ES2851381B2 - Gas turbine operating with baro-thermal pulses and operating procedure - Google Patents

Description

DESCRIPTION

Gas turbine operating with baro-thermal pulses and operating procedure

Technical field of the invention

The present invention called "GAS TURBINE OPERATING WITH BARO-THERMAL PULSES AND OPERATING PROCEDURE" belongs to the technical field of thermoelectric plants that convert thermal energy to electrical energy via turbine and electric generator, using medium or high temperature heat. from external sources of heat from concentrated solar energy, nuclear, thermal energy of fossil origin such as natural gas or hydrogen or residual thermal energy of medium or high degree.

Purpose of the invention

The present invention called "GAS TURBINE OPERATING WITH BARO-THERMAL PULSES AND OPERATING PROCEDURE", has the purpose of converting thermal energy from a heat source into mechanical work and/or electricity through the use of gas turbines that operate with barothermal pulses (gas turbines that operate with pressure pulses under a thermal cycle based on compensation between positive and negative pressures) in a closed circuit, which are installed mechanically coupled to each other through a common shaft, where their thermal working fluid is heated and cooled respectively by means of a heat transfer thermal fluid such as helium or hydrogen thermal oil and cooling or heat extraction fluids such as water or a cooling fluid They can optionally be fed with medium and/or high temperature residual heat, heat concentrated solar, heat from nuclear sources and heat of combustion generated with natural gas, hydrogen or bi or fuels preferably.

Background of the invention

In known thermoelectric plants, it is common to use turbines for the conversion of thermal to mechanical energy, which use Rankine cycles with steam turbines, Brayton cycles with gas turbines, combined cycles between both or organic Rankine cycles where both work through thermodynamic processes. open.

In the case of this invention, a cascade of turbines is proposed, each of which works with pressure pulses associated with temperature (barothermal pulses) generated by isochoric addition of heat to the thermal working fluid according to a closed thermal process within heat accumulation deposits or thermal reservoirs and subsequent adiabatic expansion and/or contraction in the gas turbine operating at baro-thermal pulses. Consequently, in the current state of technology, there are no known turbines that operate in a closed circuit using pressure pulses, nor any generation technique that uses the technique described for this invention.

Description of the invention

Brief description of the invention

The invention called "GAS TURBINE OPERATING WITH BAROTHERMAL PULSES AND OPERATING PROCEDURE", consists of one or more closed-circuit gas turbines to be installed in thermo-mechanical and thermoelectric plants, which are coupled by means of a common shaft to all the machines. rotaries of the system, where each of gas turbines, operates intermittently based on baro-thermal pulses, which consist of positive pressure pulses associated with the temperature achieved by adding heat with isochoric heating and/or negative pressure pulses associated with the temperature achieved by heat extraction with isochoric cooling of the gaseous working thermal fluid carried out inside reservoirs intended for this purpose, and where such barothermal pulses are applied to the gas turbine under two modalities:

- positive baro-thermal pulses (pressure greater than an equilibrium pressure) applied from the high pressure reservoirs and

- Negative baro-thermal pulses (pressure lower than equilibrium pressure) applied from low pressure reservoirs.

The reason for having at least two tanks to accumulate the thermal working fluid, heated at a constant volume in the heat source and cooled in the heat sink area, is due to the fact that it allows the generation of high pressure and temperature pulses so intermittent at the inlet of the gas turbine operating at baro-thermal pulses intermittently and sequentially. In the same way, the reason for having at least two tanks to accumulate the thermal working fluid cooled at a constant volume in the area of the heat sink is due to the fact that it allows the generation of low pressure and temperature pulses, which produces negative pressure pulses. intermittently in the evacuation zone of the gas turbine to thermal pulses, which are applied intermittently and sequentially, in synchrony with the positive baro-thermal pulses.

In one of the possible design options for the gas turbine operating at barothermal pulses, for each high pressure barothermal pulse applied to the inlet of the gas turbine operating at barothermal pulses, a negative pressure pulse is applied. in the evacuation zone of the gas turbine operating at baro-thermal pulses synchronized with the high pressure pulse. With the application of both positive and negative pressure pulses simultaneously between the high and low pressure zones of the gas turbine operating at baro-thermal pulses, a significant pressure difference between the inlet and outlet of the gas turbine operating at baro-thermal pulses is achieved. baro-thermal pulses, generating at the beginning of each baro-thermal pulse a significantly high torque, which is attenuated as the thermal working fluid expands inside the gas turbine to thermal pulses.

In another of the possible design options of the gas turbine operating at barothermal pulses, for each high pressure baro-thermal pulse applied to the inlet of the gas turbine operating at barothermal pulses, a pressure pulse is not applied. negative in the evacuation zone of the gas turbine operating at baro-thermal pulses but instead the heat extraction process is carried out towards the sump under the reference pressure and temperature.

With the application of positive pressure pulses only in the high pressure zone of the gas turbine operating at baro-thermal pulses, only the difference in pressure between the inlet and outlet of the gas turbine operating at baro-thermal pulses is achieved. to the equilibrium pressure with which it evacuates to the heat sink. Therefore, in this case the effect of each baro-thermal pulse gives rise to a lower torque than in the case of the option of simultaneously positive and negative baro-thermal pulses.

The thermal working fluid subjected to high temperature and its corresponding pressure inside each high pressure reservoir, once released in the form of a pulse, expands adiabatically inside the gas turbine operating at baro-thermal pulses (where the adiabatic expansion process approaches a quasi-isothermal process of expansion because the heat accumulated in the metal of each isochoric heating reservoir as well as in its respective associated heat exchanger, transfer heat to the thermal fluid of work during the adiabatic expansion process in theory, and in the same way, each isochoric cooling tank as well as in its respective heat exchanger or associated cooler, transfer heat from the heat extraction thermal fluid during the adiabatic expansion process in theory ), generating useful mechanical work that can be converted to electrical energy via mechanical energy.

In general, when one of the thermal working fluid reservoir tanks subjected to high pressure due to having been heated at constant volume is applied to the gas turbine operating at baro-thermal pulses, it expands, after expanding, which entails the decrease in pressure to the level of the intermediate reference pressure, such reservoir is isolated from the gas turbine operating at barothermal pulses, with which the following heating reservoir tank with thermal working fluid at high temperature and corresponding pressure comes into operation , so that when one of the isochoric heating tanks is in the expansion process, the other tanks are in the isochoric heating phase. In the same general way, when one of the low pressure working fluid reservoir tanks, after contracting due to having been cooled at constant volume, communicates with the gas turbine evacuation zone operating at baro-thermal pulses, which entails the increase in pressure from the minimum pressure reached by isochoric cooling to the level of the reference intermediate pressure, then it is isolated from the gas turbine by thermal pulses, giving rise to the next thermal working fluid deposit to start operating of low temperature and corresponding pressure, so that when one of the isochoric cooling tanks is in the process of working in communication with the gas turbine operating at baro-thermal pulses, the other low-temperature working thermal fluid tanks and pressure, are isolated from the gas turbine operating at baro-thermal pulses and in the isochoric cooling phase by extraction of isochoric d e heat to the heat sink.

