RU2125171C1 - Power generating plant and method of its operation - Google Patents

Abstract

FIELD: heat power engineering; power generating complexes delivering electric and heat energy of preset parameters to consumers. SUBSTANCE: when power generating plant operates at maximum or higher delivery of heat energy to consumer, compressed working medium is directed into heater by-passing heat exchanger-recuperator. Power of heater is increased according to enlarged temperature range of heated working medium. heat exchanger-recuperator is connected at heated side to heat takeoff for technical purpose and/or consumer heat supply. For this purpose at least one circulation heat exchange circuit is used. When power generating plant operates at minimum or reduced delivery of heat energy to consumer, compressed working medium is passed as heated medium through heat exchanger-recuperator. Power rating of heater installed behind heat exchanger-recuperator is reduced according to reduced temperature range of heated working medium. EFFECT: increased efficiency of plant. 7 cl, 12 dwg

Description

 The invention relates to the field of heat power engineering (including nuclear technology) and can be used in power plants or energy technology complexes in which electrical and thermal energy of specified parameters are simultaneously produced.

 One of the most important problems of the fuel and energy complex is the pursuit of an active energy-saving policy that ensures the achievement of the necessary effect with minimal energy costs and minimal metal consumption. In industry, the simplest example of energy conservation is the use of low-grade heat, which is a waste of a large number of technologies (heat supply, etc.). In addition, the rational use of medium and high temperature heat is very effective, especially in metallurgy, chemical industry, coal gasification, oil refining and building materials industry.

The current structure of consumption of fuel and energy resources in Russia is characterized by the following approximate data: lighting - 0.5%, power processes - 25%, high-temperature processes (over 400 ^o C) - 25%, medium and low temperature processes (respectively 100 - 400 ^o C and 100 - 150 ^o C) - 49.5% (see, for example, the book "Heat Engineering", edited by V. I. Krutov, M, "Engineering", 1986, p. 392). One of the most effective means of increasing the efficiency of fuel consumption is the transition to integrated energy-technological methods of using fuel: to extract all valuable components of the fuel with the obligatory combination of the process of burning part of the fuel for the production of heat and electric energy with various technological processes.

 Energy consumption for lighting and drives of mechanisms and machines (electric motors) determine the need for electricity. Energy costs for high-temperature processes form the necessary consumption of fuel, electricity and steam. Energy costs for medium temperature processes determine fuel and steam consumption. For low-temperature processes, as a rule, hot water is used as a heat carrier.

 A known method of operating a power plant (EA) that produces electrical and thermal energy of specified parameters (see, for example, the book "Technical Thermodynamics". V.D. Kirillin et al., M, Energoatomizdat, 1983, pp. 323 - 325 , Fig. 11.34), in which the liquid phase of the installation’s working fluid (for example, water) is compressed in the circulator of the installation (pump) and sent to a heat source where it is heated, as a result of which the water turns into the working medium of the installation - dry saturated or superheated steam which is then expanded in a turbine driving an electric generator, after which the steam spent in the turbine is supplied to a surface heat exchanger-condenser, where the steam is condensed at a saturation pressure that provides heating to the required temperature of the condenser cooling water, which transfers thermal energy to the consumer, for example, for heat supply, and then the condensate of the plant’s working fluid again compressed in a circulator and fed to the heat source of the installation.

At the same time, this method of operating electric power plants has an inherent disadvantage inherent in the well-known steam turbine cogeneration plants (CHP), which produce electric and thermal energy. The heat energy supplied to the consumer from steam turbine thermal power plants is characterized by a limitation on the maximum temperature of the coolant (about 200 ^o C), which accordingly restrains the power of the generated heat energy and also prevents its use in high-temperature industrial and technological processes. In connection with the foregoing, the task of developing high-temperature heating systems is particularly urgent. This problem can be solved with the help of gas turbine power plants, the positive features of which are compared with steam turbine ones: 1) insignificant need for cooling water, 2) the possibility of using higher temperatures of the working fluid, 3) lower unit weight and metal consumption per unit power, 4) the ability to quickly start and boost power.

