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    • 专利摘要:
    Device for generating mechanical energy according to advanced thermodynamic cycles with temperature ranges delimited in the heat input, which comprises a condenser (1), a pump (2), a flow divider (3), a regenerator (4), a main heat supply equipment (8), an expander (7), a secondary regenerator (10), a secondary expander (9) and a flow-linking element (11) configuring an advanced thermodynamic cycle for the production of mechanical energy wherein the heat input temperature in the heating is delimited by the application and the above elements are configured to maximize energy production. (Machine-translation by Google Translate, not legally binding)
    公开号:ES2678215A1
    申请号:ES201830534
    申请日:2018-06-04
    公开日:2018-08-09
    发明作者:Antonio Rovira De Antonio；Jose Maria Martinez-Val Peñalosa
    申请人:Universidad Nacional de Educacion a Distancia UNED；Universidad Politecnica de Madrid；
    IPC主号:
    专利说明:

    DESCRIPTION

    DEVICE FOR GENERATION OF MECHANICAL ENERGY ACCORDING TO ADVANCED THERMODYNAMIC CYCLES WITH TEMPERATURE RANKS DEFINED IN THE HEAT CONTRIBUTION. 5


    Object and technical sector of the invention
    The invention falls within the field of thermodynamic cycles for the production of mechanical power, in turn convertible into electrical energy. Its use is of relevant interest in the energy industry, particularly when the calorific focus has limitations on the temperature range during the heat input, both in the maximum and the minimum, and the maximum temperatures are also reduced compared to usual in power plants with oxidation of a fuel. This makes it especially applicable to solar thermal energy and the recovery of residual heat from another installation or from another high-temperature thermodynamic cycle.

    Background of the invention
    One of the objectives of thermodynamics has been, since its inception, the study of machines for the production of mechanical energy from thermal energy. Not in vain, the first thermodynamic bases were established with the study of steam engines, which constituted the first successful thermal engines used at the industrial level.

    Since then and until now, numerous thermodynamic cycles have been proposed, which have been the core of the various thermal motors that are known. All of them have in common the following characteristics: a fluid volume is evolved cyclically by one or more mechanical equipment, thus the working fluid undergoes various thermodynamic processes among which, inevitably, at least one heat input process is found from a thermal source and at least a process of transfer of heat or cooling to a thermal sink, which is usually the ultimate environment.

    The fields of application of the most common thermal motors are the propulsion of vehicles and the generation of electrical energy. Although there are predominant cycles in every 35
    application, both devices or engines that materialize Otto, Diesel, Joule / Brayton and Rankine type cycles have been used with great success. Minority other devices have been used that follow other types of cycles, such as Stirling, Ericsson and Kalina among others. In the case of electricity generation, the use of combined cycle facilities is very frequent, which effectively combine two cycles, one of 5 high temperature Brayton type that works with air and another of low temperature Rankine type that works with water, both being thermally coupled by a heat recovery boiler.

    Two of the main factors for measuring the performance of a cycle are mechanical work 10 and thermodynamic performance, which is the ratio between the mechanical energy produced divided by the thermal energy supplied from the heat source. It is known that both parameters improve as the maximum temperature of the cycle grows and that, in addition, the maximum thermal efficiency attainable by a thermodynamic power cycle is limited and that it grows, specifically, according to the ratio between the average temperature of heat input and the average temperature of heat transfer increases (not being the arithmetic average but a weighted by the entropy variations).

    This is the reason why, in the various applications, the highest mechanically permissible working temperatures have been historically sought by materials for heat input and lower heat transfer temperatures, limited by ambient or medium temperature refrigerant.

    The natural application of the invention is the generation of mechanical energy for the production of electricity. In this field, Brayton cycles are absolute dominant today, thanks to gas turbines, and Rankine cycles based on steam turbines.

    Brayton-type cycles reach a very high maximum temperature, exceeding 1700 30 K. Although the average heat input temperature is lower than this value, because this contribution starts from the end of compression, the average temperature is high. The absolute minimum temperature is very low, since they take room air, but they also give heat to a medium high temperature because the gases of
    Exhaust are expelled around 800 or 900 K. With this technology yields greater than 40% are obtained.

    Rankine-type cycles reach average temperatures at the hottest hot spot, but they give heat at an average temperature that is very close to the ambient temperature and that condensation occurs at a very low constant temperature. In this case, the yields may exceed 50% in some cases.

    However, the ratio between the hot and cold average temperatures is not the only determining or limiting factor of the performance achieved by a thermodynamic cycle. 10 The thermodynamic irreversibilities in the processes also play an important role, among which those of the expander and compressor equipment, which tend to reduce with the evolution of technology, and those associated with heat transfer between the different equipment, which are reduced according to the temperature difference between the body that yields heat and that which absorbs it is small, for which it is ideal that the heat capacities (product of the mass flow rate by the specific heat) of the currents of the fluids involved be similar, being ideal that they are equal, saying in that case that the heat exchanger is balanced.