Description of the figures

In what follows, the components that constitute the invention called "GAS TURBINE OPERATING WITH BARO-THERMAL PULSES AND OPERATION PROCEDURE" are described by way of illustration and not limitation, to facilitate the understanding of its structure and operation, where reference is made to the following figures:

Figure 1 shows the structure of a power module (40) operating with a gas turbine operating with baro-thermal pulses applied to the turbine inlet, which consists of at least two high-pressure isochoric heating reservoir tanks to facilitate the impulses. of high pressure, and a single cooling tank at room temperature with which the gas turbine operates, operating at baro-thermal pulses, which includes at least the following components:

- supply pipe (1) of the thermal heat transfer fluid

- return duct (2) of the heat transfer thermal fluid

- supply pipe (3) of the heat extraction thermal fluid

- return duct (4) of the heat extraction thermal fluid

- high pressure working thermal fluid heater (10)

- forced convection working thermal fluid recirculation compressor (11)

- high pressure reservoir tank by heat addition at constant volume (12)

- discharge valve (13) of the thermal working fluid at high pressure to the gas turbine operating at baro-thermal pulses (26)

- working thermal fluid heater (14)

- forced convection working thermal fluid recirculation compressor (15)

- high pressure reservoir tank by heat addition at constant volume (16)

- discharge valve (17) of the thermal working fluid at high pressure to the gas turbine operating at baro-thermal pulses (26)

- low pressure thermal working fluid cooler (29)

- forced convection working thermal fluid recirculation compressor (19)

- gas turbine operating at baro-thermal pulses (26) connected by shaft to an electric generator (27)

- heat recovery unit (28) consisting of a heat exchanger to take advantage of the residual heat evacuated by the gas turbine operating at baro-thermal pulses (26)

- thermal working fluid discharge valve (31) towards the high pressure tank (12) - thermal working fluid discharge valve (33) towards the high pressure tank (16) - thermal fluid supply compressor work (34)

- inlet (38) of the heat recovery thermal fluid to the heat recovery unit (28)

- return (39) of the heat recovery thermal fluid from the heat recovery unit (28)

Figure 2 represents the T-s (temperature-entropy) and p-V (pressure-volume) diagrams of the thermal cycle corresponding to the power module (40) operating with a gas turbine operating with baro-thermal pulses applied to the turbine inlet.

Figure 3 represents the structure of a power module (41) operating with a gas turbine operating at baro-thermal pulses at the inlet and outlet of the turbine, whose structure consists of at least two high-pressure reservoir tanks with isochoric heating by addition. of heat and two low-pressure reservoir tanks for isochoric cooling by heat extraction, which facilitate the simultaneously applied positive and negative pressure pulses with which the gas turbine operates operating at baro-thermal pulses, which includes at least the following components:

- supply pipe (1) of the thermal heat transfer fluid

- return duct (2) of the heat transfer thermal fluid

- supply pipe (3) of the heat extraction thermal fluid

- return duct (4) of the heat extraction thermal fluid

- high pressure working thermal fluid heater (10)

- forced convection working thermal fluid recirculation compressor (11)

- high pressure reservoir tank by heat addition at constant volume (12)

- discharge valve (13) of the thermal working fluid at high pressure to the gas turbine operating at baro-thermal pulses (26)

- working thermal fluid heater (14)

- forced convection working thermal fluid recirculation compressor (15)

- high pressure reservoir tank by heat addition at constant volume (16)

- discharge valve (17) of the thermal working fluid at high pressure to the gas turbine operating at baro-thermal pulses (26)

- low pressure thermal working fluid cooler (29)

- forced convection working thermal fluid recirculation compressor (19)

- low pressure reservoir tank by heat extraction at constant volume (20)

- Evacuation valve (21) of the thermal working fluid at low pressure from the gas turbine operating at baro-thermal pulses (26) towards the tank (20)

- low pressure thermal working fluid cooler (22)

- forced convection working thermal fluid recirculation compressor (23)

- low pressure reservoir tank by heat extraction at constant volume (24)

- Evacuation valve (25) of the thermal working fluid at low pressure from the gas turbine operating at baro-thermal pulses (26) towards the tank (24)

- gas turbine operating at baro-thermal pulses (26) connected by shaft to an electric generator (27)

- suction valve for the thermal working fluid (30) from the low pressure tank (20) - discharge valve for the thermal working fluid (31) towards the high pressure tank (12) - suction valve for the thermal working fluid (32) from the low pressure tank (24) - discharge valve for the thermal working fluid (33) to the high pressure tank (16) - working thermal fluid feed compressor (34)

Figure 4 represents the T-s (temperature-entropy) and p-V (pressure-volume) diagrams of the thermal cycle corresponding to the power module (41) operating with a gas turbine operating at baro-thermal pulses applied to the inlet and outlet of the turbine. , where the addition and extraction of heat are performed by an isochoric process.

Figure 5 represents the T-s (temperature-entropy) and p-V (pressure-volume) diagrams of the thermal cycle corresponding to the power module (41) operating with a gas turbine operating at baro-thermal pulses applied to the inlet and outlet of the turbine. , where the addition and extraction of heat are performed by an isochoric process following an isothermal process.

Figure 6 shows the pressure-time pulse diagram (pressure of the baro-thermal pulses applied at the inlet of the gas turbine operating at baro-thermal pulses (26) as a function of time). The high-pressure thermal working fluid reservoirs (10) and (14), as a result of the prior addition of heat added at constant volume, intermittently provide pressure pulses to the gas turbine operating at baro-thermal pulses. In the low pressure reservoir 18, heat extraction is carried out causing the cooling at constant pressure of the thermal working fluid.

Figure 7 shows the pressure-time pulse diagram (pressure of the baro-thermal pulses applied at the inlet and outlet of the gas turbine operating at baro-thermal pulses as a function of time). The high-pressure thermal working fluid reservoirs (10) and (14), as a result of the prior addition of heat added at constant volume, intermittently provide pressure pulses to the gas turbine operating at baro-thermal pulses. The reservoirs of the low pressure thermal working fluid (18) and (22), as a result of the previous extraction of heat at constant volume, intermittently provide low pressure pulses to the gas turbine operating at baro-thermal pulses in synchrony with the low pressure pulses, which causes a significant pressure difference between the pressures at the inlet and outlet of the gas turbine operating at baro-thermal pulses.

Figure 8 shows the simplified diagrams of the power modules (40) and (41). Figure 8 (a) shows the simplified diagram of the power module (40) showing the input and return ducts (1) and (2) for the addition of heat, as well as the input and return ducts (38). and (39) of heat transfer fluid from the heat recovery unit and the inlet and return ducts (3) and (4) of the heat transfer fluid for heat extraction (3) and (4) towards a thermal sink .

Figure 8 (b) shows the simplified diagram of the power module (41) showing the input and return ducts (1) and (2) for the addition of heat and the input and return ducts (3) and ( 4) of the heat transfer fluid for heat extraction (3) and (4) to a thermal sink.

Figure 9 represents in 9(a) the simplified diagram of the power module (40) corresponding to the power module (40) shown in 9(b), which consists of the structure of a power module (40) operating with gas turbine operating at baro-thermal pulses applied to the turbine inlet (26), which consists of at least two reservoir tanks (12) and (16) of high pressure isochoric heating to facilitate high pressure pulses, and a single tank (29) for isobaric cooling at room temperature with which the gas turbine operating at baro-thermal pulses (26). To capture the heat supplied from an external heat source through the exchanger (50), it includes a pump (60) for recirculating the heat transfer thermal fluid as shown in Figure 9 (a).

Figure 10 represents at 10 (a) the simplified diagram of the power module (41) corresponding to the detailed diagram of the power module (41) shown at 10 (b), which consists of the structure of a power module (41 ) operating with a gas turbine operating at baro-thermal pulses applied to the inlet of the turbine (26), which consists of at least - two reservoir tanks (12) and (16) of high pressure isochoric heating to facilitate the impulses high pressure, and at least

- two reservoir tanks (20) and (24) for low pressure isochoric cooling to facilitate high pressure negative impulses.

