• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
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  • 引用文献
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  • 优先权
    • 专利摘要:
    The invention called thermal plant with double effect machine, thermal accumulators, forced convection and thermal feed reinforced with a reverse brayton cycle and operating procedure, aims at the conversion of thermal energy to mechanical and/or electrical energy via mechanical energy and consists of in a thermal cycle, implemented on a double-effect alternative thermal machine that operates with helium as thermal fluid of work and interchangeable thermal accumulators between two sources of high and low temperature (the hot source that gives heat to the cycle and the cold source that absorbs heat of the cycle). (Machine-translation by Google Translate, not legally binding)
    公开号:ES2696950A1
    申请号:ES201700667
    申请日:2017-07-18
    公开日:2019-01-18
    发明作者:Garcia Ramón Ferreiro；Carril José Carbia
    申请人:Carbia Carril Jose；Ferreiro Garcia Ramon；
    IPC主号:
    专利说明:

    [0001]
    [0002] Thermal plant with double effect machine, thermal accumulators, forced convection and thermal feed reinforced with a reverse brayton cycle and operating procedure.
    [0003] TECHNICAL FIELD OF THE INVENTION
    [0004]
    [0005] The present invention pertains to the technical field of the conversion of thermal energy to mechanical and / or electrical energy via mechanical energy by means of a thermal cycle that performs mechanical work by adding and extracting heat from the working thermal fluid.
    [0006]
    [0007] Objective of the invention
    [0008]
    [0009] The invention denominated THERMAL PLANT WITH DOUBLE-EFFECT MACHINE, THERMAL ACCUMULATORS, FORCED CONVECTION AND REINFORCED THERMAL POWER WITH AN INVERSE BRAYTON CYCLE AND OPERATING PROCEDURE, has the objective of converting thermal energy to mechanical and / or electrical energy via mechanical energy by means of a double-acting alternative machine, which operates with helium as a working fluid, between two heat sources (the high-temperature or hot thermal source that yields heat to the working thermal fluid and the cold source that absorbs heat from the working thermal fluid) , with a thermal cycle that includes two closed processes that perform mechanical work: adiabatic expansion and adiabatic compression.
    [0010]
    [0011] BACKGROUND OF THE INVENTION
    [0012]
    [0013] The thermal machines known to date have in common the limitation of the thermal efficiency imposed by the Carnot factor. The machine object of the invention is not limited by the Carnot factor as a consequence of the thermal cycle proposed in the invention. The most similar antecedent is based on the National Patent with application number 201700181 called "alternative double-effect regenerative thermal machine, of closed and open processes and its operating procedure".
    [0014]
    [0015] Consequently, in the current state of technology, there are no known double-effect alternative thermal machines with similar cycle or similar to the characteristics of this invention.
    [0016]
    [0017] Description of the invention
    [0018]
    [0019] The invention denominated THERMAL PLANT WITH DOUBLE-EFFECT MACHINE, THERMAL ACCUMULATORS, FORCED CONVECTION AND REINFORCED THERMAL POWER SUPPLY WITH AN INVERSE BRAYTON CYCLE AND OPERATING PROCEDURE, consists of an unconventional thermal cycle implemented by means of an alternative double-effect thermal machine, which operates with helium as a working thermal fluid. This alternative double-effect thermal machine uses thermal energy from two thermal sources: hot source and cold source, where the hot source or high temperature source converts thermal energy to work in the thermo-actuator cylinder by adiabatic expansion according to a closed process , while the cold source or low temperature source converts thermal energy to mechanical work in the thermo-actuator cylinder by adiabatic compression (reduction of the volume occupied by the thermal fluid of work due to the effect of cooling), and where both thermal sources are constituted by heat exchangers (heater and cooler), and where the hot source consists of at least one heat exchanger, which transfers heat from a heat transfer fluid (steam, water, thermal oil, helium or hydrogen) to the working thermal fluid (helium), which drives the thermo-actuator cylinder, and where the heat to heat the thermal fluid of heat transfer comes from any available thermal source including waste heat such as heat of refrigeration of machines and thermal engines, compressors, solar, geothermal, thermo-oceanic, nuclear waste, fossil-based thermal energy and in general high, average waste heat and even of low temperature or from a reverse Brayton cycle, and where the cold source or heat sink consists of a heat exchanger, which transfers heat from the thermal working fluid (helium) which is responsible for operating the thermo actuator cylinder by adiabatic compression according to a closed thermal process of the cold thermal fluid of heat transfer (cold water, helium or hydrogen), which in turn is cooled by a cooling fluid such as air or water at room temperature, or the evacuation of a turboexpansor at sub-ambient temperature, as well as a conventional cooling tower by air or water or from a Brayton inve cycle rso
    [0020] Description of the figures
    [0021] In this section, the components that make up the power unit of the THERMAL PLANT WITH DOUBLE-EFFECT MACHINE, THERMAL ACCUMULATORS, FORCED CONVECTION AND REINFORCED THERMAL POWER SUPPLY WITH AN INVERSE BRAYTON CYCLE AND OPERATING PROCEDURE, are described in an illustrative and non-limiting manner. facilitate the understanding of the invention, where reference is made to the following figures:
    [0022] Figure 1 shows the structure of a power unit of the alternative double-effect thermal machine whose components include:
    [0023] - Double-acting thermo-actuator cylinder (1)