    At present, mainly due to the desire to use renewable sources of energy such as solar or geothermal as well as residual heats, there are applications where there is a moderate heat input temperature, since it is difficult to reach the usual temperatures after a combustion process In addition, on some occasions there may be conditions related to the minimum temperature during the heat input (for example, due to the use of thermal oils or molten salts 25 as heat transfer fluids in solar thermal power plants) or not exist (as could be in the case of geothermal sources and residual heat) or be very low or negligible, these conditions being those that are taken into account with the present invention, giving the thermodynamic cycles the appropriate modifications to improve their behavior, performance and work respectively in each case. 30

    The performance of Brayton cycles fed with a medium or low temperature thermal source is usually very low, even by introducing a regenerative exchanger or recuperator. Solutions have been proposed such as the one described in the Spanish patent application, P20120034, whose applicants are the same as the present one; patent ES 35
    0390877 A1 describing improvements for compression cooling and for the regeneration phase; or US 7401475 B2 and WO 0006876 A1, with which almost isothermal compressions and expansions are proposed.

    Rankine-type cycles working with organic fluids reach higher yields than Brayton cycles but are far from satisfactory values. These cycles use condensable fluids, meaning that they make use of the phase change in one of their processes. In this way, the heat transfer to the sink is done at a very low and constant temperature, due to the phase change, the average heat transfer temperature being very close to the ambient. In the heat input there is also a 10 phase change, so that during part of the heating there may be a constant temperature (if the pressure is lower than the critical point), although it is usually far from the maximum.

    To increase the average heat input temperature, the cycle is also regenerative in this case. The way to regenerate depends on the type of fluid. In this sense, it is possible to classify fluids according to three types:
    - Negative or moist: understanding as such those fluids for which the entropy of saturated steam always decreases with saturation pressure;
    - Isentropics: understood as such in the current state of the art to those whose saturated steam entropy practically does not vary with pressure except in the vicinity of the critical point and except at pressures several orders of magnitude below that of the critical point, which decreases;
    - positive or dry: understanding as such those whose entropy of saturated steam grows with pressure except in the vicinity of the critical point and except at pressures several orders of magnitude below that of the critical point, which decreases.

    For negative fluids, the thermodynamic state of the fluid at the outlet of the turbine or the expander is wet steam. Since the temperature is very low, exactly the minimum, the regeneration cannot be carried out with this thermal state and is therefore materialized by the extraction of a fraction of the flow in the turbine or the expander, at a higher temperature, and has as a mission to preheat the liquid before evaporation.

    For isentropic or positive fluids, the thermodynamic state of the fluid at the outlet of the turbine or the expander is dry steam, at a higher temperature than the minimum. The 35
    regeneration is carried out in a similar way to the Brayton cycles, taking advantage of the sensible heat of the expander steam. The objective is to preheat the liquid before the phase change.

    The regenerative Rankine cycles, subcritical or supercritical, have been very studied and 5 are being used frequently in low temperature applications. For example, EP 1801364 A1 proposes a device for materializing transcritical cycles; ES 2374874 T3 describes a device for the use of waste heat by means of Rankine cycles of organic fluids (ORC). On the other hand, Chen et al. in “A review of thermodynamic cycles and working fluids for the conversion of low-grade heat” 10 (Renewable and Sustainable Energy Reviews, 14 (2010), pp. 3059-3067, Elsevier) review Rankine, subcritical and supercritical cycles , with different organic work fluids, and Zhai et al. in “Categorization and analysis of heat sources for organic Rankine cycle systems” (Renewable and Sustainable Energy Reviews, 64 (2016), pp. 790-805, Elsevier) explain what are the important characteristics when designing Rankine cycles of organic fluids depending on the type of source and its limitations.

    Already regenerate in one way or another, with regeneration increases the ratio between average temperatures of contribution and heat transfer and improves performance. However, the irreversibilities get worse. If the regeneration materializes with a mixing exchanger the process is highly irreversible by the mixing. If it is with a contact exchanger there are two possibilities: the condensation of a certain fraction of steam extracted from the turbine or the expander to heat the liquid (for negative fluids) or the loss of sensible heat of the steam to heat the liquid (for fluids 25 isentropic or positive). In both cases, there are high temperature differences between the two currents, hot and cold, that cause irreversibility. In one case due to the condensation at constant temperature of one of the currents and in the other due to the thermal imbalance of the regenerator since the specific heat at constant pressure (Cp) of the vapor is significantly less than that of the liquid. 30

