WO2010019990A1 - Système de collecte d'énergie solaire et système de génération d'énergie comprenant un système de collecte d'énergie solaire - Google Patents

Système de collecte d'énergie solaire et système de génération d'énergie comprenant un système de collecte d'énergie solaire Download PDF

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Publication number
WO2010019990A1
WO2010019990A1 PCT/AU2009/001050 AU2009001050W WO2010019990A1 WO 2010019990 A1 WO2010019990 A1 WO 2010019990A1 AU 2009001050 W AU2009001050 W AU 2009001050W WO 2010019990 A1 WO2010019990 A1 WO 2010019990A1
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WO
WIPO (PCT)
Prior art keywords
working fluid
fluid
heat transfer
solar energy
power generation
Prior art date
Application number
PCT/AU2009/001050
Other languages
English (en)
Inventor
Kenneth William Patterson Drysdale
Original Assignee
Renewable Energy Systems Limited
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 Renewable Energy Systems Limited filed Critical Renewable Energy Systems Limited
Publication of WO2010019990A1 publication Critical patent/WO2010019990A1/fr

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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
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S20/00—Solar heat collectors specially adapted for particular uses or environments
    • F24S20/20—Solar heat collectors for receiving concentrated solar energy, e.g. receivers for solar power plants
    • 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

Definitions

  • the present invention relates to a power generation system which can utilise relatively low temperature heat sources to generate power, and in particular, but not exclusively, to a system which utilises solar energy in the production of electricity.
  • Vapour compression heat pump systems are used in refrigeration and air conditioning systems around the world to keep the atmosphere in a designated area below an ambient temperature, or to cool fluids. Heat is taken from the target fluid or atmosphere and is rejected to a heat sink, usually atmospheric air or a wafer source. Energy is consumed during this process, usually in the form of electricity to drive one or more refrigerant compressors. It is the heat extraction which is the desired result of such systems, With the rejection of heat to the heat sink being a by-product. Most such systems reject heat at a relatively low temperature, which is not suitable for powering traditional power generation equipment.
  • Ranki ⁇ e cycle may be summarised as follows:
  • a working fluid for example water
  • a boiler also referred to herein as an evaporator
  • the - temperature of the working fluid may be 400 0 C or greater at this stage, if traditional working fluids such as water are used.
  • the working fluid enters an energy conversion device, typically a turbogenerator (referred to ' hereinafter as a turbine), which converts a portion of the energy in the working fluid to electrical energy.
  • a turbogenerator referred to ' hereinafter as a turbine
  • the temperature and pressure of the working fluid are lowered as a result of this work.
  • the working fluid enters a condenser, where superheat and latent heat in the working fluid are rejected.
  • the working fluid leaves the- condenser as a liquid.
  • the liquid is pumped back to the boiler and the cycle begins again. It would be desirable to create a system which could convert the waste heat rejected from relatively low temperature heat sources such as air conditioning systems, boiler flues and the like, as well as waste heat from other relatively low temperature sources, to useful energy. It would also be desirable to utilise solar energy to create power.
  • Solar cells normally fall into one of two categories namely, photovoltaic and solar thermal. As the majority of the energy In the radiant spectrum (circa 70%) is in the infra red spectrum (heat radiation), efficient solar thermal heat capture, combined, with a low temperature means of power generation should produce the most efficient means of capturing and utilising solar energy.
  • fluid is used herein to describe a fluid in any state, including liquid, gas or saturated vapour, or any combination of liquid, gas and saturated vapour, except where the context clearly requires otherwise.
  • vapour is used to describe saturated and/or superheated vapour, except where the context clearly requires otherwise,
  • a solar energy collection system including a solar energy collector, a heat transfer fluid storage means, and means for transferring a heat transfer fluid from the heat transfer fluid storage means to the solar energy collector and means for returning the heat transfer fluid from the solar energy collector to the heat transfer fluid storage means, the system further including a heat exchange means and means for transferring the heat transfer fluid from the heat transfer fluid storage means to the heat exchange means, and means for returning the heat exchange fluid to the heat transfer fluidstorage means from the heat exchange means.