    [0024] - left chamber (2) of the double acting thermo-actuator cylinder (1)
    [0025] - Right chamber (3) of the double acting thermo-actuator cylinder (1)
    [0026] - working thermal fluid cooler (4)
    [0027] - working thermal fluid heater (5)
    [0028] - forced convection blower (6) of cold working thermal fluid
    [0029] - forced convection blower (7) of hot working thermal fluid
    [0030] - Thermal thermal fluid storage tank (20)
    [0031] - Thermal thermal fluid storage tank (30)
    [0032] - Thermal thermal fluid storage tank (40)
    [0033] - Thermal thermal fluid storage tank (50)
    [0034] - valve (21) of two positions and three ways (2/3) of communication of the coolant of the thermal fluid of work (4) and the heater of the thermal fluid of work (5) and the thermal accumulator of thermal fluid of work (20) )
    [0035] - communication valve 2/3 (31) of the working thermal fluid cooler (4) and the working thermal fluid heater (5) and the thermal thermal fluid storage tank (30) - valve 2/3 (41) for communication of the working thermal fluid cooler (4) and the working thermal fluid heater (5) and the thermal thermal fluid storage tank (40)
    [0036] - communication valve 2/3 (51) of the working thermal fluid cooler (4) and the working thermal fluid heater (5) and the thermal thermal fluid storage tank (50)
    [0037] - valve 2/3 (22) communicating the thermal thermal fluid storage tank (20) and the suction pipes of the forced convection blower (6) of the cold working thermal fluid and the forced convection blower (7) ) of hot working thermal fluid
    [0038] - 2/3 valve (32) communicating thermal work fluid thermal accumulator (30) and suction ducts of forced convection blower (6) of cold working thermal fluid and forced convection blower (7) ) of hot working thermal fluid
    [0039] - valve 2/3 (42) communicating the thermal thermal fluid accumulator (40) and the suction lines of the forced convection blower (6) of the cold working thermal fluid and the forced convection blower (7) ) of hot working thermal fluid
    [0040] - valve 2/3 (52) communicating the thermal thermal fluid storage tank (50) and the suction pipes of the forced convection blower (6) of the cold working thermal fluid and the forced convection blower (7) ) of hot working thermal fluid
    [0041] - 2/3 valve (23) that connects the thermal accumulators (20) and (30) with the working fluid communication valve 2/3 (24) with both sides of the cylinder
    [0042] - 2/3 valve (45) that connects the thermal accumulators (40) and (50) with the working fluid communication valve 2/3 (44) with both sides of the cylinder
    [0043] - valve 2/3 (24) that communicates the 2/3 valve (23) and the chambers (2) and (3) of the double acting thermo actuator cylinder (1)
    [0044] - valve 2/3 (44) that communicates the 2/3 valve (45) and the chambers (2) and (3) of the double acting thermo actuator cylinder (1)
    [0045] Figure 2 shows the structure of two power units connected in cascade with respect to the supply of heat, and belonging to the alternative double-acting poly-cylindrical thermal machine equipped with the system of addition and extraction of heat, whose components include:
    [0046] - supply conduit (70) of the hot heat transfer fluid to the heater (5) of the first power unit, where it passes to the heater (5) of the second power unit, and exits through the conduit (71)
    [0047] - Exit line (71) of the hot heat transfer fluid of the heater (5)
    [0048] - supply conduit (72) of the cold heat transfer fluid to the cooler (4) of the first power unit and to the cooler (4) of the second power unit.
    [0049] Figure 3 shows the complementary feeding system by means of the Regenerative Reverse Brayton cycle designed to complement the external sources of heat and cold, whose components include:
    [0050] - Electric starter motor (110)
    [0051] - Inverse Brayton cycle compressor (111)
    [0052] - turbo-expander of the Brayton cycle (112)
    [0053] - heat regenerator (113)
    [0054] - discharge duct (114) from the compressor (111) to the high temperature heat exchanger (130)
    [0055] - return duct (115) of heat exchanger (130) high temperature
    [0056] - return duct (116) of the low temperature heat exchanger (131) to regenerator (113) and the compressor (111)
    [0057] - evacuation conduit (117) from the turbo-expander of the reverse Brayton cycle (112) to the low temperature heat exchanger (131)
    [0058] - Heat exchanger (130) of heat supply of the reverse Brayton cycle
    [0059] - Heat exchanger (131) of cold supply of the reverse Brayton cycle
    [0060] - Heat exchanger (132) of external heat supply through the heat supply duct (70) and return by (71)
    [0061] - Heat exchanger (133) of external cold supply through the cold supply conduit (72) and return through (73)
    [0062] - hot fluid circulation pump of high temperature thermal source (134)
    [0063] - cold fluid circulation pump of low temperature thermal source (135)
    [0064] Detailed description of the invention
    [0065] The invention called THERMAL PLANT WITH DOUBLE-EFFECT MACHINE, THERMAL ACCUMULATORS, FORCED CONVECTION AND REINFORCED THERMAL POWER WITH AN INVERSE BRAYTON CYCLE AND OPERATING PROCEDURE, is characterized by performing the conversion of thermal energy to mechanical and / or electrical energy via mechanical energy, by means of an innovative thermal cycle implemented by means of an alternative double-effect poly-cylindrical thermal machine, which operates with helium as a working thermal fluid, which is equipped with two thermal bulbs, where the high-temperature focus is a thermal source intended for heat the thermal fluid of work and the focus of low temperature consists of a heat sink, which is intended to extract heat from the thermal fluid of work, and where both thermal foci (high and low temperature) are constituted by heat exchangers , (5) and (4) respectively that operate by forced thermal convection by means of Oplantes.
