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WO2014134744A1 - Procédé et dispositif d'exploitation de la chaleur d'une centrale solaire - Google Patents

Procédé et dispositif d'exploitation de la chaleur d'une centrale solaire Download PDF

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Publication number
WO2014134744A1
WO2014134744A1 PCT/CH2014/000023 CH2014000023W WO2014134744A1 WO 2014134744 A1 WO2014134744 A1 WO 2014134744A1 CH 2014000023 W CH2014000023 W CH 2014000023W WO 2014134744 A1 WO2014134744 A1 WO 2014134744A1
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WO
WIPO (PCT)
Prior art keywords
heat
pressure
power plant
solar power
operating mode
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CH2014/000023
Other languages
German (de)
English (en)
Inventor
Andrea PEDRETTI-RODI
Aldo Steinfeld
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Airlight Energy IP SA
Original Assignee
Airlight Energy IP SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Airlight Energy IP SA filed Critical Airlight Energy IP SA
Priority to EP14709522.8A priority Critical patent/EP2964908A1/fr
Publication of WO2014134744A1 publication Critical patent/WO2014134744A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/40—Solar thermal energy, e.g. solar towers
    • Y02E10/46—Conversion of thermal power into mechanical power, e.g. Rankine, Stirling or solar thermal engines

Definitions

  • the present invention relates to a method for the utilization of heat by a solar power plant according to the preamble of claim 1 and to a solar power plant for carrying out this method according to the preamble of claim 5.
  • Solar power plants of the type mentioned are known to the person skilled in the art, they produce heat which is continuously converted into a recycling unit downstream of the solar field or the heat storage, for example by a turbine arrangement into electricity, or which is used as heat in an industrial process.
  • heat storage is necessary in particular for solar power plants, since the energy production of a solar power plant is determined by the local weather conditions at the site of the power plant and thus poor or not on the current energy needs in the connected power grid or the connected industry, which does not use the energy in the form of electricity , can be designed.
  • Dish Stirling systems are equipped with paraboloid mirrors that focus the sunlight at a focal point where a heat receiver is located.
  • the mirrors are rotatably mounted biaxially in order to be able to track the current position of the sun, and have a diameter of a few meters up to 10 m and more, which then achieves powers of up to 50 kW per module.
  • a Sterling engine installed on the heat receiver converts the thermal energy directly into mechanical work, which in turn generates electricity.
  • Solar tower power plant systems have a central, raised (on the "tower") mounted absorber for hundreds to thousands of individual mirrors with mirrored to him sunlight, so the radiation energy of the sun on the many mirrors or concentra- concentrated in the absorber and so temperatures up to 1300 ° C can be achieved, which is favorable for the efficiency of the downstream thermal machines (usually a steam or fluid turbine power plant for power generation). California Solar has a capacity of several MW.
  • Parabolic trough power plants have a large number of collectors, which have long concentrators with a small transverse dimension, and thus have not a focal point, but a focal line. These line concentrators today have a length of 20 m to 250 m.
  • an absorber tube for the concentrated heat, which transports them to the power plant.
  • a transport medium such as thermal oil or superheated steam in question, or even air.
  • the temperatures achievable in the absorber tube are increased, from 400 ° C now generally to around 500 ° C, with 600 ° C or even more, for example 650 ° C sought and kept realistic in the near future.
  • Parabolic trough power plants are becoming increasingly popular, with heat produced to varying degrees, for example, the nine SEGS parabolic trough power plants in Southern California together produce an output of approximately 350 MW. Furthermore, such power plants are designed today for a variety of locations, with impassable areas, such as desert areas come into question. For large and for smaller solar power plants, it has become established to drive steam turbines with the heat generated by the solar field and thus generate electricity, for example.
  • the heat accumulator itself can be switched directly into the circulation of the fluid transporting the accumulator heat, which makes it possible, for example, to provide another heat recovery unit instead of the Rankine cycle with steam turbines. Even if the heat is not converted by the utilization unit into mechanical work, appropriate system can be simplified.
  • the heat accumulator is arranged as such in a pressure zone, it can be conventionally formed and optimized for its function, without the function-optimized design is disturbed or more expensive by the pressure compatibility according to the invention. This allows a simple and inexpensive construction of the heat accumulator.
  • the heat storage itself is designed as an accumulator, in addition to large particular small power plant units can be equipped according to the invention.
  • the storage heat-transporting fluid is supplied to the heat accumulator under substantially the operating input pressure of a turbine arrangement connected downstream of the heat accumulator, in this case isobarically heated and fed directly by the latter to the turbine arrangement.
  • FIG. 1 schematically shows a conventional solar power plant which has a heat accumulator and generates electricity with the aid of a Rankine cycle
  • FIG. 2 shows a diagram of a solar power plant according to the invention which has a heat accumulator and converts the heat of the solar field into mechanical work with the aid of a Brayton cycle;
  • FIG. 3 schematically shows a further embodiment of the solar power plant according to the invention from FIG. 2 with a modified compressor arrangement
  • Figure 4 schematically shows a preferred embodiment of the invention with a plurality of heat accumulators
  • Figure 5 shows schematically the solar power plant of Figure 2, wherein the heat storage is shown in detail.
  • FIG. 1 schematically shows a conventional solar power plant 1 with a solar array 2 comprising solar panels 3 for solar radiation 4.
  • a heat accumulator 5 is loaded with the heat collected in the solar field and discharged again as needed.
  • a line assembly 6, which is designed for an operating mode and an operating mode discharged is used.
  • the line arrangement is designed for an operating mode and an operating mode discharged.
  • the dashed line 10 symbolizes the difference between the operating mode charging and the operating mode discharging the line arrangement 6: Either the line branch
  • the steam generator 9 generates saturated superheated steam from the water supplied via the closed line branch 11 for a turbine arrangement 12, which here drives a generator 6 which supplies the power grid 16 with power.
  • water is conveyed via a water pump 13 into the steam generator 9, while behind the turbine assembly 12 of the expanded steam passes into a condenser 14, and then the correspondingly formed water then again via the water pump 13 in the steam generator.
  • the line branch 11 together with its components (steam generator 9, turbine assembly 12 and condenser 14) known to those skilled in the Rankine - cycle cycle, which is tested and reliable, but expensive to manufacture and operate and the usual recovery unit for the collected heat from solar power plants.