 The indicated advantages are met by the following known methods of operating power plants that produce electrical and thermal energy of specified parameters. For example, there is a known method of operating EI, in which a gaseous working fluid (for open-cycle gas turbine units - atmospheric air) is compressed in one compressor or at least two compressors with intermediate cooling and then fed to a heat source, where it is heated to the maximum operating temperature and then, with the release of a part of the internal energy of the working fluid, it is expanded in a turbine that drives an electric generator, then the exhaust gas in the turbine is cooled in a heat exchanger providing heating water entering the heat consumer, and then released into the chimney or dry cooling tower (see, for example, the book "Heating Systems", L.S. Khrilev, M, Energoatomizdat, 1988, p. 237), as well as the book "Thermal Engineering Handbook", ed. V.I. Yurenev and P. D. Lebedev, M, Energy, 1975, vol. 1, p. 495).

 In addition, there is a known method of operating EI, in which, in contrast to the above, the transfer of thermal energy to the consumer (for technological processes of chemical, oil refining and metallurgical industries) is ensured by selecting part of the flow rate of the working fluid of higher parameters from the gas turbine between its stages (see ., for example, the book "Heat Engineering", as amended by V.I. Krutov, M, Mechanical Engineering, 1986, p. 193, Fig. 4.15d).

 To ensure the transfer of high parameters of thermal energy to the consumer (while generating electric energy), there is also a well-known method of operating a power plant, in which the gaseous working medium of a closed-cycle plant (for example, inert gas - helium) is compressed in a compressor, then fed to a heat source (active zone of a high-temperature gas-cooled nuclear reactor) and then cooled in a surface heat exchanger, the heated side of which (for example, with the same coolant - gel (iem) provides the transfer of thermal energy to the consumer, after which it is expanded in a turbine that drives the electric generator, and then sent again for compression and circulation of the working fluid to the compressor (see, for example, the book "Heat Engineering", as amended by V. I. Krutov, M, Engineering, 1986, p. 389, Fig. 12.9).

At the same time, the indicated general methods of operation of power plants based on gas turbine plants of open (open) or closed cycles have the following general disadvantages, which reduce economy and lead to a decrease in their environmental operation:
1) the value of the absolute electrical efficiency (COP) of the plants is sufficiently low for the current level of energy,
2) large losses of thermal energy (and, accordingly, fuel) during the periods of operation of power generating plants with minimal (reduced) heat energy output to the consumer, which significantly reduces the overall (annual) heat utilization factor of the fuel of the plants and, accordingly, increases the thermal "pollution" of the environment.

 The first of the aforementioned drawbacks is related to the fact that the absolute electrical efficiency of gas turbine engines used in the above power plants with heat supply in the cycle at constant pressure and with adiabatic compression of the working fluid in compressors during intermediate cooling of the gas is not large enough and amounts to the maximum working fluid temperatures ≈30 - 36%, which is almost close to the electrical efficiency of known steam-turbine power plants (see, for example, the book "Technical Thermodynamics ", V.A. Kirillin et al., M, Energoatomizdat, 1983, pp. 276 - 277, as well as the book" Thermodynamics ", M.P. Vukalovich and I.I. Novikov, M, Mechanical Engineering, 1972 ., pp. 549 - 552 and the book "Combined Cycle Plants of Power Plants", A. I. Andryushenko and V. N. Lapshov, M, Energia, 1965, p. 233, Fig. 7.5).

 The second of the above disadvantages of the known methods of operating electric power plants results from a rather low absolute electrical efficiency of the plants, and is also related to the fact that the heat consumer does not always, but only periodically, require maximum power or high potential of thermal energy received from the electric power, and production electricity (especially transmitted to the regional or the all-Russian electric system) should be almost constant, that is, close to the rated power. In this regard, power plants operated according to the above methods and generating electricity almost continuously throughout the year at a power level close to the nominal, during periods of minimal heat energy output to the consumer (for example, for heating power plants - in the summer, non-heating season, and for industrial technological power plants - during scheduled, etc. interruptions in technological processes that consume the thermal energy of the plants) they are forced to practically reset unnecessary at this time by fighter an efficiency of heat energy to the environment, not rational burning while the original fuel, as well as causing the appropriate environmental ( "thermal") harmful nature.