    [0066] The heat transfer thermal fluids needed to heat and cool the thermal working fluid are conventional fluids used for this purpose in thermal transfer processes such as water or thermal oil among others known, and where the heat necessary to heat the thermal fluid heat transfer comes from any available heat source such as waste heat from the cooling of various machines and compressors, thermal energy of fossil origin, solar thermal, geothermal, and in general high, medium and even low temperature waste heat or from an inverse Brayton cycle, and where the heat sink (4) transfers heat from a thermal working fluid (helium) cycle thermally implemented by the thermo-actuator cylinder (1), to the thermal fluid of heat transfer, by means of a refrigerant that can be air or water at room temperature, or a steam compression refrigeration machine, or the evacuation of a turbo -expander at sub-ambient temperature, or a conventional cooling tower by air or water, or from an inverse Brayton cycle, and whose components for each power unit according to figure 1 include:
    [0067] - Double-acting thermo-actuator cylinder (1)
    [0068] - left chamber (2) of the double acting thermo-actuator cylinder (1)
    [0069] - Right chamber (3) of the double acting thermo-actuator cylinder (1)
    [0070] - working thermal fluid cooler (4)
    [0071] - working thermal fluid heater (5)
    [0072] - forced convection blower (6) of cold working thermal fluid
    [0073] - forced convection blower (7) of hot working thermal fluid
    [0074] - Thermal thermal fluid storage tank (20)
    [0075] - Thermal thermal fluid storage tank (30)
    [0076] - Thermal thermal fluid storage tank (40)
    [0077] - Thermal thermal fluid storage tank (50)
    [0078] - valve (21) of two positions and three ways (2/3) of communication of the coolant of the thermal fluid of work (4) and the heater of the thermal fluid of work (5) and the thermal accumulator of thermal fluid of work (20) )
    [0079] - communication valve 2/3 (31) of the working thermal fluid cooler (4) and the working thermal fluid heater (5) and the thermal working thermal fluid accumulator (30) - valve 2/3 (41) ) of communication of the coolant of the thermal fluid of work (4) and the heater of the thermal fluid of work (5) and the thermal accumulator of thermal fluid of work (40) - valve 2/3 (51) of communication of the cooler of the fluid working thermal (4) and the heater of the thermal fluid of work (5) and the thermal accumulator of thermal fluid of work (50) - valve 2/3 (22) that communicates the thermal accumulator of thermal fluid of work (20) and the suction ducts of the forced convection blower (6) of the cold working thermal fluid and the forced convection blower (7) of the hot working thermal fluid
    [0080] - 2/3 valve (32) communicating thermal work fluid thermal accumulator (30) and suction ducts of forced convection blower (6) of cold working thermal fluid and forced convection blower (7) ) of hot working thermal fluid
    [0081] - valve 2/3 (42) communicating the thermal thermal fluid accumulator (40) and the suction lines of the forced convection blower (6) of the cold working thermal fluid and the forced convection blower (7) ) of hot working thermal fluid
    [0082] - valve 2/3 (52) communicating the thermal thermal fluid storage tank (50) and the suction pipes of the forced convection blower (6) of the cold working thermal fluid and the forced convection blower (7) ) of hot working thermal fluid
    [0083] - 2/3 valve (23) that connects the thermal accumulators (20) and (30) with the working fluid communication valve 2/3 (24) with both sides of the cylinder
    [0084] - 2/3 valve (45) that connects the thermal accumulators (40) and (50) with the working fluid communication valve 2/3 (44) with both sides of the cylinder
    [0085] - valve 2/3 (24) that communicates the 2/3 valve (23) and the chambers (2) and (3) of the double acting thermo actuator cylinder (1)
    [0086] - valve 2/3 (44) that communicates the 2/3 valve (45) and the chambers (2) and (3) of the double acting thermo actuator cylinder (1)
    [0087] The utilization of the residual heat evacuated by the first power unit is used to feed in cascade the second power unit as shown in figure 2 and the others if they exist, so that the heat transfer fluid feeds the first unit of power by means of the conduit (70), where when leaving the exchanger (5) it passes to the second power unit by feeding the heat exchanger (5) of the second power unit, to be evacuated by the conduit (71) in if there is not enough thermal energy to supply the next power unit, if any. The heat transfer fluid of the sump feeds in parallel to each heat exchanger (4) of the respective power units. The components of the two power units connected in parallel are shown in Figure 2, including in addition to the components cited in Figure 1, the following components:
    [0088] - supply conduit (70) of the hot heat transfer fluid to the heater (5) of the first power unit, where it passes to the heater (5) of the second power unit, and exits through the conduit (71)
    [0089] - Exit line (71) of the hot heat transfer fluid of the heater (5)
    [0090] - supply conduit (72) of the cold heat transfer fluid to the cooler (4) of the first power unit and to the cooler (4) of the second power unit.
