fluid energy machine which effects a circulation of the working fluid in the third line. The drive is carried out directly by means of the fourthfluid energy machine 53 via theshaft 54. Alternatively, this circuit which is formed by thethird line 56 could even be omitted and instead of thethird heat exchanger 57 thecold accumulator 16 is provided directly in thesecond line 52. This is indicated by dash-dot lines. In this, thesecond line 52 in thecold accumulator 16 would be connected directly to a passage system which brings about a surface enlargement in the cold accumulator 16 (more about this below). - By operating the valves C and D, the efficiency of the plant can be improved in the specified operating states. The valve D lies in a
first bypass line 46, by means of which the high-pressure turbine 43 a can be bypassed when the valve D is opened. This operating state is advisable if the temperature in theheat accumulator 14 is no longer adequate in order to superheat the steam under high pressure conditions. The latter can be caused as a result of a partial discharging or charging of theheat accumulator 14 which is not yet complete. - In the extreme case, the
heat accumulator 14 is completely emptied, whereas theadditional heat accumulator 12 has already been charged. This state can arise, for example, if additional energy could be made available by means of thewind power plant 22 only for a short time, but then an over-demand for electric energy is to be covered. In this case, the valve C can also be connected to asecond bypass line 47 in addition to the valve D. In this case, theheat accumulator 14 is bypassed by thebypass line 47 so that theadditional heat accumulator 12 can be emptied via the low-pressure turbine 43 b. Therefore, thermal energy is already available in the plant and can be converted into electric energy by means of the generator G with satisfying efficiency. In this case, thecold accumulator 16 is still not charged either since this is charged together with theheat accumulator 14. For this operating state, acondenser 45 is therefore operated via the valve F. - Shown in
FIG. 3 is another embodiment of the plant in its general view as a block schematic diagram. Unlike inFIGS. 1 and 2 , a unitary presentation has been chosen in this case. The circuits formed by thesecond line 52 and by thethird line 56 are designed similar toFIG. 2 in the main. - Shown in
FIG. 3 , however, is a simpler system for charging thecold accumulator 16 and theheat accumulator 14 than inFIG. 1 . Theheat accumulator 14 is charged by means of an open circuit which is realized by theline 60. In this line, ambient air is fed to acompressor 61 via saidline 60, passes through aheat exchanger 62 where the air is heated to 480° C. and this heat is released to theheat accumulator 14 when passing through it. Aline 63 also passes through theheat exchanger 62, forming the circuit by means of which thecold accumulator 16 is cooled. After the working medium in theline 63 has passed through thecold accumulator 16, this is compressed from ambient conditions to 25 bar via acompressor 64 and heated to 514° C., passes through theheat exchanger 62, and is then expanded again to 1.1 bar via aturbine 65. The temperature drops to −121° C. in the process. The working medium in thecold accumulator 16 then absorbs heat again and as a result cools this. Thecompressor 64 and theturbine 65 are seated on ashaft 66 and can additionally be driven by means of a motor M which is connected to thisshaft 66. - In the exemplary embodiment according to
FIG. 3 , theheat accumulator 14 is not incorporated directly into the circuit formed by thefirst line 40. Rather, a further circuit is formed by afourth line 67, in which circuit there is passage through the following units at a constant pressure of approximately 1 bar. After passing through theheat accumulator 14, the working medium (for example air), heated to 476° C., is fed to afifth heat exchanger 68. Theheat exchanger 68 releases the heat to thefirst line 40 and is cooled to 91° C. (more about this below). Working medium then passes through thefourth line 67 to thefirst heat exchanger 51 so that the residual heat, which was not released to the first line via thefifth heat exchanger 68, can be released to thesecond line 52. The working medium in the further process can be cooled further via acondenser 69, wherein thecondenser 69 is also a heat exchanger which is provided in the first line 40 (more about this below). Via a tenthfluid energy machine 70 in the form of a type of circulating pump, the working medium then makes its way again into theheat accumulator 14 where this is reheated. Instead of the closed circuit shown inFIG. 3 , thefourth line 67 can also be designed as an open circuit in which the part of the line between thecondenser 69 and the tenthfluid energy machine 70 which is detailed by the dash-dot line is omitted. - The