  • FIG. 2 schematically shows a basic embodiment of the solar power plant 20 according to the invention.
  • a line arrangement 16 connects the solar field 2, the heat accumulator 5, the compressor arrangement 26 and a turbine arrangement 25 with one another.
  • the line assembly 16 has a closed line branch 21 for heat from the solar field transporting fluid, which connects the solar panel 2 and the heat storage 5 with each other. Load in the operating mode, the line branch 21 is connected in such a way that the heat accumulator 5 is loaded by the fluid flowing through it with heat.
  • the heat accumulator 5 is located in an overpressure zone 22 formed by the space 23, which can be set under a predetermined pressure (ambient pressure / operating pressure of the heat from the solar field transporting fluid / input operating pressure of the utilization unit).
  • the overpressure zone 22 is preferably pressurized by the compressor assembly 26 via the pressure line 28, s. the description below.
  • the fluid transporting the heat from the solar field 2 is preferably a gas, particularly preferably ambient air.
  • the figure further shows a turbine assembly 25, the turbines in the operating mode discharged with a gas, preferably with ambient air can be operated, and in turn drives a generator G, which supplies the power grid 16 with power. Also shown is a compressor assembly 26 that can compress the gas to the operating input pressure of the turbine assembly 25.
  • the open branch 28 of the line assembly 16 which on the one hand connects the compressor land 26 with the space 23 (and thus with the overpressure zone 22) via the line 28 and on the other hand the compressor assembly 26 to the heat storage 5 via the line 29 operable.
  • the line branch 28 connects the heat accumulator 5 with the turbine assembly 25.
  • the line branch 28 is actively connected and the compressor assembly 26 in operation so that it sucks ambient air via its intake 27, compressed to the operating input pressure of the turbine assembly 25 and via line 28, the pressure in the space 23 substantially to the pressure level of the operating input pressure Turbine arrangement 25 brings and holds.
  • the compressor assembly 26 conveys the ambient air as storage heat transporting fluid under the operating input pressure of the turbine assembly 25 via line 29 to the heat storage 5, through it and via Leitu ng 30 to the turbine assembly 25.
  • the heat transferring the storage fluid is substantially isobar from a lower operating temperature (here: the ambient temperature) to an upper operating temperature (here: the Radioeingangstermperatur the recovery unit) heated, causing the heat storage 5 discharges.
  • the compressor assembly 26 can also load in the operating mode, as described above, via the pressure line 28, the pressure zone 22 under appropriate pressure (for example, operating pressure of the heat from the solar field transporting fluid) set. Then, the heat accumulator is disposed in an overpressure zone, which can be set in operation under changing, predetermined pressure.
  • This arrangement corresponds to that of a known gas turbine (Brayton - Cycle), such as is used in aircraft, the heat storage by its integration in the line branch 28 with the direct connection to the turbine assembly 25, the function the combustion chamber Fulfills.
  • the design of the heat accumulator can be fundamentally simplified due to the arrangement in an overpressure zone since it is not exposed to compressive stress due to the fluid transporting the accumulator heat through it (see the description of FIG. 5 and WO 2012/027854, cf. which discloses a corresponding heat storage).
  • a conventional heat storage with only minor modifications for the described operation can be used.
  • the heat accumulator as an accumulator, so that it can be used without overpressure zone, for example, if the location of the power plant complicates the creation of an overpressure zone by local conditions (see the description of Figure 5).
  • the construction cost of such a pressure accumulator is considerable, especially in the case of large systems, so that an accumulator is also suitable for large systems, but is preferable for smaller installations.
  • the heat accumulator is designed such that the heat transfer fluid can flow through it at a pressure level that corresponds to the pressure level of the operating input pressure downstream of the utilization unit.
  • the input pressure of the turbine assembly 25 may be between 15 and 30 bar, but also in the concrete case, depending on the design of the utilization unit lower (for example 8 bar) or significantly higher values, for example over 50 bar or reach over 70 bar.
  • the space 23 is formed by an underground cavern, which is created in the underground at the site of the solar power plant.
  • a rocky or rocky reason is not a mandatory requirement, since, for example, solidified and stabilized bulk material such as earth or sand absorb very high compressive stresses and thus can stabilize the walls of the room 23, so that the effort to build the space surrounding the overpressure zone remains comparatively low.
  • the heat accumulator directly in the subsoil, so that it is not in an overpressure zone, but is protected by the surrounding substrate against the pressure of the fluid heat flowing through it, ie in the sense of the present invention represents an accumulator.
  • the result is a method for the recovery of heat by a solar power plant, which collects in the field of collectors heat and stored in a heat storage and fed to the recovery of a downstream utilization unit, and wherein the heat in the utilization of the heat in the heat storage substantially the pressure level is maintained, which corresponds to the input pressure of the downstream recycling unit.
  • the solar power plant according to the invention solar power plant is provided with a heat storage, which stores heat generated by the solar field, and with a line arrangement the solar field the heat storage and a utilization unit for the heat operatively connected to each other and load for an operating mode and discharged for an operating mode of the heat accumulator is, and wherein the heat accumulator is formed, discharged in the operating mode to transfer heat to a heat transferable storage heat fluid, which is at a pressure level which substantially corresponds to the input pressure of the downstream utilization unit.
  • FIG. 3 shows a further embodiment of the solar power plant 40 according to the invention with a modified compressor arrangement 41 which here has a two-stage compressor with the compressors 42 and 43, wherein a heat exchanger formed as a chill 44 in the illustrated embodiment is connected between the compressors 43 and 44.
  • Chiliers are sorption refrigeration machines which are fundamentally known to the person skilled in the art, in which the required energy is supplied in the form of heat (apart from a drive for the internal friction losses of the chiller), which here at the output of the turbine arrangement 25 in the form of residual heat of the fluid transporting the heat is present.
  • the line branch 28 of the line arrangement 16 has a discharge 45 for heat transferring fluid, which leads to the chill 44, in which the fluid residual heat is removed before it leaves the further derivative 46 this.
  • a supply line 47 for heat transferring fluid is provided, which heated by the first compressor stage (compressor 43) Fluid passes through the chiller 44 where it cools before entering the second compressor stage (compressor 42).
  • the person skilled in the art can form the compressor assembly with a different number of stages or with a different cooling for the compressed fluid, as is optimal in the specific case for the efficiency of the power plant.