    [0091] The operating procedure of each power unit of the THERMAL PLANT WITH DOUBLE EFFECT MACHINE, THERMAL ACCUMULATORS, FORCED CONVECTION AND REINFORCED THERMAL POWER SUPPLY WITH AN INVERSE BRAYTON CYCLE AND OPERATING PROCEDURE equipped with interchangeable thermal accumulators (20), (30), (40) and (50), the cooler (4), the heater (5), the forced convection blower (6) of the cold working fluid and the forced convection blower (7) of hot working fluid, is such , starting from an initial situation with the piston located in the left dead center (PMI), the thermal cycle formed by four phases carried out during the course of two revolutions begins as indicated:
    [0092] During phase 1, the plunger moves from left to right by virtue of the state of the following components:
    [0093] The thermal accumulator (20) is in the process of adiabatic expansion, valves 2/3 (21) and (22) closed, the valve (23) of the thermal accumulator (20) open to give way to the accumulator fluid (20) and closed for the accumulator (30), and the valve (24) to the chamber (2) of the thermo actuator cylinder (1) open and closed towards the chamber (3) of the thermo actuator cylinder (1).
    [0094]
    [0095] The thermal accumulator (30) is in the heating process, valves 2/3 (31) and (32) open, giving way to the fluid from and to the heater (5).
    [0096]
    [0097] The thermal accumulator (40) is in the process of adiabatic compression, the valves 2/3 (41) and (42) closed, the valve (45) of the open thermal accumulator outlet, to put the thermal accumulator (40) in communication. ) and closed for the thermal accumulator (50) and the valve (44) to the chamber (3) of the thermo actuator cylinder (1) open, and closed towards the chamber (2) of the thermo actuator cylinder (1).
    [0098]
    [0099] The thermal accumulator (50) is in the cooling process, the 2/3 (51) and (52) valves open from and to the heat exchanger cooler (4) and closed from and to the heat exchanger heater (5). ).
    [0100]
    [0101] During phase 2, the plunger moves from right to left by virtue of the state of the following components:
    [0102]
    [0103] The thermal accumulator (20) is in the cooling process, the 2/3 (21) and (22) valves open from and to the heat exchanger cooler (4) and closed from and to the heat exchanger heater (5). ).
    [0104]
    [0105] The thermal accumulator (30) is in the process of adiabatic compression, valves 2/3 (31) and (32) closed, the valve (23) of the thermal accumulator (30) open, and the valve (24) to the chamber (2) of the thermo-actuator cylinder (1) open.
    [0106]
    [0107] The thermal accumulator (40) is in the heating process, valves 2/3 (41) and (42) open from and to the heat exchanger heater (5) and closed from and to the cooler heat exchanger (4). ).
    [0108]
    [0109] The thermal accumulator (50) is in the process of adiabatic expansion, valves 2/3 (51) and (52) closed, valve (45) for the outlet of the thermal accumulator (50) open, and the valve (44) to the chamber (3) of the thermo-actuator cylinder (1) open.
    [0110]
    [0111] During phase 3, the plunger moves from left to right by virtue of the state of the following components:
    [0112]
    [0113] The thermal accumulator (20) is in the process of adiabatic compression, valves 2/3 (21) and (22) closed and the valve (23) of the thermal accumulator (20) open, and the valve (24) to the chamber (3) of the thermo-actuator cylinder (1) open.
    [0114]
    [0115] The thermal accumulator (30) is in the cooling process, the 2/3 (31) and (32) valves open from and to the cooling heat exchanger (4) and closed from and to the heat exchanger heater (5). ).
    [0116]
    [0117] The thermal accumulator (40) is in the adiabatic expansion process, the valves 2/3 (41) and (42) closed, the valves (45) of the open thermal accumulator outlet, and the valve (44) to the chamber (2) of the thermo-actuator cylinder (1) open.
    [0118]
    [0119] The thermal accumulator (50) is in the heating process, the valves 2/3 (51) and (52) open from and to the heat exchanger heater (5) and closed from and to the cooler heat exchanger (4). ).
    [0120] During phase 4, the plunger moves from right to left by virtue of the state of the following components:
    [0121] The thermal accumulator (20) is in the heating process, valves 2/3 (21) and (22) open from and to the heat exchanger heater (5) and closed from and to the cooler heat exchanger (4). ).