    To improve these characteristics, specific cycles have been devised and developed, based either on the Brayton cycle or on the idea of hybridizing both types, Rankine and Brayton, if the fluid is condensable.
     35
    In the case of being based on Brayton cycles, the variant is called a cycle with recompression or Feher cycle, and it is characterized by introducing two regenerators or recuperators instead of just one as well as a second compressor, the first's beep, located before the transfer of heat, so that the mass flow rate that is heated in the first regenerator is lower, which compensates for its higher Cp and balances the exchanger. The second 5 regeneration, with the built-in baipás, is standard. The cycle is described, for example, in the text “Fundamentals and Applications of Supercritical Carbon Dioxide (sCO2) Based Power Cycles” (Klaus Brun, Peter Friedman, Richard Dennis; Woodhead Publishing, ISBN: 9780081008041).
     10
    In the case of working with a condensable fluid, the background presented in ES2439619 A2 by the same applicants as in the present invention should be highlighted. Specifically, the cycle described follows the traditional supercritical and regenerative Rankine cycle but an additional compressor is available before the condensation of the fluid, which acts as the pump's bipas, so a 15 Brayton cycle is implemented in parallel. The regenerator or recuperator, only one in this case, is balanced because the higher Cp of the liquid is compensated by the lower mass expenditure. This configuration is called the Brayton-Rankine hybrid cycle.

    It is usual to associate each determined cycle with a specific maximum temperature. For example, when talking about maximum temperatures below 250 ° C, the most accepted solution is the Rankine cycles working with organic fluids, for their simplicity. For temperatures around 400 ° C, it is common to use conventional Rankine cycles working with water. For maximum temperatures of up to 800 ºC, the recompression candidate working with CO2 is postulated as the best candidate. For higher temperatures, conventional regenerative Brayton cycles are usually proposed.

    This association, although usual in the state of the art, is not the best, since the heating start temperature plays an important role. For example, for a maximum temperature of 400 ° C, perhaps the most appropriate cycle is not the same for heating from 100 ° C to 400 ° C as for another from 300 ° C to 400 ° C. Likewise, it is not the same to have the minimum heating temperature conditioner (the performance has to be maximized) than not to have it (the work has to be maximized), as it would sometimes happen with geothermal or residual heat sources, in which , the more heat is recovered from the source the better, for what is necessary 35
    Start heating the thermodynamic cycle fluid with a low temperature so that the residual source temperature is also low.

    The object of the invention is, precisely, to prescribe the materialization of the cycle and the most suitable fluids incorporating that nuance in its selection and, thus, to define solution and the variants that are advisable to adjust to the thermal source according to said requirement in temperature range

    General Description of the Invention
    As just mentioned, advanced thermodynamic cycles 10 and appropriate for the maximum working temperature and temperature range during heating are prescribed with the present invention, so that advanced thermodynamic cycles are associated with specific ranges of heating temperature. In particular, four cases are distinguished, for maximum medium or medium-high maximum temperatures combined with or without limitation in the minimum heating temperature, those of medium maximum temperature with and without limitation in the minimum supply temperature being of interest in the invention of heat and the maximum medium-high temperature with limitation on the minimum heat input temperature.

    In the event that the maximum temperature of heat input is average, understood as 20 such that it is below 450 ° C, and that there is no limitation for the minimum temperature of the heat input or is low, below 120 ° C, said conditions being characteristic of heat recovery, residual or not, of medium temperature, an installation is prescribed that includes:
    - a fluid that evolves in the advanced thermodynamic cycle, called working fluid 25, which is of the condensable type and of the so-called isentropics, preferably propane, isobutane or sulfur hexafluoride;
    - a condenser for the condensation of the working fluid, cooled by a cooling fluid such as air, water or any other, whose temperature at the entrance of the equipment is marked by the environment; 30
    - a drive pump to circulate and pressurize the working fluid in the liquid phase leaving the condenser;
    - a main heat input device to the working fluid, thermally fed by a heating fluid that comes from a thermal source;
    - two expansion machines or turbines that expand the working fluid in the gas phase, called the expansion machine or turbine and secondary expansion machine or secondary turbine, respectively;
    - two heat exchangers type regenerator, called regenerator and secondary regenerator, each with two circuits, the primary that receives 5 heat and the secondary that gives it;
    - a primary and secondary flow rate dividing element that divides the total workflow flow into separate, primary and secondary flows;
    - a primary and secondary flow joint element;
    - A transmitter or transformer element of the mechanical power produced as 10 can be an axis or an electric generator, among others.