  • the line arrangement switches in the operating mode unload the heat storage preferably in an open circuit, wherein the guided through the line arrangement, storage heat transporting fluid is then ambient air. It is indicated by the dashed arrow 46 in FIG. 3 that the open line branch 28 is also closed and then a fluid other than air can be used as fluid transporting the heat of storage. Again, this is a matter of the design of the solar power plant in the specific case.
  • FIG. 4 schematically shows an embodiment of the solar power plant 50 according to the invention with a plurality of heat accumulators, here the two heat accumulators 51 and 52.
  • a line arrangement 53 operably connects the solar field 2, the heat accumulators 51, 52, and the utilization unit comprising a compressor arrangement 54 and a turbine arrangement 55 for the heat from the solar field 2.
  • the line assembly 53 is loaded for an operating mode and designed to discharge an operating mode.
  • the closed line branch 56 for heat from the solar field transporting fluid and discharged for the operating mode the open line branch 57 is provided for heat-transporting fluid or active.
  • the closed line branch 56 has a line section 58 connecting the solar field 2 to the heat accumulators 51, 52, which branches off in front of the heat accumulators 51, 52 and has a shut-off valve 61, 62 in each line branch 59, 60, so that heat is transferred from the solar field to the transporting fluid one, two or none of the heat storage 51,52 can be supplied as desired.
  • Corresponding return lines 63, 64 are likewise provided with shut-off valves 65, 66 and are combined behind the heat accumulators 51, 52 in a line 67 so that the heat from the solar field 2 is recirculated into the circuit after passing through the heat accumulators 51, 52 can be.
  • the here open line branch 57 is constructed analogously: a suction line 70 for ambient air leads to the compressor assembly 54, according to which a branching line section 71 with line branches 72,73 supplies the heat storage 51,52 with storage heat transporting fluid. Shut-off valves 74, 75 allow the fluid to be selectively supplied to one, both or none of the heat accumulators 51, 52.
  • a pressure line 80 passes through the compressor assembly 54 compressed fluid in the overpressure zone 22 forming space 23, which can be pressurized, namely alternately under ambient pressure or the pressure that prevails in the heat-transporting fluid, or below the operating input pressure of the Turbine arrangement 55.
  • the line assembly 53 (as the line arrangements according to Figures 2 and 3 also) load for an operating mode and discharged for a mode of operation of the heat accumulator, the line assembly in the operating mode load for the passage of heat-laden, heat from the solar field transporting fluid is formed by the heat storage and discharged in the operating mode, the heat storage rather switched with a turbine assembly in series, such that it is supplied with storage heat transporting fluid.
  • a plurality of heat accumulators are provided and connected to the line arrangement so that it can be switched to a different operating mode for different heat accumulators, such that during operation, for example, a heat accumulator is charged and a heat accumulator is not charged.
  • the shut-off valves 61 and 65 are opened, so that the heat accumulator 51 through the line 58 with heat from the solar field 2 transporting fluid Weg- is flowing, until the heat storage 51 is charged with heat.
  • the closed shut-off valves 62 and 66 prevent heat from the solar field 2 from transporting fluid into the heat accumulator 52.
  • the heat accumulator 52 can be flowed through by storage heat transporting fluid by the shut-off valves 75,79 opened and the shut-off valves 74,79 are kept closed, until the heat accumulator 52 is discharged. Thereafter, the cycle can be reversed, that is, the valves mentioned switched and so the heat storage 51 discharged and the heat storage 52 are loaded.
  • compressor assembly 54 in multiple stages and, according to the embodiment of Figure 3, a cooling arrangement for the compressed, heat storage fluid provide.
  • turbine assembly 55 and compressor assembly 54 are interconnected by a mechanical connection 82, as is often the case with gas turbines having combustors, and now also for the recovery unit of solar power plant 50 (or the embodiment of FIG. 2 or 3) ) can be realized.
  • the skilled person can provide more than two heat storage and form the line arrangement such that, if desired, each heat storage in combination with others or independently operated independently of the others, i. loaded with heat, or discharged, or can be kept in an idle state to optimize the operation of the solar power plant for a given time.
  • the turbine assembly can be operated without detour via a heat storage, as the mentioned heat exchanger takes its place, which is desirable depending on the current needs of the solar power plant (for example, maintenance of the heat storage).
  • FIG. 5 schematically shows the embodiment of the solar power plant 20 according to the invention from FIG. 2, wherein, in contrast to FIG. 2, the turbine arrangement 26 is mechanically connected to the compressor arrangement 25.
  • the overpressure zone 22 is shown in the ground 91, with a heat accumulator 5 also shown concretely in the cross section.
  • the heat accumulator 5 has a dry filling of bulk material 92, which can be flowed through by heat laden fluid, for example from top to bottom and thus the bulk material from top to bottom, in layers, heats up. Due to the thermal expansion of the bulk material, this pressure exerts on the walls 93 of the heat accumulator 5. Because the walls 93 expand (eg, in the manner of an inverted truncated cone) towards the top (ie, the bulk container widens upwardly), the back pressure (force vector 94) of the walls 93 on the bulk material 92 is not horizontal, but somewhat upwards , with the result that its horizontal component 95 resists the expansion pressure of the bulk material 92 and a vertical component 96 pushes it slightly upwards.
  • heat laden fluid for example from top to bottom and thus the bulk material from top to bottom, in layers, heats up. Due to the thermal expansion of the bulk material, this pressure exerts on the walls 93 of the heat accumulator 5. Because the walls 93 expand (eg, in the manner of an
  • heat accumulator 5 is exposed to no (or only insignificant) compressive stress due to the fluid conveyed through it due to the external pressure which can be adjusted by the overpressure zone 22 via the pressure line 28.
  • a comparatively weakly loaded heat accumulator 5 with walls which widen upwards in this way is therefore particularly easy to build and maintain, but is suitable for passing and heating storage heat transporting fluid under the above-mentioned operating pressures.
  • the side wall 93 of the heat accumulator 5 is supported against the outside by a clustered accumulation 98 of bulk material, which is preferably compressed. Without thereby filling the overpressure zone 22, this results in a considerable support of the side walls 93, since accumulated and possibly compacted bulk material can absorb high loads due to the internal wedging of the bulk material particles.
  • the accumulated bulk material can be further supported by an outer wall 99 (which is also indicated only by dashed lines) against the outside. Due to the above-mentioned internal wedging of the bulk material particles, this outer wall 99 does not have to absorb high loads, even if the expansion pressure of the bulk material 92 in the heat accumulator 5 is considerable.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