 So, for example, the duration of the heating season in most regions of Russia ranges from 199 (Voronezh) to 251 (Arkhangelsk) days a year (see, for example, the book "Heat Technical Reference", M, Energy, 1976 , ed.V.N. Yurenev and P.D. Lebedev, pp. 568 - 569). This suggests that the above power plants that produce electrical and thermal energy for heat supply, being forced to almost 5 months. in a year (when electricity is produced as well as during the year) it is very unproductive to dump a significant amount of thermal energy of the burned fuel into the environment. At the same time, the consumer is given a reduced (about 4-5 times) amount of heat energy necessary for the functioning of hot water supply.

 Consequently, power plants operated by the above methods are uneconomical for the conditions of their operation with sufficiently long (planned or forced) interruptions in the consumption of thermal energy produced by them.

 The aforementioned drawbacks are deprived of the known method of operating a power plant, in which a gas working fluid is compressed in one or, mainly, in two or more compressors with intermediate gas cooling in a gas cooler, configured to provide heat extraction for heating, and / or in the refrigerator by transferring heat environment, then the compressed gas is passed as a heated medium through at least one heater, where the gas is heated to operating temperature, after which the working fluid expands they are revealed in a turbine that drives compressors and an electric generator, then the gas exhausted from the turbine is directed to the heating side of the above heat exchanger, after which it is passed through a gas cooler, which is capable of transferring thermal energy to the consumer, as a heating medium, and then it is cooled further by transferring heat to the external environment , after which the cooled working fluid of the installation is again compressed (see, for example, the book "Heat Engineering", ed. V.I. Krutov, Moscow: Engineering, 1986, p. 350, Fig. 9.14).

 A power plant for implementing this method of operation may comprise, for example, combined at least two compressors with gas cooler installed between them, with a gas cooler installed between them, configured to provide heat extraction for heating, and / or a refrigerator that transfers the heat of the working fluid to the external medium, the heated side of at least one heat exchanger, at least one gas heater, made, for example, in the form of a combustion chamber Nia organic fuel and connected with the pipe installed behind it, a gas outlet of which is connected to the atmosphere, wherein the heated gas cooler side of the last heat exchanger is connected to the circulation circuit heat energy consumer.

 The absolute electrical efficiency of this known installation is significantly increased (up to ≈44 - 48%) mainly due to the introduction of a heat recovery unit inside the cycle into the thermodynamic cycle of the initial gas turbine engine (see, for example, the book "Thermodynamics", MP Vukalovich and I . I. Novikov, M, Engineering, 1972, pp. 554 - 559). At the same time, the heat exchanger-regenerator introduced into the unit transfers part of the thermal energy of the working fluid that has left the single or last turbine of the cycle to the gas compressed by the compressor before it is heated in the heater. It follows that with the increase in absolute electrical efficiency and, correspondingly, the power of the generated electricity, the potential and power of thermal energy that can be transferred from the specified power plant to the consumer are accordingly reduced. It should also be mentioned that the power of the generated heat energy should significantly decrease during the operation of the power plant (while maintaining the power output) in modes with minimal (or reduced) heat supply to the consumer (for example, during the non-heating season, etc.). At the same time, in order to unconditionally ensure parallel production of electricity, the "surplus" of thermal energy that is unnecessary for the consumer, which is cooled in the cycle of the working fluid, must ultimately be transferred to the environment.

These circumstances ultimately impede the achievement of high thermal efficiency of the installation, which is estimated for power plants (including those plants that simultaneously produce electrical and thermal energy for consumers) in this way by a universal indicator such as the (average annual) coefficient of thermodynamic efficiency of the installation cycle ( see, for example, the book "Combined-cycle plants of a power plant", A.I. Andryushenko and V.N. Lapshov, M, Energy, 1965, pp. 176 - 179):
η $\genfrac{}{}{0ex}{}{\text{i.e.}}{\text{c}}$ = (L _c + E $\genfrac{}{}{0ex}{}{\text{t}}{\text{q}}$ ) / Q ₁ ,
Where
L _C - useful work cycle;
E $\genfrac{}{}{0ex}{}{\text{t}}{\text{q}}$ - operability of heat removed in the cycle to the consumer;
Q ₁ - heat of fuel supplied in the cycle.