Where the power module shown in figure 10 (a) includes at least the following components:

- supply pipe (1) of the thermal heat transfer fluid

- return duct (2) of the heat transfer thermal fluid

- supply pipe (3) of the heat extraction thermal fluid

- return duct (4) of the heat extraction thermal fluid

Figure 11 shows the structure of a plant made up of several power modules (40) coupled in parallel with respect to the heat transfer fluid used to feed the modules of the type (40).

Figure 12 shows the structure of a plant made up of several power modules (40) coupled in series with respect to the heat transfer fluid used to feed the modules of the type (40).

Figure 13 shows the structure of a plant made up of power modules (41) coupled in parallel with respect to the heat transfer fluid used to feed the modules of the type (41).

Figure 14 shows the structure of a plant made up of power modules (41) coupled in series with respect to the heat transfer fluid used to feed the modules of the type (41).

Figure 15 shows the schematic of the heat recovery system for a power module (41) by means of a heat pump implemented under an inverse Brayton cycle, which includes the following components:

- heat exchanger (50) for thermal reinforcement to the heat pump, which captures heat from an external heat source to reinforce the supply of heating energy to the power module (41) through the duct (1)

- heat exchanger (51) for recovery of residual heat from the module (41) carried out by the suction of the compressor (53) of the inverse Brayton cycle corresponding to the heat pump

- heat exchanger (52) for sub-cooling of the thermal fluid for heat transfer from the module (41) to the thermal sink.

- compressor (53) of the inverse Brayton cycle that forms the heat pump.

- expander (54) of the inverse Brayton cycle that forms the heat pump.

- heat supply duct (55) by means of the thermal heat transfer fluid - heat return duct (56) by means of the thermal heat transfer fluid Figure 16 shows the parallel coupling scheme of heat recovery systems for power modules (41) by means of a heat pump implemented under the inverse Brayton cycle, where the heat supplied from an external heat source enters in parallel through the duct (55) to each thermal reinforcement heat exchanger (50) to the heat pump of each power module (41), exiting towards the external heat source through the duct (56).

Figure 17 shows the series coupling scheme of heat recovery systems in plants formed by power modules (41) by means of a heat pump implemented under the inverse Brayton cycle, where the heat supplied from an external heat source enters through the duct (55) to the first heat exchanger (50) for thermal reinforcement to the heat pump of the first power module, then passing to the second heat exchanger (50) for thermal reinforcement to the heat pump of the second power module for out via conduit (56) to the external heat source.

Detailed description of the invention

The invention called "GAS TURBINE OPERATING WITH BARO-THERMAL PULSES AND OPERATING PROCEDURE", consists of one or more gas turbines with closed circuit barothermic pulses, which work by means of pressure pulses and which are intended for thermo-mechanical plants and thermo-electric plants, where the barothermal pulse gas turbines are coupled to each other by means of a shaft common to all the rotating machines of the plant, and where each of the gas turbines operates intermittently based on the application of barothermal pulses -thermal, which consist of positive pressure pulses (high pressure of the thermal working fluid) associated with the temperature of the thermal working fluid, where both pressure and temperature are achieved by isochoric addition of heat to the thermal working fluid, as well such as the application of negative baro-thermal pulses, which consist of negative pressure pulses (low pressure of the thermal working fluid) associated with the temperature of the fluid or thermal work, which entails cooling of the thermal working fluid, and where both baro-thermal pulses (positive and negative) are carried out inside high pressure reservoir tanks for positive pulses and inside low pressure reservoir tanks for negative pulses, and where such positive and negative baro-thermal pulses are simultaneously applied to the gas turbine to baro-thermal pulses under two modalities:

- positive baro-thermal pulses (pressure greater than equilibrium pressure) applied from the high pressure reservoirs where they expand in the turbine giving mechanical work and - negative baro-thermal pulses (pressure less than equilibrium pressure) applied from the low pressure reservoirs in the evacuation zone of the gas turbine operating at baro-thermal pulses, and

where the pressure difference between the pressure of the positive pulses and the negative pulses gives rise to the performance of mechanical work in the gas turbine operating at barothermal pulses and,

where the thermal working fluid evacuated from the gas turbine operating at barothermal pulses to the low pressure reservoir tanks is transferred again to the high pressure reservoir tanks, thus closing the circuit to repeat the cycle indefinitely and,

where the thermal energy necessary to generate the baro-thermal pulses can optionally come from both medium or high grade residual heat, as well as from the external combustion of hydrogen, natural gas or biofuels, as well as nuclear energy and concentrated solar energy and

where the thermal working fluid must be characterized by a high coefficient of adiabatic expansion and high specific heat, preferably helium.

The operating principle of the gas turbine operating at baro-thermal pulses is based on the fact that the addition of heat at a constant volume and closed process to a thermal working fluid confined in a reservoir causes an increase in temperature and corresponding pressure within the reservoir. . If, under these conditions, instantaneous discharge of the thermal working fluid is caused to the gas turbine operating at baro-thermal pulses, the turbine responds with a rotational movement due to the torque exerted by the thermal working fluid when it expands. As the thermal working fluid expands adiabatically, its pressure and temperature decrease until reaching equilibrium between pressures (turbine inlet and outlet pressure).

When equilibrium is reached between inlet and outlet pressures, the rotation torque is cancelled, and for the turbine to continue rotating and continue performing mechanical work, it is necessary to apply the next baro-thermal pulse and so on indefinitely.

When the pressure of the high pressure reservoir tank reaches the equilibrium pressure due to expansion, it loses the capacity to perform mechanical work, for which it is necessary to recover the initial pressure again by means of the isochoric addition of heat. The isochoric heat addition phase requires time for heat transfer from the heat transfer fluid to the thermal working fluid. During the time interval required for the isochoric heating of the thermal working fluid confined within the high pressure reservoir tank, no energy is supplied to the turbine from this reservoir. Therefore, at least one other high pressure reservoir is needed to take over from this one during the idle interval. So for the turbine to operate continuously with baro-thermal pulses, at least two high-pressure reservoirs are needed so that at the end of each barothermal pulse generated from one reservoir, the next baro-thermal pulse begins from at least one other alternate reservoir.

The gas turbine structure operating at baro-thermal pulses that satisfies the condition of having two high-pressure reservoirs so that at the end of each baro-thermal pulse generated from one reservoir, the next baro-thermal pulse begins from at least another reservoir alternatively, it is shown in figures 1 and 3, where the gas turbine structure operating at baro-thermal pulses shown in figures 1 and 3, gives rise to two power modules that include the gas turbine operating at baro-thermal pulses -thermal:

- Power module (40) represented by Figure 1 operating with a gas turbine at baro-thermal pulses applied to the turbine inlet, whose structure is characterized by the gas turbine operating at baro-thermal pulses, which operates with pressure pulses at intermittent intervals of time, and consisting of at least two reservoir reservoirs of thermal working fluid (12) and (16) at high pressure acquired by the isochoric addition of heat to facilitate high pressure pulses, and a single low pressure reservoir tank 29 for isobaric cooling at room temperature, among which the gas turbine operates operating at baro-thermal pulses, and where all of which includes at least the following components:

- supply pipe (1) of the thermal heat transfer fluid

- return duct (2) of the heat transfer thermal fluid

- supply pipe (3) of the heat extraction thermal fluid

- return duct (4) of the heat extraction thermal fluid

- high pressure working thermal fluid heater (10)

- forced convection working thermal fluid recirculation compressor (11)

- high pressure reservoir tank by heat addition at constant volume (12)

- discharge valve (13) of the thermal working fluid at high pressure to the gas turbine operating at baro-thermal pulses (26)

- working thermal fluid heater (14)

- forced convection working thermal fluid recirculation compressor (15)

- high pressure reservoir tank by heat addition at constant volume (16)

- discharge valve (17) of the thermal working fluid at high pressure to the gas turbine operating at baro-thermal pulses (26)

- low pressure thermal working fluid cooler (29)

- forced convection working thermal fluid recirculation compressor (19)

- gas turbine operating at baro-thermal pulses (26) connected by shaft to an electric generator (27)

- heat recovery unit (28) consisting of a heat exchanger to take advantage of the residual heat evacuated by the gas turbine operating at baro-thermal pulses (26), where the recovered heat is transferred through the inlet and outlet ducts (38 ) and (39) of the heat recovery unit (28).