    The indicated components are connected as follows:
    - the output of the condenser is connected to the input to the discharge pump;
    - the outlet of the discharge pump is connected to the 15-flow primary and secondary flow dividing element, which divides the current into two primary and secondary flows;
    - the first output of the primary and secondary flow flow dividing element, through which the primary flow flows, is connected to the regenerator by the input of its primary circuit; twenty
    - The output of the primary circuit of the regenerator is connected to the conduit or inlet manifold of the main heat input equipment, which is fed by the heat fluid from the thermal source;
    - the duct or outlet manifold of the main heat input equipment is connected to the inlet of the expander machine; 25
    - the output of the expander machine is connected to the secondary regenerator by the input of its secondary circuit;
    - the output of the secondary circuit of the secondary regenerator is connected to the primary and secondary flow flow connection element by the first of its inputs; 30
    - the second output of the primary and secondary flow flow divider element, through which the secondary flow flows, is connected to the secondary regenerator by the input of its primary circuit;
    - the output of the primary circuit of the secondary regenerator is connected to the secondary expander machine; 35
    - the output of the secondary expander machine is connected to the regenerator by the input of its secondary circuit;
    - the output of the secondary circuit of the regenerator is connected to the primary and secondary flow flow connection element by its second input;
    - the output of the flow joint element is connected to the input of the condenser;
    Thus, during the evolution of the advanced thermodynamic cycle the following processes take place:
    - The primary flow is heated in the gas phase and at supercritical pressure in the main heat input equipment from the regenerator outlet, at a low temperature, which allows efficient use of residual heat, and up to the maximum heat input temperature ;
    - immediately afterwards it expands in the expander machine, which performs the mechanical work on the outside;
    - then heat is transferred to the secondary flow in the secondary regenerator; fifteen
    - the secondary flow, after receiving said heat input in the secondary regenerator, expands in the secondary expander machine, which performs mechanical work on the outside;
    - then it gives heat to the primary flow in the regenerator;
    - both flows already expanded and having ceded heat in the respective regenerators are mixed and the mixture is sent to the condenser;
    - and at the condenser outlet the total flow is pumped and divided into the two flows, primary and secondary, to send them the respective heat inputs mentioned in the main heat input and secondary regenerator equipment, respectively. 25
    In the event that the maximum temperature of heat input is medium-high, understanding that it is less than 750 ° C, and that there is a minimum temperature of the heat input, greater than 270 ° C, said conditions being typical of the plants solar concentrators with high concentration (with heliostat fields and central tower receiver), an installation comprising the same components as in the previous case is prescribed, with the exception that a closed-loop gas turbine is included, preferably operating with air pressurized or pressurized carbon dioxide, which requires a refrigerator to materialize the cold focus said gas turbine.

    The closed-cycle gas turbine is thermally fed by the heating fluid that comes from the thermal source and cooled thanks to its refrigerator, which physically coincides with the main heat input equipment of the advanced cycle, so the gas turbine in Closed cycle is cooled as the working fluid of the advanced cycle is heated. 5

    The previous components are connected as follows:
    - the output of the condenser is connected to the input to the discharge pump;
    - the outlet of the impulse pump is connected to the primary and secondary flow flow dividing element, which divides the current into two flows, primary and secondary;
    - the first output of the primary and secondary flow flow dividing element, through which the primary flow flows, is connected to the regenerator by the input of its primary circuit;
    - the output of the primary regenerator circuit is connected to the conduit or input manifold of the main heat input equipment, the thermal source that feeds the equipment being the expanded gas coming from the closed-loop gas turbine and the turbine remaining of refrigerated gas thanks to the working fluid, which is heated;
    - the duct or outlet manifold of the main heat input equipment is connected to the inlet of the expander machine;
    - the output of the expander machine is connected to the secondary regenerator by the input of its secondary circuit;
    - the output of the secondary circuit of the regenerator is connected to the primary and secondary flow flow connection element by the first of its inputs; 25
    - the second output of the primary and secondary flow flow divider element, through which the secondary flow flows, is connected to the secondary regenerator by the input of its primary circuit;
    - the output of the primary circuit of the secondary regenerator is connected to the secondary expander machine; 30
    - the output of the secondary expander machine is connected to the regenerator by the input of its secondary circuit;
    - the output of the secondary circuit of the regenerator is connected to the primary and secondary flow flow connection element by its second input;
    - the output of the primary and secondary flow flow connection element is connected to the condenser input.
    Thus, during the evolution of the advanced thermodynamic cycle the following processes take place:
    - The primary flow, pre-heated in the regenerator, completes its heating in 5 gas phase up to the maximum temperature and at supercritical pressure thanks to the heat transfer by the closed-loop gas turbine in the main heat input equipment heat input;
    - immediately afterwards it expands in the expander machine, which performs the mechanical work on the outside; 10
    - then heat is transferred to the secondary flow in the secondary regenerator;
    - the secondary flow, after receiving said heat input in the secondary regenerator, expands in the secondary expander machine, which performs mechanical work on the outside;
    - then it gives heat to the primary flow in the regenerator; fifteen
    - both flows, primary and secondary, expanded and having ceded heat in the respective regenerators, are mixed and the mixture is sent to the condenser;
    - and at the output of the condenser the total flow is pumped and divided into the two flows, primary and secondary, to send them the respective heat inputs mentioned in the main and regenerative heat input equipment, respectively. twenty

    As a variant of the two configurations described, the suppression of the regenerator is prescribed, for which the primary flow from the first output of the primary and secondary flow flow divider element is connected to the input manifold of the main heat input element , and the output of the secondary expander machine 25 is connected to the primary and secondary flow flow joint element by its second inlet.