Wherein
E $\genfrac{}{}{0ex}{}{\text{t}}{\text{q}}$ = Q _t • (1-T _o / T _cf ),
Where
Q _t - heat supplied to the consumer (for example, to the heating network);
T _about - absolute temperature of a cold source;
T _op - average absolute temperature of heat transfer by the heat carrier.

In addition, to characterize the efficiency of combined heat and power plants (CHP), the fuel heat utilization coefficient K, _{etc., is used.} , defined as the ratio of the amount of useful work performed in the cycle, L _e and the heat q _t given to an external consumer, to the amount of heat q ₁ released during the combustion of fuel:
K, _etc. = (L _e + q _t ) / q ₁
For modern steam turbine CHP K, _etc. = 0.6 - 0.8.

In view of the above, the known method of operating a power plant and a power plant for its implementation have the following disadvantages:
insufficient thermodynamic efficiency and, accordingly, low efficiency of a power plant that simultaneously produces electric and thermal energy, due to reduced power and potential values (t _max. ≈ 250 - 300 ^o C) of thermal energy transferred to the consumer during periods of operation in the modes with maximum (increased) the issuance of thermal energy to him, and also because of the need to discharge a noticeable amount of usable thermal energy into the external environment during the periods of operation of the electric power in modes with a minimum (decrease hydrochloric) delivery of heat energy to consumers. In addition, the limited potential of thermal energy that can be transferred to the consumer prevents the use of such well-known ES in widespread industrial and technological cycles, which, in addition to electricity, require medium - (up to 400 ^o C) and high - (over 400 ^o C ) potential heat.

 The need to address the above-mentioned disadvantages of the known method of operating electric power plants is also supported by the following well-known provisions of the power system (see, for example, the book "Heat Engineering", edited by V.I. Krutov, M, Mechanical Engineering, 1986, pp. 334 - 338, 353 - 354 , 380 - 387).

 Power plants generate electric and thermal energy for the needs of industry and public services. Depending on the energy source, there are thermal power plants (TPPs), hydroelectric power plants (HPPs), nuclear power plants (NPPs), etc. Condensation power plants (TPPs) and heat and power plants (TPPs) are TPPs. Thermal power plants, unlike IES, along with electricity produce thermal energy (for example, hot water and steam for the needs of heating). Currently, TPPs (IES and TPPs) account for the bulk (about 71%) of the electricity generated in Russia. Electrical and thermal energy produced by thermal power plants should be used by consumers almost at the time of their production. This feature of the operation of power plants necessitate the high reliability of the work. Reliability of power supply is enhanced by combining power plants with transmission lines into energy systems. The variability of the load schedule of the power system leads to the inability to operate all power plants at full installed capacity, which is equal to the sum of the rated capacities of electric generators and heating equipment of a single station or power plant. In this mode, only power plants operate at full installed capacity, covering the basic part of the load, which is 0.4 - 0.6 of the maximum power of the power system. To provide a variable part of the load schedule of the electrical system, semi-peak and peak power plants are provided. Peak power plants operate 55 - 1,500 hours a year, semi-peak - 3,500 - 4,500 hours, and base plants - more than 5,500 hours a year. At present and in the near future, the basic part of the load schedule of the country's total energy system will be covered by electric power transmission from sufficiently powerful TPPs and hydroelectric power stations. At the same time, the installed capacity utilization factor (KIUM) of the base power plants producing only electricity (KES and GRES) is quite high and amounts to 0.62 - 0.74. A further increase in KIUM (which is proportional to the time required for the station to be loaded during the year) can lead to an unjustified increase in costs associated with ensuring the reliability of equipment required under these conditions, and therefore should be justified for each specific project of power plants.

 In contrast to the foregoing, the schedule of thermal loads (daily, annual) issued to the consumer, is characterized, as a rule, even more uneven than the schedule of electrical loads. For example, the heating heat load is seasonal in nature and depends on climatic conditions (for most regions of Russia, the heating season lasts 7 months a year). Year-round hot water supply (the share of the load of which from the nominal heat load of a thermal power plant is only 20%) is determined by the days of the week and changes dramatically throughout the day.