  • the means for transferring the heat transfer fluid from the heat transfer fluid storage means to the solar energy collector includes a heat transfer fluid pumping means.
  • the pumping means is a variable rate pumping means
  • the solar energy collection system includes a control means for controlling the flow rate of the heat transfer fluid pumping means.
  • control system Is adapted to monitor a temperature of the heat transfer fluid in the heat transfer fluid storage means, and to control the flow rate of the heat transfer fluid pumping means in order to maximise the temperature of the heat transfer fluid in the heat transfer fluid storage means.
  • the solar energy collector includes a plurality of extruded aluminium strips, each said strip provided with a plurality of flow paths therethrough.
  • the heat transfer fluid flows in series through the flow paths provided in the individual aluminium strips.
  • a power generation system including a closed working fluid circuit including;
  • a superheater means for superheating a working fluid vapour an energy conversion means adapted to receive working fluid vapour from the superheating means and to convert internal energy of the working fluid vapour to useful energy, ⁇ a condensing means adapted to remove heat from the working fluid, thereby at least .
  • the condensing means having an inlet in fluid communication with an outlet of the energy conversion means, a subcooling means having an inlet in fluid communication with an outlet of the condensing means, the subcooli ⁇ g means adapted to remove heat from the working fluid so that the working fluid becomes a subcooled liquid, a receiver for collecting the subcooled working fluid, a working fluid pumping means for circulating the working fluid around the working fluid circuit, means for dividing the working fluid into first and second parallel streams, wherein the first parallel stream flows through a first parallel flow path, and the second parallel
  • first parallel flow path includes a first heating means adapted to vaporise the working fluid
  • second parallel flow path includes second heating means adapted to heat the working fluid with heat removed from the working fluid in the condensing means, and pressure reducing means upstream of the second heating
  • the pressure reducing means adapted to reduce a pressure of the working fluid to below a condensation pressure of the working fluid
  • the working fluid circuit further including an ejector pump having a motive fluid inlet in fluid communication with the first parallel flow path and a suction fluid inlet in fluid communication with the second parallel flow path, wherein the ejector pump
  • the working fluid is heated with energy collected by a solar energy collector.
  • the energy collected by the solar energy collector is transferred to the working fluid by a heat exchanger.
  • the working fluid in the second parallel flow path is heated with energy collected by a solar energy collection system according to the first aspect, 25
  • the heat exchanger is provided upstream of the second heating means.
  • the working fluid circuit includes a third parallel flow path, and the working fluid in the third parallel flow path is heated with energy collected by a solar energy collector according to 30 the first aspect.
  • the third parallel flow path is connected to a motive fluid inlet of the ejector pump.
  • the first and third parallel flow paths are provided with flow control valves. 35
  • the working fluid pumping means is provided upstream of the first and second parallel flow paths.
  • a second ejector pump is provided between an outlet of the first ejector pump and an inlet of the superheater means, the second ejector pump including a suction inlet in fluid communication with an outlet of the first ejector pump.
  • the second ejector pump has a motive fluid inlet which is in a parallel connection with the motive fluid inlet of the first ejector pump.
  • the energy conversion means is a turbine.
  • the second parallel flow path includes a compressor between the second heating means and the suction inlet of the first ejector means.
  • the pressure reducing means includes a thermostatic valve. . .
  • the pressure reducing means includes at least one capillary tube.
  • the pressure reducing means includes a plurality of capillary tubes arranged in parallel.
  • a power generation system substantially as herein described in respect of any one of the embodiments of the present invention as shown in any one or more of Figures 1 to 7 of the accompanying figures.
  • the invention may also be said broadly to consist in the parts, elements and features referred to or indicated in the specification of the application, individually or collectively, in any or all combinations of two or more of said parts, elements or features.
  • Figure 1 Is a schematic diagram of a power generation system according to one embodiment of the present invention.
  • Figure 2 Is a schematic diagram of a second embodiment of the power generation . system.
  • Figure 3 Is a schematic diagram of a third embodiment of the power generation system.