- thermal working fluid discharge valve (31) towards the high pressure tank (12) - thermal working fluid discharge valve (33) towards the high pressure tank (16) - thermal fluid supply compressor work (34)

- Power module (41) represented by figure 3 operating with a gas turbine operating at baro-thermal pulses applied to the inlet and outlet of the turbine, whose structure is characterized by the gas turbine operating at baro-thermal pressure pulses positive pressure applied to the input and negative pressure pulses applied to the output, both applied at intermittent time intervals, where to generate the positive and negative pulses there are at least two reservoir tanks of thermal working fluid (12) and (16) of high pressure acquired by isochoric heat addition, and at least two low pressure reservoir reservoirs of the thermal working fluid (20) and (24) acquired by isochoric heat extraction at constant volume, where both positive and negative pressure pulses are applied simultaneously, in such a way as to cause a significant increase between the turbine inlet and outlet pressure, where all of which includes at least the following components entities:

- supply pipe (1) of the thermal heat transfer fluid

- return duct (2) of the heat transfer thermal fluid

- supply pipe (3) of the heat extraction thermal fluid

- return duct (4) of the heat extraction thermal fluid

- high pressure working thermal fluid heater (10)

- forced convection working thermal fluid recirculation compressor (11)

- high pressure reservoir tank by heat addition at constant volume (12)

- discharge valve (13) of the thermal working fluid at high pressure to the gas turbine operating at baro-thermal pulses (26)

- working thermal fluid heater (14)

- forced convection working thermal fluid recirculation compressor (15)

- high pressure reservoir tank by heat addition at constant volume (16)

- discharge valve (17) of the thermal working fluid at high pressure to the gas turbine operating at baro-thermal pulses (26)

- low pressure thermal working fluid cooler (18)

- forced convection working thermal fluid recirculation compressor (19)

- low pressure reservoir tank by heat extraction at constant volume (20)

- Evacuation valve (21) of the thermal working fluid at low pressure of the gas turbine operating at baro-thermal pulses (26)

- low pressure thermal working fluid cooler (22)

- forced convection working thermal fluid recirculation compressor (23)

- low pressure reservoir tank by heat extraction at constant volume (24)

- Evacuation valve (25) of the thermal working fluid at low pressure of the gas turbine operating at baro-thermal pulses (26)

- gas turbine operating at baro-thermal pulses (26) connected by shaft to an electric generator (27)

- suction valve for the thermal working fluid (30) from the low pressure tank (20) - discharge valve for the thermal working fluid (31) towards the high pressure tank (12) - suction valve for the thermal working fluid (32) from the low pressure tank (24) - thermal working fluid discharge valve (33) to the high pressure tank (16) - thermal working fluid supply compressor (34)

The mode of operation of the power module (40) operating with a gas turbine operating at baro-thermal pulses applied to the turbine inlet (26), according to figure 1, operates in a closed circuit in such a way that the thermal working fluid is alternately transferred at low temperature and pressure from the low-pressure thermal working fluid cooler (29) to the high-pressure reservoir tanks (12) and (16), alternately by the thermal fluid discharge valve. (31) towards the high-pressure reservoir (12), and alternatively through the discharge valve of the thermal working fluid (33) towards the high-pressure reservoir (16), driven and transferred by the compressor of supply of the thermal working fluid (34).

Inside the high-pressure reservoir tanks (12) and (16), the process of adding heat at constant volume alternately takes place by means of recirculation of the thermal working fluid (to favor the transfer of value by forced convection) by the respective high pressure thermal working fluid heaters (10) (14), where the heating process is due to the addition of heat to the high pressure thermal working fluid heaters (10) (14) through the supply line (1) of the heat transfer fluid from an external heat source and returning through the return duct (2) to the external heat source.

The isochoric addition of heat to the high pressure reservoirs (12) and (16) is carried out in an intermittent alternating manner in such a way that the addition of heat and subsequent conversion into mechanical work in the gas turbine operating at baro-pulses (26) requires that: - when the high pressure reservoir (12) is in the isochoric heating phase, the high pressure reservoir (16) is in the adiabatic expansion phase, for which the discharge valve (13) of the high pressure thermal working fluid towards the gas turbine operating at baro-thermal pulses (26) is closed, while the discharge valve (17) of the high pressure thermal working fluid towards the gas turbine gas operating at barothermal pulses (26) open; Y

- when the high pressure reservoir (16) is in the isochoric heating phase, the high pressure reservoir (12) is in the adiabatic expansion phase, for which the discharge valve (17) of the thermal fluid of working at high pressure towards the gas turbine operating at barothermal pulses (26) is closed, while the discharge valve (13) of the thermal working fluid at high pressure towards the gas turbine operating at barothermal pulses (26 ) open.

When one of the high pressure thermal working fluid discharge valves (13) or (17) opens, a baro-thermal pulse is applied to the gas turbine operating at baro-thermal pulses (26) which expands adiabatically until reach the equilibrium pressure (expansion pressure in the turbine equal to the pressure of the cooler (29) of the low-pressure thermal working fluid), where the pressure profile of the baro-thermal pulses is shown in figure 6.

The working thermal fluid after adiabatic expansion in the gas turbine operating at baro-thermal pulses (26), still contains a significant amount of usable heat, which is likely to be partially recovered by the heat recovery unit (28) by means of the inlet and outlet ducts (38) and (39), which consists of a heat exchanger useful to take advantage of the residual heat evacuated by the gas turbine operating at barothermal pulses (26).

The thermal working fluid at low pressure evacuated by the gas turbine operating at baro-thermal pulses (26) transfers heat to the heat transfer fluid in the heat recovery unit 28 passing to the low pressure reservoir (29), where it is cooled at constant pressure by means of a cooling fluid that enters through conduit 3 to the low pressure reservoir (29), and returns through conduit 4 transferring the cooling heat to a thermal sink at room temperature.

The thermal working fluid at low pressure and temperature contained in the low pressure reservoir (29) is sucked in by the feed compressor (34), thus closing the operating circuit to repeat the cycle indefinitely.

The thermal cycle whose mode of operation has been described obeys the temperature-entropy and pressure-volume diagrams shown respectively in Figure 2 (a) and 2 (b), which includes the following four thermodynamic transformations:

- transformation (a-b) corresponds to an open adiabatic process during which the thermal working fluid is transferred by isentropic compression in the feeding phase to one of the reservoir tanks for subsequent isochoric heating,

- transformation (b-c) corresponds to the closed process of isochoric heating of the thermal working fluid in one of the isochoric heating reservoir tanks (12) or (16), - transformation (c-d) corresponds to the open process of adiabatic expansion of the fluid thermal work in the gas turbine operating at baro-thermal pulses (26) and performing useful mechanical work

- transformation (d-a) corresponds to the open isobaric cooling process of the thermal working fluid evacuated by the gas turbine operating at baro-thermal pulses (26) carried out in the heat recovery unit (28) and in the fluid cooler working thermal tank or low pressure reservoir (29) up to room temperature.