    In the event that the maximum temperature of heat input is average, understanding that it is less than 450 ° C, and that there is a minimum temperature of heat input, 30 greater than 290 ° C, these conditions being the usual ones in the power plants solar concentrators with medium concentration (with fields of parabolic trough collectors or linear Fresnel reflectors), an installation is prescribed that includes the same components as in the first case with the exceptions that the secondary expander and secondary regenerator are suppressed and it incorporates 35
    a compressor machine or compressor. The previous components are connected as follows:
    - the output of the condenser is connected to the input to the discharge pump;
    - the output of the impulse pump is connected to the regenerator by the input of its primary circuit; 5
    - the output of the regenerator's primary circuit is connected to the main flow balancing and balancing element by the first of its inputs;
    - the outlet of the main flow and balance flow union element is connected to the inlet conduit or manifold of the main heat input equipment, which is fed by the heat fluid from the thermal source; 10
    - the duct or outlet manifold of the main heat input equipment is connected to the inlet of the expander machine;
    - the output of the expansion machine is connected to the regenerator by the input of its secondary circuit;
    - the output of the secondary circuit of the regenerator is connected to the main flow balancing and balancing element, which divides the flow into two flows, main and the balancer;
    - the first output of the main flow and balancing flow division element, through which the main flow flows, is connected to the condenser inlet; twenty
    - the second output of the main flow and balancing flow division element, through which the balancing flow flows, is connected to the compressor machine inlet;
    - the output of the compressor machine is connected to the main flow and balance flow union element by the second of its inputs; 25

    In this way, the components are connected forming a Brayton-Rankine hybrid cycle, in which the following processes take place:
    - the working fluid is heated in the gas phase and at supercritical pressure in the main heat supply equipment from the outlet of the 30-flow connection element of the main and balancer flows, with a temperature range covering the minimum heat input temperature up to the maximum heat input temperature;
    - immediately afterwards it expands in the expander machine, in which it performs the mechanical work on the outside;
    - Then it gives up heat circulating in the secondary circuit of the regenerator and consequently cools;
    - and at the output of the secondary regenerator circuit, the flow is divided into two flows, the main and the balancer;
    - the balancing flow is directed to the compressor machine, which is connected at its outlet with the flow joint element;
    - the main flow is directed to the condenser, where it condenses at a setpoint temperature higher than that of the cooling medium, giving heat to the environment, the condensed liquid being subsequently pumped into the discharge pump;
    - the main flow, after being pressurized, is regeneratively heated in the primary circuit of the regenerator with the heat given by all the gas that is cooled in the secondary circuit of said regenerator, and finally reaches the joint element with the equilibrium flow; fifteen
    - in said connecting element said main flow is joined with the equilibrium flow that has been compressed in the gas phase, both entering as a single flow in the main heat supply equipment.

    The application is also characterized by the type of thermal source. The heat supplied 20 in main heat input equipment comes from one of the following sources:
    - a solar thermal energy collection facility,
    - of geothermal origin,
    - of any type of combustion,
    - of nuclear reactions and radiation, 25
    - of the heat transferred from a higher temperature Brayton cycle, in its cold branch, than the main heat input temperature of this cycle.

    Brief description of the figures
    Figure 1 shows the prescribed configuration for the case of maximum temperature of 30 medium heat input and that there is no limitation on the minimum input temperature or is low. Figures 2 and 3 show the prescribed configurations for cases where the maximum temperature of the heat input is, respectively, medium-high or medium and if there is a limitation on the minimum temperature of said contribution.
    To facilitate the understanding of the figures and of the preferred embodiments of the invention, the relevant elements thereof, which appear in the figures, and the characteristic thermodynamic points are listed below:
    1. Condenser, cooled by a cooling fluid such as air, water or any other. 5
    2. Drive pump that circulates and pressurizes the working fluid in liquid phase.
    3. Flow dividing element of the primary and secondary flows.
    4. Regenerative heat exchanger or regenerator.
    5. Electric generator.
    6. Shaft of rotary machines and electric generator. 10
    7. Expansion machine or turbine.
    8. Main heat input equipment to the fluid thermally fed by a heating fluid.
    9. Secondary expander machine or secondary turbine.
    10. Secondary regenerative heat exchanger or secondary regenerator, whereby the secondary flow heats the primary.
    11. Element of union of flows of the primary and secondary flows.
    12. Gas turbine in closed cycle with its refrigerator (13).
    13. Gas turbine cooler in closed cycle (12).
    14. Main flow divider element and balancer. twenty
    15. Main and balancing flow joint element.
    16. Compressor or compressor machine.