  • Figure 4 Is a schematic diagram of a fourth embodiment of the power generation system.
  • Figure 5 Is a schematic diagram of a fifth embodiment of the power generation system, • with the heat transfer fluid circuits removed for clarity.
  • Figure 6 Is a schematic diagram of a solar energy collection system of the present invention.
  • Figure 7 Is a schematic diagram of a power generation system according to one embodiment of the present invention with an optional compressor upstream of . the ejector pump.
  • a power generation system is generally referenced by arrow 100.
  • the power generation system 100 includes a working fluid which flows around a closed circuit 1.
  • the particular working fluid used may differ depending on the temperature range which the power generation system is intended to work within, but it is anticipated that in most embodiments the working fluid will be a refrigerant, or a similar organic compound which has a relatively low boiling point. In the embodiment shown the working fluid is R134A.
  • the circuit 1 includes an energy conversion device such as a turbine 2, a condenser 3 for condensing the working fluid flowing from the turbine 2, a subc ⁇ oler 4 for subcooling the working fluid flowing from the condenser 3, a receiver 5 for storing the sibcooled working fluid liquid from the subcooler 4, and a pump S.
  • the turbine and pump are combined into a single device, such as that described in international application No. PCT/AU2008/000506.
  • the pump 6 pumps the working fluid at a rate of around 5 kg/s when under normal operating conditions.
  • the working fluid circuit is split into two parallel streams of working fluid which flow down respective first and second flow parallel paths 7, 8.
  • the first parallel stream flows through a first heating means 9 via a ⁇ on return valve 9A. Heat is added to the. liquid working fluid by the first heating means 9, and the liquid working fluid is vapourised.
  • the second parallel working fluid stream enters a pressure reduction means 10 such as a thermostatic expansion valve (Tx valve) or one or more capillary tubes arranged in a parallel flow configuration.
  • the pressure reduction means 10 reduces the pressure of the second parallel stream below the pressure of the working fluid in the condenser 3, and below the condensing pressure, so that It becomes a vapour, and the temperature drops to below the temperature of the working fluid leaving the turbine 2.
  • the second stream of working fluid is then passed through a second heating means 11 which heats the working fluid with heat removed from the working fluid vapour as it is condensed in the condenser 3.
  • the second heating means 11 is a discrete heat exchanger.
  • the condenser 3 and the second heating means 11 are preferably primary and secondary sides of a single heat exchanger, as is shown in the figures.
  • the combined condenser/second heating means is hereinafter referred to as the recirculator heat exchanger 12.
  • the condenser and second heating means may be separate heat exchangers, with a suitable heat transfer fluid flowing between them.
  • the recirculator heat exchanger 12 may be provided with thermoelectric generation means (not shown) which generate electrical current from the temperature difference between the two working fluid streams, although this may only be viable in relatively high temperature embodiments of the invention.
  • the internal structure of the second heating means 11 is such that the flow of working fluid is not slowed to any substantial degree, as this may tend to increase the temperature and pressure of the working fluid, thereby reducing the effectiveness of the heat transfer.
  • the recirculator 12 may preferably be a tube and shell type heat exchanger.
  • Ejector pumps may also be known to those skilled in the art as “ejectors” or “injectors”.
  • the working fluid vapour from the first parallel flow path 7 enters the primary or "motive” input 15 of the ejector 14.
  • the ejector pump 14 draws the working fluid from the second parallel flow path 8 and combines it with the working fluid from the first parallel flow path 7.
  • the pressure of the combined streams of working fluid is determined by the pressure ratio of the ejector, and is intermediate the pressure of the first stream at the primary input 13.to the ejector and the pressure of the second stream at the secondary input 15. If required the second stream of working fluid may flow through a diffuser (not shown) at the outlet to the ejector 14, in order to raise its pressure.
  • Suitable ejector pump designs are known to those skilled in the art. Ejector pump designs are described in a number of standard texts, for example, Perry's Chemical Engineer's Handbook, a* edition (ISBN 0-07-142294-3).