first line 40 forms a circuit by means of which electric current can be generated by a generator G via a shaft 71. To this end, one circuit is operated with water, wherein thefifth heat exchanger 68 is operated as a multi-stage waste heat steam generator with a high-pressure stage 68 a and a low-pressure stage 68 b (Rankine cycle). The water is fed at ambient temperature by means of afeed pump 44 a at 5.5 bar first of all into the low-pressure stage 68 b of thefifth heat exchanger 68. A part of the water leaves this low-pressure stage 68 b at 4.1 bar and 145° C. in order to be fed (as steam) to the low-pressure stage 43 b of the second thermal fluid energy machine. Another part of the water is fed in the liquid state by means of asecond feed pump 44 b, to the high-pressure stage 68 a of thefifth heat exchanger 68 and leaves this as steam at 80 bar and 459° C. in order to be fed to the high-pressure stage 43 a of the second thermalfluid energy machine 43. Both the fourth and the second thermal fluid energy machines drive a shaft 71 which is connected to a generator G. After expansion of the steam to 0.03 bar at 24° C., this is fed again via thecondenser 69 to thefeed pump 44 a. - The construction of the
heat accumulator 14, of thecold accumulator 16 and of the additional heat accumulator in the case of the plant in the figures is the same in each case and is shown in more detail inFIG. 1 by means of a detailed enlargement based on thecold accumulator 16. Provided is a container, the wall 24 of which is provided with an insulatingmaterial 25 which haslarge pores 26. Provision is made inside the container for concrete 27 which functions as a heat accumulator or a cold accumulator.Pipes 28 which extend in parallel are laid within the concrete 27 and the working gas flows through these and in the process releases heat or absorbs heat (depending on the type of operation and type of accumulator). - The charging and discharging circuits of
FIGS. 1 to 3 can also be combined with each other so that further exemplary embodiments result from this.
Claims (18)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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EP12164473.6 | 2012-04-17 | ||
EP12164473.6A EP2653670A1 (en) | 2012-04-17 | 2012-04-17 | Assembly for storing and emitting thermal energy with a heat storage device and a cold air reservoir and method for its operation |
PCT/EP2013/056549 WO2013156284A1 (en) | 2012-04-17 | 2013-03-27 | System for storing and outputting thermal energy having a heat accumulator and a cold accumulator and method for the operation thereof |
Publications (1)
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US20150136351A1 true US20150136351A1 (en) | 2015-05-21 |
Family
ID=48045492
Family Applications (1)
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US14/394,094 Abandoned US20150136351A1 (en) | 2012-04-17 | 2013-03-27 | System for storing and outputting thermal energy having a heat accumulator and a cold accumulator and metho for the operation thereof |
Country Status (4)
Country | Link |
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US (1) | US20150136351A1 (en) |
EP (2) | EP2653670A1 (en) |
CN (1) | CN104302876A (en) |
WO (1) | WO2013156284A1 (en) |
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US20180016948A1 (en) * | 2015-02-11 | 2018-01-18 | Futurebay Limited | Apparatus and method for energy storage |
GB2552963A (en) * | 2016-08-15 | 2018-02-21 | Futurebay Ltd | Thermodynamic cycle apparatus and method |
US10724767B2 (en) * | 2016-07-14 | 2020-07-28 | Hitachi Plant Mechanics Co., Ltd. | High-pressure hydrogen filling system with expansion turbine |
CN114592937A (en) * | 2022-04-11 | 2022-06-07 | 中国科学院工程热物理研究所 | Electricity storage system and method for compressed air and heat pump electricity storage coupling |
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EP3247887A1 (en) * | 2015-03-20 | 2017-11-29 | Siemens Aktiengesellschaft | Excess air valves for pressure control |
PT3379040T (en) * | 2017-03-20 | 2021-04-15 | Lumenion Gmbh | Power plant for generating electric power and a method for operating a power plant |
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Also Published As
Publication number | Publication date |
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EP2825737A1 (en) | 2015-01-21 |
WO2013156284A1 (en) | 2013-10-24 |
CN104302876A (en) | 2015-01-21 |
EP2653670A1 (en) | 2013-10-23 |
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