La présente invention concerne un procédé d'exploitation de chaleur par une centrale solaire. De la chaleur est collectée dans le champ de collecteurs (2) et stockée dans un accumulateur de chaleur (5) et envoyée à un module d'exploitation (25) en aval afin d'être exploitée. Lors de l'exploitation de la chaleur, la pression dans l'accumulateur de chaleur est maintenue sensiblement au niveau correspondant à la pression d'entrée du module d'exploitation en aval. Une centrale solaire servant à mettre ce procédé en œuvre possède un accumulateur de chaleur qui accumule la chaleur générée par le champ solaire et un système de conduites qui relient entre eux le champ solaire, l'accumulateur de chaleur ainsi qu'un module d'exploitation de manière thermiquement fonctionnelle et qui est adapté pour travailler dans un mode chargement ainsi que dans un mode déchargement de l'accumulateur de chaleur. L'accumulateur de chaleur est disposé dans une zone de surpression qui peut être soumise à une pression variable prédéterminée en service.
PCT/CH2014/000023 2013-03-07 2014-02-17 Procédé et dispositif d'exploitation de la chaleur d'une centrale solaire Ceased WO2014134744A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP14709522.8A EP2964908A1 (fr) 2013-03-07 2014-02-17 Procédé et dispositif d'exploitation de la chaleur d'une centrale solaire