The operating mode of the power module (41) equipped with a gas turbine operating with baro-thermal pulses applied to the inlet and outlet of the turbine (26), according to figure 3, operates in a closed circuit in such a way that the fluid The thermal working temperature is alternately transferred at low temperature and pressure from the low-pressure reservoir tanks (20) and (24) by the suction valves (30) and (32) of the feed compressor (34) to the high-pressure reservoirs. pressure (12) and (16), through the discharge valves (31 and (33) of the feed compressor (34) Inside the high pressure reservoir tanks (12) and (16) the process of addition of heat at constant volume through recirculation of the thermal working fluid (to favor heat transfer by forced convection) by the respective high pressure thermal working fluid heaters (10) (14), where the heating process must be to the addition of heat to the heaters of the high pressure thermal working fluid (10) (14) through the supply line (1) of the heat transfer fluid from an external heat source and returning through the return line (2) to the heat source external.

The isochoric addition of heat to the high pressure reservoirs (12) and (16) is carried out in an intermittent alternating manner in such a way that the addition of heat and subsequent conversion into mechanical work in the gas turbine operating at baro-pulses (26) requires that:

- when the high pressure reservoir (12) is in the isochoric heating phase, the high pressure reservoir (16) is in the adiabatic expansion phase, for which the discharge valve (13) of the thermal fluid of high pressure work towards the gas turbine operating at barothermal pulses (26) is closed, while the discharge valve (17) of the thermal working fluid at high pressure towards the gas turbine operating at barothermal pulses (26) is open; Y

- when the high pressure reservoir (16) is in the isochoric heating phase, the high pressure reservoir (12) is in the adiabatic expansion phase, for which the discharge valve (17) of the thermal fluid of working at high pressure towards the gas turbine operating at barothermal pulses (26) is closed, while the discharge valve (13) of the thermal working fluid at high pressure towards the gas turbine operating at barothermal pulses (26 ) open.

When one of the high pressure thermal working fluid discharge valves (13) or (17) opens, a baro-thermal pulse is applied to the gas turbine operating at baro-thermal pulses (26) which expands adiabatically until reach the equilibrium pressure (expansion pressure in the turbine equal to the pressure of the cooler (18) of the low-pressure thermal working fluid), where the pressure profile of the baro-thermal pulses is shown in figure 6.

The thermal working fluid after adiabatic expansion in the gas turbine operating at baro-thermal pulses (26), is alternately evacuated by the evacuation valves (21) of the thermal working fluid at low pressure from the baro-thermal turbine. (26), or through the evacuation valve (25) of the thermal working fluid at low pressure from the baro-thermal turbine (26) towards the respective low pressure reservoir tanks, both the low pressure reservoir tank by extraction of heat at constant volume (20) as the low pressure reservoir tank by extraction of heat at constant volume (24).

Inside the low pressure reservoir tanks (20) and (24), the constant volume heat extraction process takes place intermittently by recirculating the thermal working fluid between (20) and (18) and between (24) and (22), to favor the transfer of heat by forced convection, where the heat is extracted from the respective coolers of the low pressure thermal working fluid (18) or (22), towards the thermal sink from where it is supplied through the duct supply (3) heat extraction cooling thermal fluid, returning through the return duct (4) to the thermal sink.

Inside the low pressure reservoir tanks (20) and (24), the constant volume heat extraction process takes place intermittently by means of recirculation of the thermal working fluid (to favor heat transfer by forced convection) by the respective low pressure thermal working fluid coolers (18) or (22), where the cooling process is due to the alternative extraction of heat from the low pressure thermal working fluid coolers (18) (22) through the duct (3) supplying the heat extraction thermal fluid and returning through the return duct (4) of the heat extraction thermal fluid towards the thermal sink.

The mode of operation in the task of intermittent heat extraction from each of the low pressure reservoir tanks (20) and (24) requires that:

- when the reservoir tank (20) is in the isochoric cooling phase, the evacuation valve (21) of the thermal working fluid at low pressure to the baro-thermal turbine (26) is closed and the reservoir tank (24 ) is in the phase of adiabatic contraction through the evacuation valve (25) of the thermal working fluid at low pressure; Y

- when the reservoir tank (24) is in the isochoric cooling phase, the evacuation valve (25) of the thermal working fluid at low pressure to the baro-thermal turbine (26) is closed and the reservoir tank (20 ) is in the phase of adiabatic contraction through the evacuation valve (21) of the thermal working fluid at low pressure.

When one of the pairs of valves (13) and (21) or (17) and (25) is opened, two baro-thermal pulses are simultaneously applied, one positive and one negative, to the gas turbine operating at baro-thermal pulses ( 26), where the high-pressure thermal working fluid expands adiabatically and the low-pressure thermal working fluid contracts adiabatically until reaching equilibrium pressure between the high-pressure reservoir tank and the corresponding low-pressure reservoir tank, whose profile is shown in figure 7.

When the equilibrium pressure is reached within each of the respective reservoir tanks of the low pressure thermal working fluid, both the low pressure reservoir tank by heat extraction at constant volume (20) and the low pressure reservoir tank By extracting heat at constant volume (24), the respective feeding phase of the low pressure thermal working fluid begins, being transferred by the thermal working fluid feeding compressor (34) to the high pressure reservoir tanks ( 12) and (16), completing the closed circuit of the described thermal cycle.

The operating mode of the power module (41) equipped with a gas turbine operating at baro-thermal pulses applied to the inlet and outlet of the gas turbine operating at baro-thermal pulses (26), works with a thermal cycle based on closed processes, which differs from all conventional thermal cycles by carrying out the task of extracting heat at a constant volume according to a closed process of each one of the low pressure reservoir tanks of which the thermal cycle consists, while in the conventional thermal cycles cooling occurs in open process. From this property we have that the power module (41) equipped with a gas turbine operating at baro-thermal pulses applied to the inlet and outlet of the turbine (26), exhibits the ability to operate with various thermal cycles in which the Heat extraction from the low pressure reservoir tanks (20) and (24) is carried out at constant volume. The task of operating with the thermal cycle characterized by extracting heat from the low pressure reservoir tanks (20) and (24) according to closed processes at constant volume includes the following two options:

- thermal cycle whose described mode of operation obeys the temperature-entropy and pressure-volume diagrams shown respectively in figure 4 (a) and 4 (b), which includes the following five thermodynamic transformations:

- process 1-2, which corresponds to the feeding of the thermal working fluid, which consists of an adiabatic-isentropic compression process, which absorbs external mechanical work, - process 2-3, which corresponds to an isochoric process of addition of heat from an external heat source, to heat the thermal working fluid with which a positive baro-thermal pulse is generated.

- process 3-4, which corresponds to an adiabatic-isentropic expansion process, which performs useful mechanical work by means of a pressure pulse.

- process 4-5, which corresponds to an isochoric cooling phase by heat extraction according to a closed process with which a negative baro-thermal pulse is generated,

- process 5-1, which corresponds to a contraction process based on adiabatic-isentropic compression, which performs a useful mechanical work.