  • the recombined working fluid stream flows from the ejector 14 to a superheater 17, where additional heat is added to ensure that the working fluid is in a superheated vapour state.
  • the superheated vapour enters the energy conversion means, typically a turbine 2, to complete the cycle.
  • An oil separator and an accumulator may be provided upstream of the turbine 2 to remove any oil or droplets of liquid working fluid from the working fluid stream entering the turbine 2, in order to avoid damage to the turbine blades. Oil accumulated in the oil separator may be used to lubricate the bearings of the turbine 2 before being pumped back into an oil separator reservoir. Refrigerant droplets accumulated in the accumulator are boiled off as vapour and pass through the turbine.
  • the ratio ' of mass flow through the second parallel flow path 8 to mass flow though the first parallel flow path 87 is typically around 2:3 , that is, around 60% of the working fluid flows through the second parallel flow path 8.
  • heat is transferred from a suitable heat source 18, for example a heat exchanger in thermal communication with the flue of an industrial boiler, to the first heating means 9 and the superheater heat exchanger 17 by a heat transfer fluid contained within a closed heat transfer fluid circuit 19.
  • a suitable heat source for example a heat exchanger in thermal communication with the flue of an industrial boiler
  • a heat transfer fluid contained within a closed heat transfer fluid circuit 19.
  • One such fluid is a mixture of DowcalTM10, manufactured by the Dow Chemical Company, and water.
  • a pump 20 circulates the heat transfer fluid around the closed heat transfer fluid circuit 19. in the embodiment shown the pump 20 circulates the heat transfer fluid at a rate of around 6.5 kg/s, in a steady state, to support a 90 kW turbine. In other embodiments the flow could be much higher, for example a steady state flow of around 13 kg/s, if a 20OkW turbine is used.
  • the relatively low heat input required from the heat source is due to the majority of the heat being returned via the recirculator, leaving
  • a variable superheater bypass 21 for the heat transfer fluid is provided around the superheater 17 and a variable first heating means bypass 22 is provided around the first heating means 9, in order to control the flow of heat into each heat exchanger, and the flow of heat into the system as a whole.
  • Variable valves (not shown) allow control of the heat transfer fluid through the bypasses.
  • the pump 20 is provided with a variable speed drive which allows its flow rate to be varied, thereby varying the heat transferred into the working fluid from the heat source. In this way heat balance in the working fluid circuit can be maintained.
  • the working fluid circuit 1 may include a variable turbine bypass 23 to allow all or a portion of the working fluid to flow around the turbine 2 if required.
  • the turbine bypass 23 may be used to protect the turbine 2 from overspsed, or from working fluid which is leaving the superheater 17 at a temperature below that which would guarantee that it is free from liquid droplets which might damage the turbine,
  • the superheater 17 may also be provided with a dryer for the working ffuid.
  • the heat source 18 heats the heat transfer fluid to around 100 0 C.
  • the heat transfer fluid flows to the superheater 17 and heats the working fluid in the superheater 17 to around 90 ⁇ C, at a pressure of around 18 bar.
  • the heat transfer fluid leaves the superheater 17 at a temperature of around 85*C and moves to the first heating means 9.
  • the heat transfer fluid heats the working fluid in the first heating means to around 75°C, at a pressure of around 22 bar.
  • the heat transfer fluid leaves the first heating means 9 at a temperature of around 65°C and returns to the heat source 18 via the pump 20.
  • the heat transfer fluid may flow directly from the heat source 18 to the first heating means 9 in parallel with the heat transfer fluid flowing to the superheater 17.
  • the amount of heat transferred from the heat source 18 to the working fluid is directly proportional to the mass flow rate of the heat transfer fluid (in this case DowcalTM 10).
  • the mass flow rate can be controlled by using the variable speed drive to control the speed of the pump 20 in response to control inputs from various parts of the cycle, such as the turbine output or the superheat content of the working fluid at the input to the turbine.
  • the working fluid leaves the turbine 2 at a temperature of around 39°C and a pressure of around 10 bar, and flows to the condenser side of the recirculator heat exchanger 12.