    In addition to the above identifiers, which refer to physical elements of the circuit to materialize the invention, the following alphabetic-numerical labels are used in the drawings to identify different thermodynamic states of the working fluid and their respective flows:
    P1. Flow to the condenser outlet (1) and pump inlet (2).
    P2 Flow at the pump outlet (2).
    P2 ’. Primary flow at the output of the primary and secondary flow flow dividing element (3) through the first of its outputs and input to the secondary regenerator (10) through the primary circuit (Figures 1 and 2).
    P2 ”. Secondary flow at the output of the primary and secondary flow flow dividing element (3) through the second of its outputs and input to the regenerator (4) by its 5 primary circuit (Figures 1 and 2).
    P3 ’. Flow at the entrance to the main heat input equipment (8) (figures 1 and 2).
    P3p Main flow at the outlet of the regenerator (4) through its primary circuit and input to the main flow balancing and balancing element (15) by the first of its inputs (Figure 3). 10
    P3e Balancing flow at the outlet of the compressor machine (16) and input to the main flow balancing and balancing element (15) for the second of its inputs (figure 3).
    P3 Total flow at the entrance of the main heat input equipment (8) (figure 3).
    P4 ’. Primary flow at the outlet of the main heat input equipment (8) and input to the expander machine (7) (figures 1 and 2).
    P4 ” Secondary flow at the entrance of the secondary expander machine (9) (Figures 1 and 2).
    P4 Total flow at the outlet of the main heat input equipment (8) and entrance to the expander machine (7) (Figure 3). twenty
    P5 ’. Primary flow at the outlet of the expander machine (7) and input to the secondary regenerator (10) through its secondary circuit (Figures 1 and 2).
    P5 ”. Secondary flow at the outlet of the secondary expander machine (9) (Figures 1 and 2).
    P5 Total flow at the outlet of the expander machine (7) and input to the regenerator (4) 25 through its secondary circuit (figure 3).
    P6 ’. Primary flow at the output of the secondary regenerator (10) through its secondary circuit and input to the primary and secondary flow flow connection element (11) through the first of its inputs (Figures 1 and 2).
    P6 ". Secondary flow at the outlet of the regenerator (4) through its secondary circuit and 30 input to the primary and secondary flow flow connection element (11) through the second of its inputs (Figures 1 and 2).
    P6 Total flow at the outlet of the regenerator (4) through its secondary circuit (figure 3).
    P6p. Main flow at the output of the main flow balancing and balancing element (14) through the first of its outputs and input to the condenser (1) (Figure 3).
    P6e Balancing flow at the output of the main flow balancing and balancing element (14) through the second of its outputs and entering the compressor machine 5 (16) (Figure 3).

    Description of a preferred embodiment
    Preferably, propane is selected as a working fluid in advanced thermodynamic cycles, due to its high availability and good performance, although any isentropic fluid is susceptible to being used, among which the isobutane and sulfur hexafloride are additionally highlighted .

    Preferred embodiments of the invention, although not unique or limiting, are described below. fifteen

    As an example of materialization in the event that the maximum temperature of heat input is medium and that there is no minimum temperature of heat input, stand out the heat recovery facilities, residual or not, of medium temperature. In said example, the maximum temperature of the gas stream from which it is intended to recover heat is around 400 ° C.

    In that case, it is prescribed that propane condenses in the condenser (1) at a temperature of 35 ° C, which corresponds to a saturation pressure of 12.2 bar. In the feed pump (2) the working pressure is increased up to 175 bar, so that they work in supercritical conditions (the critical pressure of propane is 42.5 bar).

    The main flow, approximately 60% of the total, is heated in the regenerator (4) to the temperature of 334 K and is introduced into the main heat input equipment (8) 30 where it is heated to a temperature of 650 K. For this, the heat transfer fluid is introduced at 673 K and exits at 339 K.

    The main flow is expanded in the expander machine (7) and, after expansion, it is sent to the secondary regenerator (10) at a temperature of 541 K, where it heats the secondary flow, which is approximately 40% of the total, up to temperature of 536 K. After said heating, the secondary flow expands in the secondary expansion machine 5 (9), where it leaves at a temperature of 416 K, and is used to heat the primary flow in the regenerator (4).

    The primary and secondary flows are mixed at the output of the respective regenerators and introduced into the condenser (1) at a temperature of 321 K. 10

    As an example of materialization in the event that the maximum temperature of heat input is medium-high and that there is a minimum temperature of heat input, the installations of high concentration solar thermal power plants using molten salts as heat transfer fluid stand out . In this example, the maximum temperature of the salts is around 600 ° C, there is also a minimum temperature to prevent freezing, taking a value around 270 ° C.