- the thermal cycle whose described mode of operation obeys the temperature-entropy and pressure-volume diagrams shown respectively in figures 5 (a) and 5 (b), which includes the following five thermodynamic transformations:

- process 1-2, which corresponds to the feeding of the thermal working fluid, which consists of an adiabatic-isentropic compression process, which absorbs the external mechanical work.

- process 2-3, which corresponds to an isochoric process of adding heat from an external heat source, to heat the thermal working fluid with which a positive baro-thermal pulse is generated.

- process 3-4, which corresponds to an isothermal expansion process while absorbing heat from an external source, performing useful mechanical work by means of a pressure pulse, - process 4-5, which corresponds to an isochoric extraction cooling phase of heat according to a closed process with which a negative baro-thermal pulse is generated,

- process 5-1, which corresponds to a closed isothermal heat extraction process accompanied by the performance of useful mechanical work by contraction based on isothermal compression.

Description of preferred embodiments of the invention

The invention called "GAS TURBINE OPERATING WITH BARO-THERMAL PULSES AND OPERATION PROCEDURE", gives rise to the realization of innovative thermoelectric plants, for which the contributions derived from gas turbines with baro-thermal pulses with which Thermomechanical and thermoelectric plants are implemented, enabled to recover waste heat and thus increase the heat utilization factor based on the combination of a heat pump with one of the modules (40) or (41), which are represented in figures 16 and 17.

The power modules (40) and (41) are characterized by their ability to implement plant structures capable of recovering part of the residual heat rejected both by each of the aforementioned power modules, and by the plant structure in which it is installed. are integrated. In order to increase the heat utilization factor, two available heat supply modes (supply of power modules in parallel and supply of power modules in series) are developed to supply the plant modules (40) and (41). ) by means of heat transfer thermal fluid with input through duct (1) and return through duct (2), giving rise to the following plant structures formed by coupling modules of both type (40) and type ( 41):

- the structure of a plant formed by several power modules (40) coupled in parallel with respect to the heat transfer fluid used in feeding the modules of the type (40) shown in figure 11,

- the structure of a plant made up of several power modules (40) coupled in series with respect to the heat transfer fluid used to feed the modules of the type (40) shown in figure 12,

- the structure of a plant formed by power modules (41) coupled in parallel with respect to the heat transfer fluid used in supplying the modules of the type (41) shown in figure 13,

- the structure of a plant formed by power modules (41) coupled in series with respect to the heat transfer fluid used to feed the modules of the type (41) shown in figure 14.

In order to achieve a high heat utilization factor, a plant implemented based on the combination of a heat pump formed by an inverse Brayton cycle and at least one power module of the type (41) is developed, as shown in Figure 15, which includes the following components:

- heat exchanger (50) for thermal reinforcement to the heat pump, which captures heat from an external heat source to reinforce the supply of heating energy to the power module (41) through the duct (1),

- heat exchanger (51) for recovery of residual heat from the module (41) carried out by the suction of the compressor (53) of the inverse Brayton cycle corresponding to the heat pump,

- heat exchanger (52) for sub-cooling of the heat transfer thermal fluid from the module (41) to the thermal sink,

- compressor (53) of the inverse Brayton cycle that forms the heat pump,

- expander (54) of the inverse Brayton cycle that forms the heat pump.

- heat supply duct (55) by means of the thermal heat transfer fluid, - heat return duct (56) by means of the thermal heat transfer fluid,

Operation mode:

The plant implemented based on the combination of a heat pump formed by an inverse Brayton cycle and at least one power module of the type (41) as shown in figure 15, obeys the mode of operation according to which, the heat from an external heat source enters through the duct (55) to the heat exchanger (50) of thermal reinforcement to the heat pump (and returning to the external heat source through the return duct (56)), where it is transferred through the conduit (1) to the power module (41), returning through the conduit (2) to the heat exchanger (51) for recovery of residual heat, where it is cooled by heat transfer to the thermal fluid of heat transfer sucked by the compressor (53). The thermal fluid cooled in the waste heat recovery heat exchanger (51) passes to the expander (54) where it expands, producing mechanical work at the cost of cooling even more. The evacuation of the thermal fluid for heat transfer from the expander (54) passes to the heat exchanger (52) for sub-cooling of the thermal fluid for cooling the power module (41), returning to the compressor (53) through the heat exchanger (51) for recovery of residual heat from the module (41) carried out by the suction of the compressor (53) of the inverse Brayton cycle corresponding to the heat pump.

The scheme of parallel coupling of heat recovery systems for power modules (41) by means of a heat pump implemented under the inverse Brayton cycle, is shown in figure 16, where the heat supplied from an external heat source enters in parallel to each heat exchanger (50) of thermal reinforcement to the heat pump through the supply duct (55), leaving towards the external heat source through the return duct (56),

- heat return duct (56) by means of the heat transfer thermal fluid.

The series coupling scheme of heat recovery systems for power modules (41) by means of a heat pump implemented under the inverse Brayton cycle, is shown in figure 17, where the heat supplied from an external heat source enters in series to each heat booster module (50) to the heat pump through the heat supply duct (55) and returns through the heat return duct (56) to an external heat source.

Claims (11)