  • the condensed working fluid leaves the recirculator heat exchanger 12 at a temperature of around 38°C and moves to the subcooler 4, where it is cooled to around 30 0 C, and moves to the receiver 5 and then the pump 6.
  • the pump 6 pumps the working fluid through the first parallel flow path 7 to the first heating means 9 at a pressure of around 22 bar.
  • the working fluid in the second parallel flow path 8 leaves the pump at around 22 bar and flows to the pressure reduction means 10.
  • the pressure reduction means 10 reduces the pressure to around 2 bar, and the temperature to around -
  • the working fluid in the second parallel flow path 8 Is then heated by the recirculator heat exchanger 12 to around 45 D C, and flows to the ejector pump 14, where it is recombi ⁇ ed with the working fluid from the first parallel flow path 7, as is described above.
  • a control means (not shown) monitors the temperature of the working fluid exiting the superheater 17 and modulates the flow of heat transfer fluid through the bypasses 21 , 22, and the overall flow rate of heat transfer fluid pumped by the pump 20, in order to ensure that the working fluid leaving the superheater 17 is at the correct temperature and pressure,
  • control means closes the bypasses 21, 22 and opens bypass 23 around the turbine.
  • the control system closes the turbine bypass 23 and increases the flow through the bypass 22, thereby reducing the heat entering the heat exchanger 9 in the first parallel stream 7 so as to maintain heat balance, with the majority of the heat rejected from the energy conversion means 2 being returned to the ejector suction input 13 via the recirculator/co ⁇ denser means 12.
  • the net effect of this is an increase in conversion efficiency, as less heat is now required from the heat source 18 to maintain the energy conversion means 2 at a given power output under steady state conditions.
  • the pre-heater bypass 22 is used to reduce the pre-heater heat input once steady state conditions have been met to maintain thermal balance, given that the majority of the turbine heat rejected is being re-circulated.
  • the second parallel flow path 8 may lead from upstream of the pump 6, for example from between the receiver 5 and pump 6 rather than downstream of the pump 6. Whether this is desirable or not depends on the efficiency of the ejector pump 14, and the pressure created at the- suction fluid inlet 13.
  • a second embodiment 101 of the power generation system includes' means for capturing solar energy and adding it to the working fluid.
  • the solar energy capturing means may include one or more solar collectors 24 which heat a suitable heat transferfluid, for example a water/DowcalTM mixture, or a suitable low temperature refrigerant such as R410A, with solar energy.
  • the heat transfer ffuid is circulated around a second closed heat transfer fluid circuit 25 by a suitable pump 26. If refrigerant is used, then the circuit 25 may be a heat pump circuit including a receiver, thermostatic expansion valve, and other associated components (not shown).
  • the solar energy capturing means may include the solar energy collection system described below with reference to Figure 6.
  • the solar energy heat exchanger 27 is preferably provided upstream of the recirculator heat exchanger 12, and downstream of the pressure reducing means 10, although other positions of the solar energy heat exchanger 27 in the working fluid circuit 1 may also be suitable.
  • a matrix of blackened copper or aluminium tubing may be used as a solar collector 24, although many suitable alternative forms of solar collector will be apparent to those skilled in the art.
  • any suitable number of solar collectors 24 may be used.
  • a number of second heat transfer fluid circuits 25 may be provided, in series or in parallel as required, to add additional heat to the working fluid entering the recirculator heat exchanger 12.
  • a third embodiment is generally referenced 102.
  • the working fluid circuit 1 includes a third parallel flow path 28 which takes working fluid from the receiver 5.
  • a pump 29 then pumps the working fluid through a second pressure reducing means 30, which is similar to the pressure reducing means 10 in the second parallel flow path.
  • the second pressure reducing means 30 reduces the temperature and pressure of the working fluid before it flows to a solar energy collector 24 and absorbs solar energy.
  • the working fluid leaving the solar collector flows through a solar energy heat exchanger 27 and heats the working fluid in the second parallel flow path 8.