    [0122] The thermal accumulator (30) is in the adiabatic expansion process, the valves 2/3 (31) and (32) closed, the valve (23) for the outlet of the thermal accumulator (30) open, and the valve (24) to the chamber (3) of the thermo-actuator cylinder (1) open.
    [0123] The thermal accumulator (40) is in the cooling process, the 2/3 (41) and (42) valves open from and to the heat exchanger cooler (4) and closed from and to the heat exchanger heater (5). ).
    [0124] The thermal accumulator (50) is in the process of adiabatic compression, valves 2/3 (51) and (52) closed, the valve (45) of the thermal accumulator (50) open, and the valve (44) to the chamber (2) of the thermo-actuator cylinder (1) open. This thermal cycle is repeated for each unit of power indefinitely.
    [0125] To increase the thermal efficiency of the plant, it is proposed to reinforce or complement the external energy supply from the inside of the plant with a reverse Brayton cycle coupled to the plant, as shown in figure 3, which provides the two thermal foci of high and low temperature capable of supplementing the contribution of external energy, so that the contribution of thermal energy of high and low temperature responsible for feeding both the hot bulb and the cold bulb of each unit of available power, is performed simultaneously from the outside of the plant and from inside the plant, where the supply of high-temperature or hot energy from the outside of the plant includes waste heat such as heat from refrigeration of machines and thermal engines, compressors, solar, geothermal, thermo-oceanic, residual nuclear, thermal energy of fossil origin and in general high, medium and even low temperature residual heat, The cold energy supply from the outside of the plant includes any heat transfer fluid at room temperature such as air or water at room temperature, as well as any refrigerant for industrial use. On the other hand, the supply of hot and cold energy from inside the plant comes from an inverse Brayton cycle that forms part of the structure of the plant object of the invention.
    [0126] The energy supply system, which comprises the external and internal supply formed by a reverse Brayton cycle, includes at least the following components:
    [0127] - Electric starter motor (110)
    [0128] - Inverse Brayton cycle compressor (111)
    [0129] - turbo-expander of the Brayton cycle (112)
    [0130] - heat regenerator (113)
    [0131] - discharge duct (114) from the compressor (111) to the high temperature heat exchanger (130)
    [0132] - return duct (115) of heat exchanger (130) high temperature
    [0133] - return duct (116) of the low temperature heat exchanger (131) to regenerator (113) and the compressor (111)
    [0134] - evacuation conduit (117) from the turbo-expander of the reverse Brayton cycle (112) to the low temperature heat exchanger (131)
    [0135] - Heat exchanger (130) of heat supply of the reverse Brayton cycle
    [0136] - Heat exchanger (131) of cold supply of the reverse Brayton cycle
    [0137] - Heat exchanger (132) of external heat supply through the heat supply duct (70) and return by (71)
    [0138] - Heat exchanger (133) of external cold supply through the cold supply conduit (72) and return through (73)
    [0139] - High temperature heat transfer heat transfer fluid circulation pump (134)
    [0140] - low temperature heat transfer heat transfer fluid circulation pump (135)
    [0141] The operation procedure of the thermal feed system reinforced with a reverse Brayton cycle that adopts the structure shown in Figure 3 is such that when the compressor (111) of the reverse Brayton cycle is operated by the electric starter motor (110), the temperature of the working thermal fluid of the reverse Brayton cycle (helium) circulating at high temperature through the conduit (114) towards the heat exchanger (130), where it gives heat to the heat transfer fluid that feeds the power units, returning through the conduit (115) to the regenerator (113) and from here to the turbo-expander (112), where it performs mechanical work while cooling. From the turbo-expander (112), it passes to the heat exchanger (131), through the duct (117) absorbing heat from the power units and returning through the duct (116) back to the compressor (111).
    [0142] The heat exchangers (5) of high temperature of the power units are fed by the heat exchanger (132) of external heat supply with the help of the heat exchanger (130) of the inverse Brayton cycle, by the heat exchanger conduit. heat supply (70) and return through (71). In the same way, the low temperature heat exchangers (4) of the power units are supplied by the heat exchanger (133) of the external cold supply with the help of the heat exchanger (131) of the reverse Brayton cycle, through the heat extraction duct (73) and return through (72).
    [0143] Description of preferred embodiments of the invention
    [0144] The preferred configuration of the thermal plant with double effect machine, thermal accumulators, forced convection and thermal feed reinforced with a reverse brayton cycle and operating procedure is shown in figure 2, where the residual heat evacuated by the first power unit is used to feed cascade the second power unit as shown in figure 2 and the other units if they existed, so that the heat transfer fluid feeds the first power unit through conduit (70), where to exit of the exchanger (5) passes to the second power unit by feeding the heat exchanger (5) of the second power unit, to be evacuated by the duct (71) in case of lack of sufficient thermal energy to feed the next unit of power. power if any. The heat transfer fluid of the sump feeds in parallel to each heat exchanger (4) of the respective power units. The components of the two power units connected in parallel are show in Figure 2, including in addition to the components cited in Figure 1, the following components:
    [0145] - supply conduit (70) of the hot heat transfer fluid to the heater (5) of the first power unit, where it passes to the heater (5) of the second power unit, and exits through the conduit (71)
    [0146] - Exit line (71) of the hot heat transfer fluid of the heater (5)
    [0147] - supply conduit (72) of the cold heat transfer fluid to the cooler (4) of the first power unit and to the cooler (4) of the second power unit.