    In that case, it is prescribed that the heat transfer fluid, the molten salt, be sent to the thermal generator of the closed-loop gas turbine (12). This works with air or pressurized carbon dioxide, among other fluids, the latter being selected for its best performance. The temperature of the gas at the entrance to the compressor is specified in 348 K, since it has been cooled in the refrigerator (13) of the closed-loop gas turbine (12) by the working fluid, propane. The compression ratio of the 25-cycle closed-loop gas turbine (12) is specified at 8.5: 1, and the maximum temperature of the carbon dioxide after heating by molten salts will be less than the maximum allowable by these, by Example 20K smaller.

    As for the advanced cycle, it is prescribed that the propane condenses in the condenser 30 (1) at a temperature of 35 ° C, which corresponds to a saturation pressure of
    12.2 bar In the feed pump (2) the working pressure is increased up to 175 bar, so they work in supercritical conditions.

    The main flow, approximately 60% of the total, is heated in the regenerator (4) to the temperature of 343 K and is introduced into the main heat input equipment (8) 5 where, at the same time it is heated to setpoint temperature, 613 K, cools the gas turbine in a closed cycle (12).

    The main flow expands in the expander (7) and, after expansion, is sent to the secondary regenerator (10) at a temperature of 499 K, where it heats the secondary flow 10, which is approximately 40% of the total, up to a temperature of 494 K. After said heating, the secondary flow expands in the secondary expander (9), where it leaves at a temperature of 363 K, and is used to heat the primary flow in the regenerator (4).
     fifteen
    The primary and secondary flows are mixed at the output of the respective regenerators and introduced into the condenser (1) at a temperature of 324 K.

    As an example of materialization in the event that the maximum temperature of heat input is medium and that there is a minimum temperature of heat input, there are 20 installations of medium concentration solar thermal power plants that use thermal oil as heat transfer fluid. In this example, the maximum oil temperature is around 400 ° C, there is also a minimum temperature, which takes a value around 290 ° C.
     25
    It is prescribed that propane condenses in the condenser (1) at a temperature of 35 ° C, which corresponds to a saturation pressure of 12.2 bar. In the feed pump (2) the working pressure is increased up to 175 bar, so they work in supercritical conditions.
     30
    The equilibrium flow is set at 25% of the total, so the main one is 75%. This main flow is preheated in the regenerator (4) to a temperature of 533 K. The equilibrium flow, which comes from the compressor machine (16) to 473 K, is mixed with the main and, both, are heated in the equipment main heat input (8) up to 650 K. After this heating the total flow expands in the expander machine (7), from which 5 leaves at a temperature of 537 K and is introduced into the regenerator (2) to preheat the flow principal. At the outlet of the regenerator (2), the total flow is 325 K and is divided into two flows in the flow divider element of the main and balancer flow (14), the main flow that goes to the condenser (1) and the balancer that goes to the compressor machine (16). 10
    权利要求:
    Claims (4)
    [1]