1. GAS TURBINE OPERATING WITH BARO-THERMAL PULSES, characterized in that the gas turbine structure operating with baro-thermal pulses is implemented under power modules of the type (40) whose structure is characterized by the gas turbine operating with baro-thermal pulses -thermal all of which includes at least the following components: - supply pipe (1) of the thermal heat transfer fluid, - return duct (2) of the heat transfer thermal fluid, -supply duct (3) of the heat extraction thermal fluid, - return duct (4) of the heat extraction thermal fluid, - high pressure working thermal fluid heater (10), - forced convection thermal working fluid recirculation compressor (11), - high pressure reservoir tank by heat addition at constant volume (12), - discharge valve (13) of the thermal working fluid at high pressure to the gas turbine operating at baro-thermal pulses (26), - working thermal fluid heater (14), - forced convection working thermal fluid recirculation compressor (15) - high pressure reservoir tank by addition of heat at constant volume (16), - discharge valve (17) of the thermal working fluid at high pressure to the gas turbine operating at baro-thermal pulses (26), - low pressure thermal working fluid cooler (29), - forced convection working thermal fluid recirculation compressor (19) - gas turbine operating at baro-thermal pulses (26) connected by shaft to an electric generator (27), - heat recovery unit (28) consisting of a heat exchanger to take advantage of the residual heat evacuated by the gas turbine operating at baro-thermal pulses (26), where the recovered heat is transferred through the inlet and outlet ducts (38 ) and (39) of the heat recovery unit (28), - thermal working fluid discharge valve (31) towards the high pressure tank (12), - thermal working fluid discharge valve (33) towards the high pressure tank (16), - fluid supply compressor thermal work (34). 2. OPERATING PROCEDURE OF THE GAS TURBINE OPERATING WITH BARO-THERMAL PULSES, characterized by one or more closed circuit gas turbines, and which are intended for thermo-mechanical and thermo-electric plants, where the pulsed gas turbines The baro-thermal turbines are coupled to each other by means of a shaft common to all the rotating machines of the plant, and where each one of the gas turbines operates intermittently based on the application of positive pressure pulses (high pressure of the thermal fluid of work) associated with the temperature of the thermal working fluid, where the thermal working fluid must be characterized by a high coefficient of adiabatic expansion and high specific heat, preferably helium, and where, the operating principle of the gas turbine operating to baro-thermal pulses is based on the fact that the addition of heat at constant volume and closed process to a thermal working fluid confined in a reservoir causes the increase of t corresponding temperature and pressure within the reservoir. If, under these conditions, instantaneous discharge of the thermal working fluid is caused to the gas turbine operating at baro-thermal pulses, the turbine responds with a rotational movement due to the torque exerted by the thermal working fluid when it expands. As the thermal working fluid expands adiabatically, its pressure and temperature decrease until reaching equilibrium between pressures (turbine inlet and outlet pressure). When the balance between inlet and outlet pressures is reached, the rotational torque is cancelled, and for the turbine to continue rotating and continue to perform mechanical work, it is The application of the next baro-thermal pulse is necessary and thus the cycle is repeated indefinitely, and where it includes at least another high pressure reservoir to relieve it during the inactive interval. 3. OPERATING PROCEDURE OF THE GAS TURBINE OPERATING WITH BAROTHERMAL PULSES, according to claim 2a, according to which, the mode of operation of the power module (40) operating with a gas turbine operating with barothermal pulses applied to the turbine inlet (26), operates in a closed circuit in such a way that the thermal working fluid is alternately transferred at low temperature and pressure from the low pressure thermal working fluid cooler (29) to the high-pressure reservoir tanks. (12) and (16), alternatively through the thermal working fluid discharge valve (31) towards the high-pressure reservoir (12), and alternatively through the thermal working fluid discharge valve (33) towards the high-pressure reservoir (16), driven and transferred by the thermal working fluid feed compressor (34), where the addition of heat to the thermal working fluid is carried out in such a way that within the Deposit s high pressure reservoirs (12) and (16) alternately lead to the process of adding heat at constant volume through recirculation of the thermal working fluid (to favor the transfer of value by forced convection) by the respective fluid heaters high pressure thermal working fluid (10) (14), where the heating process is due to the addition of heat to the heaters of the high pressure thermal working fluid (10) (14) through the supply line (1) of the heat transfer fluid from an external heat source and returning through the return duct (2) to the external heat source, and where, the isochoric addition of heat to the high pressure reservoirs (12) and (16) is carried out in an intermittent alternating manner in such a way that the addition of heat and subsequent conversion into mechanical work in the gas turbine operating at baro-thermal pulses (26) requires that: - when the high pressure reservoir (12) is find in the isochoric heating phase, the high pressure reservoir (16) is in the adiabatic expansion phase, for which the discharge valve (13) of the thermal working fluid at high pressure towards the gas turbine operating at baro pulses - thermal (26) is closed, while the discharge valve (17) of the thermal working fluid at high pressure towards the gas turbine operating at barothermal pulses (26) open; Y - when the high pressure reservoir (16) is in the isochoric heating phase, the high pressure reservoir (12) is in the adiabatic expansion phase, for which the discharge valve (17) of the thermal fluid of working at high pressure towards the gas turbine operating at barothermal pulses (26) is closed, while the discharge valve (13) of the thermal working fluid at high pressure towards the gas turbine operating at barothermal pulses (26 ) open, where, When one of the discharge valves of the high-pressure thermal working fluid (13) or (17) opens, a baro-thermal pulse is applied to the gas turbine operating at baro-thermal pulses (26) which expands adiabatically until reach equilibrium pressure (expansion pressure in the turbine equal to the pressure of the cooler (29) of the low-pressure thermal working fluid), and where, the thermal working fluid after adiabatic expansion in the gas turbine operating at baro-thermal pulses (26), still contains a significant amount of usable heat, which is likely to be partially recovered by the heat recovery unit (28) by through the inlet and outlet ducts (38) and (39), which consists of a useful heat exchanger to take advantage of the residual heat evacuated by the gas turbine operating at barothermal pulses (26), and where, the thermal working fluid at low pressure evacuated by the gas turbine operating at baro-thermal pulses (26) transfers heat to the heat transfer fluid in the heat recovery unit (28) passing to the low pressure reservoir (29) where it is cooled at constant pressure by means of a cooling fluid that enters through the conduit (3) to the low pressure reservoir (29), and returns through duct (4) transferring the cooling heat to a thermal sink at room temperature, and where, the thermal working fluid at low pressure and temperature contained in the low pressure reservoir (29) is sucked in by the feed compressor (34), thus closing the operating circuit to repeat the cycle indefinitely. 4. GAS TURBINE OPERATING WITH BARO-THERMAL PULSES, according to claim 1 where the gas turbine structure operating with baro-thermal pulses is implemented under a power module of the type (41) which includes at least the following components: - supply pipe (1) of the thermal heat transfer fluid, - return duct (2) of the heat transfer thermal fluid, - supply pipe (3) of the heat extraction thermal fluid, - return duct (4) of the heat extraction thermal fluid, - high pressure working thermal fluid heater (10), - forced convection thermal working fluid recirculation compressor (11), - high pressure reservoir tank by heat addition at constant volume (12), - discharge valve (13) of the thermal working fluid at high pressure to the gas turbine operating at baro-thermal pulses (26), - working thermal fluid heater (14), - forced convection working thermal fluid recirculation compressor (15) - high pressure reservoir tank by heat addition at constant volume (16) - discharge valve (17) of the thermal working fluid at high pressure to the gas turbine operating at baro-thermal pulses (26), - low pressure thermal working fluid cooler (18), - forced convection thermal working fluid recirculation compressor (19), - low pressure reservoir tank by heat extraction at constant volume (20), - Evacuation valve (21) of the thermal working fluid at low pressure of the gas turbine operating at baro-thermal pulses (26), - low pressure thermal working fluid cooler (22), - forced convection thermal working fluid recirculation compressor (23), - low pressure reservoir tank by heat extraction at constant volume (24), - Evacuation valve (25) of the thermal working fluid at low pressure of the gas turbine operating at baro-thermal pulses (26), - gas turbine operating at baro-thermal pulses (26) connected by shaft to an electric generator (27), - suction valve for the thermal working fluid (30) from the low pressure tank (20), - discharge valve for the thermal working fluid (31) towards the high pressure tank (12), - fluid suction valve thermal working fluid (32) from the low pressure tank (24), - thermal working fluid discharge valve (33) to the high pressure tank (16), - thermal working fluid supply compressor (34) . 