    权利要求:
    Claims (5)
    [1]
    1. THERMAL PLANT WITH DOUBLE-EFFECT MACHINE, THERMAL ACCUMULATORS, FORCED CONVECTION AND REINFORCED THERMAL POWER WITH AN INVERSE BRAYTON CYCLE AND OPERATING PROCEDURE is characterized by converting thermal energy to mechanical and / or electrical energy via mechanical energy, by means of of an innovative thermal cycle implemented by means of an alternative double-acting poly-cylindrical thermal machine, which operates with helium as a working thermal fluid, which is equipped with two thermal foci, where the high temperature focus is a thermal source intended to heat the thermal fluid of work and the focus of low temperature consists of a heat sink, which is intended to extract heat from the thermal fluid of work, and where both thermal foci (high and low temperature) are constituted by heat exchangers, ( 5) and (4) respectively that operate by forced thermal convection by means of blowers.
    The heat transfer thermal fluids needed to heat and cool the thermal working fluid are conventional fluids used for this purpose in thermal transfer processes such as water or thermal oil among others known, and where the heat necessary to heat the thermal fluid heat transfer comes from any available heat source such as waste heat from the cooling of various machines and compressors, thermal energy of fossil origin, solar thermal, geothermal, and in general high, medium and even low temperature waste heat , and where the heat sink (4) transfers heat from a thermal working fluid (helium) of the thermal cycle implemented by the thermo-actuator cylinder (1), to the thermal fluid of heat transfer, by means of a refrigerant that can be air or water at room temperature, or a steam compression refrigeration machine, or the evacuation of a turbo-ex pansor at sub-environmental temperature, or a conventional cooling tower by air or water, and whose components for each power unit include:
    - Double-acting thermo-actuator cylinder (1)
    - left chamber (2) of the double acting thermo-actuator cylinder (1)
    - Right chamber (3) of the double acting thermo-actuator cylinder (1)
    - working thermal fluid cooler (4)
    - working thermal fluid heater (5)
    - forced convection blower (6) of cold working thermal fluid
    - forced convection blower (7) of hot working thermal fluid
    - Thermal thermal fluid storage tank (20)
    - Thermal thermal fluid storage tank (30)
    - Thermal thermal fluid storage tank (40)
    - Thermal thermal fluid storage tank (50)
    - valve (21) of two positions and three ways (2/3) of communication of the coolant of the thermal fluid of work (4) and the heater of the thermal fluid of work (5) and the thermal accumulator of thermal fluid of work (20) )
    - communication valve 2/3 (31) of the working thermal fluid cooler (4) and the working thermal fluid heater (5) and the thermal thermal fluid storage tank (30)
    - valve 2/3 (41) for communication of the working thermal fluid cooler (4) and the working thermal fluid heater (5) and the thermal thermal fluid storage tank (40)
    - communication valve 2/3 (51) of the working thermal fluid cooler (4) and the working thermal fluid heater (5) and the thermal thermal fluid storage tank (50)
    - valve 2/3 (22) communicating the thermal thermal fluid storage tank (20) and the suction pipes of the forced convection blower (6) of the cold working thermal fluid and the forced convection blower (7) ) of hot working thermal fluid
    - 2/3 valve (32) communicating thermal work fluid thermal accumulator (30) and suction ducts of forced convection blower (6) of cold working thermal fluid and forced convection blower (7) ) of hot working thermal fluid
    - valve 2/3 (42) communicating the thermal thermal fluid accumulator (40) and the suction lines of the forced convection blower (6) of the cold working thermal fluid and the forced convection blower (7) ) of hot working thermal fluid
    - valve 2/3 (52) communicating the thermal thermal fluid storage tank (50) and the suction pipes of the forced convection blower (6) of the cold working thermal fluid and the forced convection blower (7) ) of hot working thermal fluid
    - 2/3 valve (23) that connects the thermal accumulators (20) and (30) with the working fluid communication valve 2/3 (24) with chambers (2) and (3) of the double-acting thermostatic cylinder (one)
    - 2/3 valve (45) that connects the thermal accumulators (40) and (50) with the working fluid communication valve 2/3 (44) with chambers (2) and (3) of the double-acting thermostatic cylinder (one)
    - valve 2/3 (24) that communicates the 2/3 valve (23) and the chambers (2) and (3) of the double acting thermo actuator cylinder (1)
    - valve 2/3 (44) that communicates the 2/3 valve (45) and the chambers (2) and (3) of the double acting thermo actuator cylinder (1)
    [2]
    2. THERMAL PLANT WITH DOUBLE-EFFECT MACHINE, THERMAL ACCUMULATORS, FORCED CONVECTION AND REINFORCED THERMAL POWER SUPPLY WITH AN INVERSE BRAYTON CYCLE AND OPERATING PROCEDURE, according to the first claim, characterized by the cascade coupling of two or more power units, where the heat The residual evacuated by the first power unit is used to feed in cascade the second power unit and the others if they exist, so that the heat transfer fluid feeds the first power unit through the duct (70), where the leaving the exchanger (5) goes to the second power unit by feeding the heat exchanger (5) of the second power unit, to be evacuated by the duct (71) in case of lack of sufficient thermal energy to power the next unit of power if any. The heat transfer fluid of the sump feeds in parallel to each heat exchanger cooler (4) of the respective power units, where the components of the two power units connected in cascade include those corresponding to each power unit, apart of the components of heat and cold supply that are cited:
    - supply conduit (70) of the hot heat transfer fluid to the heater (5) of the first power unit, where it passes to the heater (5) of the second power unit, and exits through the conduit (71)
    - Exit line (71) of the hot heat transfer fluid of the heater (5)
    - supply conduit (72) of the cold heat transfer fluid to the cooler (4) of the first power unit and to the cooler (4) of the second power unit.