  • the working fluid in the third parallel flow path 28 then returns to the receiver 5, via the subcooler 4. Any suitable number of additional parallel flow paths containing solar collectors may be used.
  • the second and third parallel flow paths 8, 28 take liquid, working fluid from upstream of the pump 6,
  • the ejector pump 13 is provided with 1wo suction inlets 13, 13A, as is described further below.
  • Working fluid in the third parallel flow path 28 flows from the receiver to the solar energy heat exchanger 27, and from there to the second suction inlet 13A of the ejector pump 14.
  • the two suction inlets 13, 13A may feed into the same, chamber.
  • the ejector pump 14 may be a two stage device, with the working fluid from the motive fluid inlet 15 combining with the working fluid from the third parallel flow path 2B in a first stage. The outlet of the first stage is then used as the fluid for the suction inlet of the second stage.
  • the two stages may be integrated as a single two-stage unit, or may be separated into two discrete ejector pumps arranged in series, with the outlet from the first ejector pump being connected to the secondary or suction inlet of the second ejector pump.
  • the pressure of the working fluid entering the superheater 17 may be increased by providing a further ejector pump 31 downstream of the first ejector pump 14.
  • the further ejector pump 31 has a motive inlet 32 which receives working fluid directly from the vapouriser 9, in parallel with the motive fluid inlet 16 of the first ejector.
  • the working fluid from the outlet of the first ejector pump 14 flows to the suction inlet 33 of the further ejector pump 31. In this way the pressure of the working fluid entering the superheater 17 and turbine 2 can be increased.
  • a solar energy collection system 200 includes a solar heat collector 34.
  • the solar heat collector, 34 comprises a plurality of extruded aluminium strips.
  • each strip is 53mm wide, 13mm thick and 5,900mm long with four 10.5mm bores placed side by side and running the entire length of the. extrusion.
  • the wall thickness between the bores is around 1.5mm.
  • extruded aluminium flat sheet strips are butted together side by side and mounted in a flat frame, providing around 500 kW heat capacity.
  • the strips are preferably anodised black.
  • Plastic snap fit external connectors and polyurethane tubing form a zig zag parallel path for the heat transfer fluid.
  • the heat collectors are attached.t ⁇ double side insulating foam tape which acts as an insulator thus preventing heat from escaping as well as securing the aluminium strips to the host structure.
  • Thermoelectric generators are optionally attached to the aluminium or copper surface on a thin film of thermally conducting grease and secured by a suitable thin strip clamping arrangement.
  • thermoelectric generators can be used to surface mount the thermoelectric generators to the aluminium extrusions.
  • thermoelectric generators are then connected electrically in series and thermally in parallel in suitable groups to suite the current and voltage requirements of the particular application.
  • the heat is removed by the flow of heat transfer fluid through the zig zag path.
  • the heat transfer fluid for example DowcalTM 10 is pumped from a heat transfer fluid collection means, usually a tank 35, to the solar heat collector 34 by a pump 36, and returned to the tank 35 from the solar heat collector 34.
  • the flow rate of the pump 36 may be controlled by a control system to ensure that the temperature of the heat transfer fluid in the tank 35 is kept at a required temperature, or that it is kept at as high a temperature as possible.
  • a further pump 37 pumps the heat transfer fluid from the tank 35 to the solar energy heat exchanger 27.
  • the control means may vary the speed of the.pump 37 in order to control the transfer of heat into the working fluid through the solar energy heat exchanger 27.
  • additional parallel flow paths may be provided, each with an additional heat exchanger, in order to allow heat from other sources to be added to the system, for example from heat rejected from a condenser of a chiller or air conditioning plant.
  • the output pressure of the ejector 14 may be increased by providing a compressor 38 (and accumulator if required) between the second heating means 11 and the suction fluid inlet 13,
  • Figure 7 shows one example of this arrangement, with the compressor 38 shown, but the accumulator not shown.
  • a further compressor (not shown) may be provided in parallel with the superheater 17 and turbine 2, in order to assist in establishing a flow around the circuit. This may be particularly important where the ejector 14 requires supersonic internal flows to be established in order to operate properly.

