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5 EP 1 930 587 A2 6 temperature recuperators 40 and 42 function as heat ex- changers that recapture heat and send the heat back into supercritical carbon dioxide system 14 to improve the efficiency of supercritical carbon dioxide system 14. Thus, heat is added to the Brayton cycle working fluid in 5 high and low temperature recuperators 40 and 42, as well as in heat exchanger 26. [0018] From low temperature recuperator 42, the Bray- ton cycle working fluid is sent through third intermediate temperature line 60 to first valve 72. At first valve 72, a 10 portion of the Brayton cycle working fluid is passed through precooler line 62 to precooler 44 where the tem- perature of the Brayton cycle working fluid is reduced to approximately 90 °F (32°C) before the Brayton cycle working fluid is transported through main compressor line 15 64 to main compressor 46. Precooler 44 may reject the heat into water, which is sent to a cooling tower to release the heat to the atmosphere. Alternatively, the heat rejec- tion may also be accomplished by directly air cooling the heat. The cooling is required to lower the temperature of 20 the Brayton cycle working fluid to the required low starting temperature of closed supercritical carbon dioxide sys- tem 14. At main compressor 46, the Brayton cycle work- ing fluid is pressurized to a pressure of approximately 2900 psi (20.00 MPa) and a temperature of approximate- 25 ly 142 °F (61 °C). By operating main compressor 46 with inlet conditions immediately above the carbon dioxide critical point, the work required is significantly reduced. The Brayton cycle working fluid then flows through low temperature recuperator inlet line 66 back to low temper- ature recuperator 42 and is heated to a temperature of approximately 317 °F (158°C). The Brayton cycle work- ing fluid then leaves low temperature recuperator 42 and enters second valve 74 through low temperature recu- perator outlet line 58. 35 [0019] In parallel, the second portion of the Brayton cycle working fluid is transported from first valve 72 through recompression compressor inlet line 68 to rec- ompression compressor 48 where it is pressurized to ap- proximately 2899 psi (19.99 MPa) at a temperature of 40 approximately 317 °F (158°C). The Brayton cycle work- ing fluid from recompression compressor 48 subsequent- ly rejoins the main compressor 46 discharge through rec- ompression compressor outlet line 70 into second valve 74. The combined Brayton cycle working fluid then leaves 45 second valve 74 through high temperature recuperator inlet 76 and enters high temperature recuperator 40, where it is heated to approximately 746 °F (397°C). From high temperature recuperator 40, the Brayton cycle work- ing fluid is passed through high temperature recuperator 50 outlet line 54 and enters heat exchanger 26 at a temper- ature of approximately 746 °F (397°C) and a pressure of approximately 2895 psi (19.96 MPa). [0020] FIG. 2 shows a diagram of a method of using the heat transfer fluid from solar heating system 12 to 55 provide thermal energy to supercritical carbon dioxide system 14. As previously mentioned, the molten salt is initially stored in cold storage tank 18, Box 100. When needed, the molten salt is pumped to solar receiver 20 (Box 102) and heated to a temperature of at least ap- proximately 1065 °F (574°C), Box 104. As shown in Box 106, the heated molten salt is then sent to hot storage tank 24 until it is needed by supercritical carbon dioxide system 14. The heated molten salt is pumped to super- critical carbon dioxide system 14, where the thermal en- ergy from the molten salt is transferred to the supercritical carbon dioxide to power supercritical carbon dioxide sys- tem 14, Box 108. [0021] The turbine system uses a molten salt solar heating system to provide thermal energy to a supercrit- ical carbon dioxide system. The supercritical carbon di- oxide system requires peak carbon dioxide temperatures of approximately 1022 °F (550°C). The solar heating sys- tem passes molten salt as a heat transfer fluid through the solar heating system to transport the thermal energy required to power to supercritical carbon dioxide system. In an exemplary embodiment, the solar heating system is a solar power tower system that heats the molten salt to a temperature of approximately 1065 °F (574°C). [0022] Although the present invention has been de- scribed with reference to preferred embodiments, work- ers skilled in the art will recognize that changes may be made in form and detail without departing from the scope of the invention. Claims 1. A turbine system (10) comprising: a supercritical carbon dioxide turbine (14); and a solar heating system (12) having a molten salt heat transfer fluid for providing thermal energy to the supercritical carbon dioxide turbine (14). 2. The turbine system of claim 1, wherein the super- critical carbon dioxide turbine (36) operates at a tem- perature of at least about 1022 degrees Fahrenheit (550°C). 3. The turbine system of claim 1 or 2, wherein the mol- ten salt heat transfer fluid comprises between about 50% sodium nitrate and about 70% sodium nitrate and between about 30% potassium nitrate and about 50% potassium nitrate by weight. 4. The turbine system of any preceding claim, wherein the solar heating system (12) heats the molten salt heat transfer fluid to a temperature of at least about 1065 degrees Fahrenheit (574°C). 5. The turbine system of any preceding claim, wherein the supercritical carbon dioxide turbine (14) compris- es a supercritical carbon dioxide Brayton power con- version cycle. 30 4PDF Image | EP 1 930 587 A2 EUROPEAN PATENT APPLICATION
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