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH556/13 2013-03-07
CH00556/13A CH707730A1 (de) 2013-03-07 2013-03-07 Verfahren zur Verwertung der Wärme eines Solarkraftwerks sowie Solarkraftwerk.

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WO2014134744A1 true WO2014134744A1 (fr) 2014-09-12

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EP (1) EP2964908A1 (fr)
CH (1) CH707730A1 (fr)
WO (1) WO2014134744A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2006878A (en) * 1977-10-18 1979-05-10 Rolls Royce Solar Heated Gas Turbine Plant
EP0006211A1 (fr) * 1978-06-16 1980-01-09 Ciba-Geigy Ag Dispositif pour la préparation d'eau chaude par l'énergie solaire
US4280482A (en) * 1979-07-16 1981-07-28 Seige Corporation Method and apparatus for collecting, intensifying and storing solar energy
US4543945A (en) 1984-02-06 1985-10-01 William P. Green Structure and manufacture of radiation collectors
WO2008153946A2 (fr) * 2007-06-06 2008-12-18 Ausra, Inc. Centrale à cycle combiné
WO2012027854A2 (fr) 2010-08-30 2012-03-08 Airlight Energy Ip Sa Accumulateur de chaleur

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2006878A (en) * 1977-10-18 1979-05-10 Rolls Royce Solar Heated Gas Turbine Plant
EP0006211A1 (fr) * 1978-06-16 1980-01-09 Ciba-Geigy Ag Dispositif pour la préparation d'eau chaude par l'énergie solaire
US4280482A (en) * 1979-07-16 1981-07-28 Seige Corporation Method and apparatus for collecting, intensifying and storing solar energy
US4543945A (en) 1984-02-06 1985-10-01 William P. Green Structure and manufacture of radiation collectors
WO2008153946A2 (fr) * 2007-06-06 2008-12-18 Ausra, Inc. Centrale à cycle combiné
WO2012027854A2 (fr) 2010-08-30 2012-03-08 Airlight Energy Ip Sa Accumulateur de chaleur

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Publication number Publication date
CH707730A1 (de) 2014-09-15
EP2964908A1 (fr) 2016-01-13

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