    1. Device for generating mechanical energy according to advanced thermodynamic cycles with temperature ranges defined in the heat input comprising:
    - a fluid that evolves in the advanced thermodynamic cycle, called working fluid 5, which is of the condensable type and of the so-called isentropics, preferably propane, isobutane or sulfur hexafluoride;
    - a condenser (1) for the condensation of the working fluid, cooled by a cooling fluid such as air, water or any other, whose temperature at the entrance of the equipment is marked by the environment; 10
    - a drive pump (2) for circulating and pressurizing the working fluid in the liquid phase leaving the condenser (1);
    - a main heat input device (8) to the working fluid, thermally fed by a heating fluid;
    - two expansion machines or turbines that expand the working fluid in gas phase 15, called the expansion machine or turbine (7) and secondary expansion machine or secondary turbine (9), respectively;
    - two heat exchangers type regenerator, called regenerator (4) and secondary regenerator (10), each with two circuits, the primary one that receives heat and the secondary one that yields it; twenty
    - a primary and secondary flow rate dividing element (3) that divides the total workflow flow into separate, primary and secondary flows;
    - a primary and secondary flow joint element (11);
    - a transmitter or transformer element of the mechanical power produced such as an axis (6) or an electric generator (5), among others; 25
    characterized in that the maximum heat input temperature is less than 450 ° C and that there is no limitation for the minimum heat input temperature or is low, less than 120 ° C, and the above components are connected as follows:
    - the output of the condenser (1) is connected to the input to the drive pump (2); 30
    - the output of the discharge pump (2) is connected to the primary and secondary flow flow dividing element (3), which divides the current into two primary and secondary flows;
    - the first output of the primary and secondary flow flow dividing element (3), through which the primary flow flows, is connected to the regenerator (4) by the input of its primary circuit;
    - The output of the primary circuit of the regenerator (4) is connected to the conduit or inlet manifold of the main heat input equipment (8), which is fed 5 by the heat fluid from the thermal source;
    - the duct or outlet manifold of the main heat input equipment (8) is connected to the inlet of the expander machine (7);
    - the output of the expander machine (7) is connected to the secondary regenerator (10) by the input of its secondary circuit; 10
    - the output of the secondary circuit of the secondary regenerator (10) is connected to the primary and secondary flow flow connection element (11) by the first of its inputs;
    - the second output of the primary and secondary flow flow divider element (3), through which the secondary flow flows, is connected to the secondary regenerator 15 (10) by the input of its primary circuit;
    - the output of the primary circuit of the secondary regenerator (10) is connected to the secondary expander machine (9);
    - the output of the secondary expander machine (9) is connected to the regenerator (4) by the input of its secondary circuit; twenty
    - the output of the secondary circuit of the regenerator (4) is connected to the flow connection element (11) by its second input;
    - the output of the primary and secondary flow flow connection element (11) is connected to the condenser input (1).
     25
    [2]
    2. Device for generating mechanical energy according to advanced thermodynamic cycles with temperature ranges delimited in the heat input according to claim one characterized in that it comprises the same components described in claim one with the exception that a cycle gas turbine is included closed (12), preferably operating with pressurized air or pressurized carbon dioxide, which requires a refrigerator (13) to materialize the cold focus said gas turbine; the maximum heat input temperature is less than 750 ° C; the minimum during thermal input is greater than 270 ° C; The closed-cycle gas turbine (12) is thermally fed by the heating fluid that comes from the thermal source and cooled thanks to its refrigerator (13), which physically coincides with the
    main heat input equipment (8) of the advanced cycle, whereby the working fluid of the advanced cycle is heated with the expanded gas coming from the closed-loop gas turbine (12) and the closed-loop gas turbine remaining refrigerated thanks to the working fluid, which is heated.
     5
    [3]
    3. Device for generating mechanical energy according to advanced thermodynamic cycles with temperature ranges delimited in the heat input according to claim one or two, characterized in that the regenerator (4) is suppressed, for which the primary flow from the first outlet of the primary and secondary flow flow divider element (3) is connected to the input manifold of the main heat input element (8), and the output of the secondary expander machine (9) is connected to the connection element of primary and secondary flow rates (11) for its second entry.

    [4]
    4. Device for generating mechanical energy according to advanced thermodynamic cycles 15 with temperature ranges delimited in the heat input according to claim one characterized in that it comprises the same components described in claim one with the exceptions that the secondary expander machine is suppressed ( 9) and the secondary regenerator (10) and a compressor or compressor machine (16) is incorporated; the maximum heat input temperature is less than 450 ° C; the minimum during thermal input is greater than 290 ° C; and the previous components are connected as follows, forming a Brayton-Rankine hybrid cycle:
    - the output of the condenser (1) is connected to the input to the drive pump (2); 25
    - the output of the drive pump (2) is connected to the regenerator (4) by the input of its primary circuit;
    - the output of the primary circuit of the regenerator (4) is connected to the main flow balancing and balancing element (15) for the first of its inputs; 30
    - the outlet of the main flow and balance flow joint element (15) is connected to the inlet conduit or manifold of the main heat input equipment (8), which is fed by the heat fluid from the thermal source;
    - the duct or outlet manifold of the main heat input equipment (8) is connected to the inlet of the expander machine (7); 35
    - the output of the expander machine (7) is connected to the regenerator (4) by the input of its secondary circuit;
    - the output of the secondary circuit of the regenerator (4) is connected to the main flow balancing and balancing element (14), which divides the flow into two flows, main and the balancer; 5
    - the first output of the main flow and balancer flow division element (14), through which the main flow flows, is connected to the condenser inlet (1);
    - the second output of the main flow and balancing flow dividing element (14), through which the balancing flow flows, is connected to the input of the compressor machine (16);
    - The output of the compressor machine (16) is connected to the main flow and balance flow connection element (15) by the second of its inputs.
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    同族专利:
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    ES2678215B2|2019-11-07|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    SU1090899A1|1982-05-05|1984-05-07|Краснодарский политехнический институт|Method of operating heat-electric generation plant|
    US6098398A|1996-09-30|2000-08-08|Mitsubishi Heavy Industries, Ltd.|Low temperature hydrogen combustion turbine|
    US20150267567A1|2013-06-07|2015-09-24|Her Majesty The Queen In Right Of Canada As Represented By The Minister Of Natural Resources|Hybrid rankine cycle|
    JP2015129486A|2014-01-08|2015-07-16|株式会社東芝|Steam turbine plant|
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