    [3]
    3. Procedure of operation of the THERMAL PLANT WITH DOUBLE-EFFECT MACHINE, EXCHANGEABLE THERMAL ACCUMULATORS according to claim 1a, equipped with interchangeable thermal accumulators (20), (30), (40) and (50), cooler (4), heater ( 5), blower (6) of forced convection of the cold working fluid and blower (7) of forced convection of hot working fluid, is such that starting from an initial situation with the piston located in the left dead center (PMI) ), begins the thermal cycle formed by four phases carried out during the course of two revolutions as specified:
    During phase 1, the plunger moves from left to right by virtue of the state of the following components:
    The thermal accumulator (20) is in the process of adiabatic expansion, valves 2/3 (21) and (22) closed, the valve (23) of the thermal accumulator (20) open, and the valve (24) to the chamber (2) of the thermo-actuator cylinder (1) open and closed towards the chamber (3) of the thermo-actuator cylinder (1).
    The thermal accumulator (30) is in the heating process, valves 2/3 (31) and (32) open, giving way to the fluid from and to the heater (5).
    The thermal accumulator (40) is in the process of adiabatic compression, the valves 2/3 (41) and (42) closed, the valve (45) of the open thermal accumulator outlet, to put the thermal accumulator (40) in communication. ) and closed for the thermal accumulator (50) and the valve (44) to the chamber (3) of the thermo-actuator cylinder (1) open, and closed towards the chamber (2) of the thermo-actuator cylinder (1).
    The thermal accumulator (50) is in the cooling process, the 2/3 (51) and (52) valves open from and to the heat exchanger cooler (4) and closed from and to the heat exchanger heater (5). ).
    During phase 2, the plunger moves from right to left by virtue of the state of the following components:
    The thermal accumulator (20) is in the cooling process, the 2/3 (21) and (22) valves open from and to the heat exchanger cooler (4) and closed from and to the heat exchanger heater (5). ).
    The thermal accumulator (30) is in the process of adiabatic compression, valves 2/3 (31) and (32) closed, the valve (23) of the thermal accumulator (30) open, and the valve (24) to the chamber (2) of the thermo-actuator cylinder (1) open.
    The thermal accumulator (40) is in the heating process, valves 2/3 (41) and (42) open from and to the heat exchanger heater (5) and closed from and to the cooler heat exchanger (4). ).
    The thermal accumulator (50) is in the process of adiabatic expansion, valves 2/3 (51) and (52) closed, valve (45) for the outlet of the thermal accumulator (50) open, and the valve (44) to the chamber (3) of the thermo-actuator cylinder (1) open.
    During phase 3, the plunger moves from left to right by virtue of the state of the following components:
    The thermal accumulator (20) is in the process of adiabatic compression, valves 2/3 (21) and (22) closed and the valve (23) of the thermal accumulator (20) open, and the valve (24) to the chamber (3) of the thermo-actuator cylinder (1) open.
    The thermal accumulator (30) is in the cooling process, the 2/3 (31) and (32) valves open from and to the cooling heat exchanger (4) and closed from and to the heat exchanger heater (5). ).
    The thermal accumulator (40) is in the adiabatic expansion process, the valves 2/3 (41) and (42) closed, the valves (45) of the open thermal accumulator outlet, and the valve (44) to the chamber (2) of the thermo-actuator cylinder (1) open
    The thermal accumulator (50) is in the heating process, the valves 2/3 (51) and (52) open from and to the heat exchanger heater (5) and closed from and to the cooler heat exchanger (4). ).
    During phase 4, the plunger moves from right to left by virtue of the state of the following components:
    The thermal accumulator (20) is in the heating process, valves 2/3 (21) and (22) open from and to the heat exchanger heater (5) and closed from and to the cooler heat exchanger (4). ).
    The thermal accumulator (30) is in the adiabatic expansion process, the valves 2/3 (31) and (32) closed, the valve (23) for the outlet of the thermal accumulator (30) open, and the valve (24) to the chamber (3) of the thermo-actuator cylinder (1) open.