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Abstract

L'invention porte sur un système de génération d'énergie qui comprend un circuit fermé à fluide de travail (1) possédant un surchauffeur (17), une turbine (2), un condenseur (3), un sous-refroidisseur (4), un récepteur (5) et une pompe (6). Le fluide de travail est séparé en des premier et second courants parallèles. Le premier courant parallèle s'écoule à travers un premier trajet d'écoulement parallèle (7) qui comprend un premier moyen de chauffage (9) apte à vaporiser le fluide de travail. Le second trajet d'écoulement parallèle (8) comprend des seconds moyens de chauffage (11) aptes à chauffer le fluide de travail avec la chaleur retirée du fluide de travail dans le condenseur (3), et des moyens de détente (10) en amont des seconds moyens de chauffage (11). Une pompe d'éjection (14) recombine les premier et second courants de fluide de travail avant que le fluide de travail n'entre dans le moyen de surchauffe (18). L'invention porte également sur un système de collecte d'énergie solaire. L'énergie solaire est transférée au fluide de travail par l'intermédiaire d'un échangeur de chaleur (27).
PCT/AU2009/001050 2008-08-18 2009-08-18 Système de collecte d'énergie solaire et système de génération d'énergie comprenant un système de collecte d'énergie solaire WO2010019990A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
NZ57063608 2008-08-18
NZ570636 2008-08-18
NZ572136 2008-10-17
NZ57213608 2008-10-17

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WO2010019990A1 true WO2010019990A1 (fr) 2010-02-25

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010116162A2 (fr) 2009-04-09 2010-10-14 Carding Specialists (Canada) Limited Transfert d'énergie solaire et appareil de stockage
US20110277981A1 (en) * 2010-05-17 2011-11-17 General Electric Company Gas treatment and solar thermal collection system
WO2012066314A1 (fr) 2010-11-19 2012-05-24 Carding Specialists (Canada) Ltd Appareil de stockage et de transfert d'énergie
JP2014047632A (ja) * 2012-08-29 2014-03-17 Kobe Steel Ltd 発電装置及び発電装置の制御方法
KR101482876B1 (ko) 2012-08-29 2015-01-14 가부시키가이샤 고베 세이코쇼 발전 장치 및 그 제어 방법
CN109519241A (zh) * 2017-09-19 2019-03-26 株式会社东芝 热发电系统

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GB2064098A (en) * 1979-11-21 1981-06-10 Satchwell Controls Ltd Heating systems utilizing a heat transfer fluid
GB2097116A (en) * 1981-03-25 1982-10-27 Anderson John Improvements in or relating to control apparatuses for solar heating systems
WO1982003677A1 (fr) * 1981-04-13 1982-10-28 Corp Altas Systeme de chauffage solaire d'eau d'un reservoir a double paroi a drain de retour hermetique
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WO2010116162A2 (fr) 2009-04-09 2010-10-14 Carding Specialists (Canada) Limited Transfert d'énergie solaire et appareil de stockage
US20110277981A1 (en) * 2010-05-17 2011-11-17 General Electric Company Gas treatment and solar thermal collection system
US8641812B2 (en) * 2010-05-17 2014-02-04 General Electric Company Gas treatment and solar thermal collection system
WO2012066314A1 (fr) 2010-11-19 2012-05-24 Carding Specialists (Canada) Ltd Appareil de stockage et de transfert d'énergie
JP2014047632A (ja) * 2012-08-29 2014-03-17 Kobe Steel Ltd 発電装置及び発電装置の制御方法
KR101428418B1 (ko) 2012-08-29 2014-08-07 가부시키가이샤 고베 세이코쇼 발전 장치 및 발전 장치의 제어 방법
KR101482876B1 (ko) 2012-08-29 2015-01-14 가부시키가이샤 고베 세이코쇼 발전 장치 및 그 제어 방법
CN109519241A (zh) * 2017-09-19 2019-03-26 株式会社东芝 热发电系统
CN109519241B (zh) * 2017-09-19 2022-03-22 株式会社东芝 热发电系统

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