5. OPERATING PROCEDURE OF THE GAS TURBINE OPERATING WITH BARO-THERMAL PULSES, according to claim 2a, according to which, the mode of operation of the power module (41) equipped with a gas turbine operating with baro-thermal pulses applied to the inlet and outlet of the turbine (26), it operates in a closed circuit in such a way that the thermal working fluid is alternately transferred at low temperature and pressure from the low pressure reservoir tanks (20) and (24) by the suction valves (30) and (32) of the feed compressor (34) towards the high-pressure reservoirs (12) and (16), through the discharge valves (31 and (33) of the feed compressor (34) , where, the thermal working fluid after adiabatic expansion in the gas turbine operating at baro-thermal pulses (26), is alternately evacuated by the evacuation valve (21) of the thermal working fluid at low pressure from the baro-thermal turbine. (26), or by the valve of evacuation (25) of the thermal working fluid at low pressure from the baro-thermal turbine (26) towards the respective low pressure reservoir tanks, both the low pressure reservoir tank by heat extraction at constant volume (20) and the low pressure reservoir by heat extraction at constant volume (24), and where, Inside the low pressure reservoir tanks (20) and (24), the heat extraction process takes place intermittently at constant volume by recirculating the thermal working fluid between (20) and (18) and between (24) and (22), to favor the transfer of heat by forced convection, where the heat is extracted from the respective coolers of the low pressure thermal working fluid (18) or (22), towards the thermal sink from where it is supplied through the duct supply (3) heat extraction cooling thermal fluid, returning through the return duct (4) to the thermal sink, and where, Within the low pressure reservoir tanks (20) and (24), the constant volume heat extraction process takes place intermittently by means of recirculation of the thermal working fluid (to favor heat transfer by forced convection) by the respective low pressure thermal working fluid coolers (18) or (22), where the cooling process is due to the alternative extraction of heat from the low pressure thermal working fluid coolers (18) (22) through the duct (3) supplying the heat extraction thermal fluid and returning through the return duct (4) of the heat extraction thermal fluid towards the thermal sink, and where, The mode of operation in the task of intermittent heat extraction from each of the low pressure reservoir tanks (20) and (24) requires that: - when the reservoir tank (20) is in the isochoric cooling phase, the evacuation valve (21) of the thermal working fluid at low pressure to the baro-thermal turbine (26) is closed and the reservoir tank (24 ) is in the phase of adiabatic contraction through the evacuation valve (25) of the thermal working fluid at low pressure and, - when the reservoir tank (24) is in the isochoric cooling phase, the evacuation valve (25) of the thermal working fluid at low pressure to the baro-thermal turbine (26) is closed and the reservoir tank (20 ) is in the phase of adiabatic contraction through the evacuation valve (21) of the thermal working fluid at low pressure, and where, when one of the pairs of valves (13) and (21) or (17) is opened ) and (25) simultaneously apply two baro-thermal pulses, one positive and one negative to the gas turbine operating at baro-thermal pulses (26), where the high-pressure working thermal fluid expands adiabatically and the thermal fluid The low pressure working chamber contracts adiabatically until pressure equilibrium is reached between the high pressure reservoir tank and the corresponding low pressure reservoir tank, and where, when the equilibrium pressure is reached within each of the respective reservoir tanks of the low-pressure thermal working fluid, both the low-pressure reservoir tank by heat extraction at constant volume (20), and the low-pressure reservoir tank By extracting heat at constant volume (24), the respective feeding phase of the low pressure thermal working fluid begins, being transferred by the thermal working fluid feeding compressor (34) to the high pressure reservoir tanks ( 12) and (16), completing the closed circuit of the described thermal cycle. 6. OPERATING PROCEDURE OF THE GAS TURBINE OPERATING WITH BARO-THERMAL PULSES, according to claim 2a, characterized by the modes of operation of the thermal cycle of the power module (41), which exhibits the ability to operate with several thermal cycles in in which the extraction of heat from the low pressure reservoir tanks (20) and (24) is carried out at a constant volume and where the options of operating with the thermal cycle characterized by carrying out the extraction of heat from the reservoir tanks of low pressure (20) and (24) at constant volume include: - thermal cycle whose mode of operation operates with adiabatic expansion and contraction obeys the following five thermodynamic transformations: - process 1-2, which corresponds to the feeding of the thermal working fluid, which consists of an adiabatic-isentropic compression process, which absorbs the external mechanical work, - process 2-3, which corresponds to an isochoric addition process of heat from an external heat source, to heat the thermal working fluid with which a positive baro-thermal pulse is generated, - process 3-4, which corresponds to an adiabatic-isentropic expansion process, which performs useful mechanical work by means of a pressure pulse, - process 4-5, which corresponds to an isochoric cooling phase by heat extraction according to a closed process with which a negative baro-thermal pulse is generated, - process 5-1, which corresponds to a contraction process based on adiabatic-isentropic compression, which performs a useful mechanical work. - the thermal cycle whose mode of operation operates with isothermal expansion and contraction which includes the following five thermodynamic transformations: - process 1-2, which corresponds to the feeding of the thermal working fluid, which consists of an adiabatic-isentropic compression process, which absorbs the external mechanical work, - process 2-3, which corresponds to an isochoric addition process of heat from an external heat source, to heat the thermal working fluid with which a positive baro-thermal pulse is generated, - process 3-4, which corresponds to an isothermal expansion process while absorbing heat from an external source, performing useful mechanical work by means of a pressure pulse, - process 4-5, which corresponds to an isochoric extraction cooling phase of heat according to a closed process with which a negative baro-thermal pulse is generated, - process 5-1, which corresponds to a closed isothermal heat extraction process accompanied by the performance of useful mechanical work by contraction based on isothermal compression. 7. OPERATING PROCEDURE OF THE GAS TURBINE OPERATING WITH BARO-THERMAL PULSES according to all claims claim 2a, according to which the power modules (40) and (41) are characterized by two modes of feeding the available heat : - supply of power modules in parallel and - supply of power modules in series, to supply heat to the plant modules (40) and (41) by means of the heat transfer thermal fluid with input through the duct (1) and return through the duct (2). 8. GAS TURBINE OPERATING WITH BARO-THERMAL PULSES, according to claim 4, characterized in that in order to achieve a high heat utilization factor, a plant implemented based on the combination of a heat pump formed by an inverse Brayton cycle is developed. and at least one power module of the type (41), which includes the following components: - heat exchanger (50) for thermal reinforcement to the heat pump, which captures heat from an external heat source to reinforce the supply of heating energy to the power module (41) through the duct (1), - heat exchanger (51) for recovery of residual heat from the module (41) carried out by the suction of the compressor (53) of the inverse Brayton cycle corresponding to the heat pump, - heat exchanger (52) for sub-cooling of the heat transfer thermal fluid from the module (41) to the thermal sink., - compressor (53) of the inverse Brayton cycle that forms the heat pump, - expander (54) of the inverse Brayton cycle that forms the heat pump, - heat supply duct (55) by means of the thermal heat transfer fluid, - heat return duct (56) by means of the thermal heat transfer fluid. 9. OPERATING PROCEDURE OF THE GAS TURBINE OPERATING WITH BARO-THERMAL PULSES, according to claim 2, characterized in that the plant implemented based on the combination of a heat pump formed by an inverse Brayton cycle and at least one power module of the type (41), obeys the mode of operation according to which, the heat from an external heat source enters through the duct (55) to the heat exchanger (50) of thermal reinforcement to the heat pump (and returning to the source of external heat through the return duct (56)), from where it is transferred through the duct (1) to the power module (41), returning through the duct (2) to the heat exchanger (51) for heat recovery. residual heat, where it is cooled by heat transfer to the heat transfer thermal fluid sucked in by the compressor (53). The thermal fluid cooled in the waste heat recovery heat exchanger (51) passes to the expander (54) where it expands, producing mechanical work at the cost of cooling even more. The evacuation of the thermal fluid for heat transfer from the expander (54) passes to the heat exchanger (52) for sub-cooling of the thermal fluid for cooling the power module (41), returning to the compressor (53) through the heat exchanger (51) for recovery of residual heat from the module (41) carried out by the suction of the compressor (53) of the inverse Brayton cycle corresponding to the heat pump. 10. OPERATING PROCEDURE OF THE GAS TURBINE OPERATING WITH BARO-THERMAL PULSES, according to claim 9, characterized by the parallel coupling technique of heat recovery systems for power modules (41) by means of a heat pump implemented under the reverse Brayton cycle, where the heat supplied from an external heat source enters in parallel to each heat booster heat exchanger (50) to the heat pump through the supply duct (55), exiting towards the external heat source through the return duct (56) 11. OPERATING PROCEDURE OF THE GAS TURBINE OPERATING WITH BARO-THERMAL PULSES, according to claim 9, characterized by the series coupling technique of heat recovery systems for power modules (41) by means of a heat pump implemented under the cycle Reverse Brayton, where the heat supplied from an external heat source enters in series to each heat booster module (50) to the heat pump through the heat supply pipe (55) and returns through the heat return pipe ( 56) to an external heat source.