    The thermal accumulator (40) is in the cooling process, the 2/3 (41) and (42) valves open from and to the heat exchanger cooler (4) and closed from and to the heat exchanger heater (5). ).
    The thermal accumulator (50) is in the process of adiabatic compression, valves 2/3 (51) and (52) closed, the valve (45) of the thermal accumulator (50) open, and the valve (44) to the chamber (2) of the thermo-actuator cylinder (1) open.
    This thermal cycle is repeated for each unit of power indefinitely.
    [4]
    4. Thermal feed system of the THERMAL PLANT WITH DOUBLE-EFFECT MACHINE, THERMAL ACCUMULATORS, FORCED CONVECTION AND REINFORCED THERMAL POWER SUPPLY WITH AN INVERSE BRAYTON CYCLE, characterized by reinforcing the supply of external energy from the inside of the plant with an inverse Brayton cycle coupled to the plant, which provides the two high and low temperature thermal bulbs capable of supplementing the external energy input, in such a way that the contribution of high and low temperature thermal energy responsible for feeding both the hot focus and the focus Each unit of available power is cooled simultaneously from the outside of the plant and from inside the plant, so that the supply of high-temperature or hot energy from the outside of the plant includes waste heat such as heat of cooling of machines and thermal engines, compressors, solar, geothermal, thermocean, nuclear waste, thermal energy of fossil origin and in general high, medium and even low temperature waste heat, while the supply of cold low temperature energy from the The exterior of the plant includes any heat transfer fluid at room temperature such as air or water at room temperature, as well as any refrigerant for industrial use. On the other hand, the supply of hot and cold energy from inside the plant comes from an inverse Brayton cycle that forms part of the structure of the plant object of the invention.
    The energy supply system, which comprises the external and internal supply formed by a reverse Brayton cycle, includes at least the following components:
    - Electric starter motor (110)
    - Inverse Brayton cycle compressor (111)
    - turbo-expander of the Brayton cycle (112)
    - heat regenerator (113)
    - discharge duct (114) from the compressor (111) to the high temperature heat exchanger (130)
    - return duct (115) of heat exchanger (130) high temperature
    - return duct (116) of the low temperature heat exchanger (131) to regenerator (113) and the compressor (111)
    - evacuation conduit (117) from the turbo-expander of the reverse Brayton cycle (112) to the low temperature heat exchanger (131)
    - Heat exchanger (130) of heat supply of the reverse Brayton cycle
    - Heat exchanger (131) of cold supply of the reverse Brayton cycle
    - Heat exchanger (132) of external heat supply through the heat supply duct (70) and return by (71)
    - Heat exchanger (133) of external cold supply through the cold supply conduit (72) and return through (73)
    - High temperature heat transfer heat transfer fluid circulation pump (134)
    - low temperature heat transfer heat transfer fluid circulation pump (135)
    [5]
    5. Operating procedure of the thermal feed system of the THERMAL FLOOR WITH DOUBLE EFFECT MACHINE, THERMAL ACCUMULATORS, FORCED CONVECTION AND REINFORCED THERMAL POWER SUPPLY WITH AN INVERSE BRAYTON CYCLE
    according to claim 4a, which is such that by operating the compressor (111) of the reverse Brayton cycle by the electric starter motor (110), the working fluid temperature of the inverse Brayton cycle that circulates at high temperature through the conduit rises (114) to the heat exchanger (130), where it gives heat to the heat transfer fluid it feeds the power units driven by the circulation pump of the heat transfer fluid of high temperature (134), returning through the conduit (115) to the regenerator (113) and from here to the turbo-expander (112), where it performs Mechanical work while cooling. From the turbo-expander (112), it passes to the heat exchanger (131), through the duct (117) absorbing heat from the power units and returning through the duct (116) back to the compressor (111).
    The heat exchangers (5) of high temperature of the power units are fed by the heat exchanger (132) of external heat supply with the help of the heat exchanger (130) of the inverse Brayton cycle, by the heat exchanger conduit. heat supply (70) and return through (71). In the same way, the low temperature heat exchangers (4) of the power units are supplied by the heat exchanger (133) of the external cold supply with the help of the heat exchanger (131) of the reverse Brayton cycle, driven by the circulation pump of the low temperature heat transfer thermal fluid (135), by the heat extraction duct (72) and return by (73).
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    WO2003081011A1|2002-03-27|2003-10-02|Richard Laurance Lewellin|Engine for converting thermal energy to stored energy|
    ES2551397T3|2011-01-28|2015-11-18|Walter Loidl|Thermal motor|
    ES2571004A1|2014-11-20|2016-05-23|Univ Coruna|Thermal plant with closed process cycles coupled in cascade |
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    ES201700667A|ES2696950B2|2017-07-18|2017-07-18|Thermal plant with double effect machine, thermal accumulators, forced convection and reinforced thermal feed with a reverse Brayton cycle and operating procedure.|ES201700667A| ES2696950B2|2017-07-18|2017-07-18|Thermal plant with double effect machine, thermal accumulators, forced convection and reinforced thermal feed with a reverse Brayton cycle and operating procedure.|
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