 The industrial heat load is more uniform throughout the year, but at the same time it changes during the day, as a result, for thermal power plants providing coverage of the heating load, the KIUM is noticeably smaller than for the KEC and amounts to KIUM = 0.46 - 0.63. This means that the generating capacity of thermal power plants (mainly production or thermal energy) exceeds almost 1.6 to 2.2 times the power needed to generate the same amount of energy when working with a uniform nominal load during the year.

 Thus, for power plants of thermal power plants producing electric and thermal energy, the presence of sufficiently long periods (during the year, for example) of operation, both in the mode with maximum (increased) and minimum (reduced) heat energy to the consumer of various parameters ( low, medium and high potential) is a widespread objective reality that must be taken into account when creating new highly economical power plants for thermal power plants.

 In connection with the stated problem, the invention is aimed at solving, it is to increase thermodynamic efficiency and therefore economy, as well as expanding the areas of effective use of a power plant that simultaneously produces electric and thermal energy by increasing the capacity and potential of thermal energy transmitted to the consumer during operation with the maximum (increased) issue of thermal energy to him, as well as by reducing the amount of workable thermal energy discharged into the external environment during periods of operation of a power plant in modes with minimal (reduced) generation of thermal energy to a consumer while ensuring the possibility of highly efficient production (in all operating modes) of an almost constant amount of electricity while maintaining the nomenclature and the number of basic units (elements) of equipment of a known power plant .

 To solve this problem, in a known method of operating a power plant, in which the working fluid of the plant is compressed in one or mainly in two or more compressors with intermediate cooling in an eye cooler, configured to provide heat removal for heating, and / or in the refrigerator due to heat transfer environment, then the working fluid is directed to at least one heater, where it is heated to the working temperature, then the working fluid is expanded into compressors driving, and, for example p, an electric generator to the turbine, then the spent in the last working fluid of the installation is passed as a heating medium through at least one heat exchanger-recuperator and then through the last gas cooler of the cycle, made, for example, with the possibility of transferring thermal energy to the consumer, during operation of the installation in mode c With the maximum or increased output of thermal energy to the consumer, the compressed working fluid of the installation is sent to bypass the heat exchanger-recuperator in a heater, the power of which increases accordingly a wider temperature range of the heated working fluid, while the heat exchanger-recuperator is connected on the heated side to the selection of heat for energy technology needs and / or heat supply to the consumer, for which at least one circulation heat exchange circuit is used, and during operation of the installation in the mode with minimal or reduced output of thermal energy to the consumer, the compressed working fluid is passed as a heated medium through the specified heat exchanger-recuperator, and the power is installed Nogo him heater is reduced in accordance with the decreased temperature range of the heated working fluid.

 At the same time, during the period of increased output, the consumer of thermal energy during its selection from the gas cooler installed behind the first compressor and using atmospheric air as a working fluid in the additional heat exchanger heats the atmospheric air entering the compressor with at least part of the flow rate of the working fluid spent in the turbine after passing it through the last gas cooler of the cycle, after which the cooled working fluid is released into the atmosphere, while the remaining part of the flow is spent of a turbine working fluid discharged to the atmosphere, bypassing the additional heat exchanger.

 In addition, when operating a plant operating in a closed thermodynamic cycle, a cooled working fluid emerging from the last gas cooler of the cycle is sent for compression to the first compressor of the plant. Moreover, any inert gas or nitrogen, which is heated, for example, in a nuclear reactor, can be used as the working fluid of the installation. In addition, an inert gas, for example, helium, neon or argon with an ionizing additive made, for example, in the form of cesium, and which is heated, for example, in a nuclear reactor, and then expanded before expanding in the turbine, can be used as the working fluid of the installation in an electric power generating magnetohydrodynamic generator. To achieve the above technical result, a power plant operated according to the claimed method is proposed, the prototype of which is a power plant presented in the book "Heat Exchanger" ed. V.I. Krutov (M. Mechanical Engineering, 1986) on p. 350, Fig. 9, 14.

 Moreover, in a power plant containing one or, mainly, two or more compressors with, for example, combined with pipelines for circulating the working fluid of the plant, with a gas cooler installed between them, configured to provide heat removal for heating, and / or a refrigerator, providing heat transfer to the external environment , the heated side of at least one heat exchanger-recuperator, at least one working fluid heater, made, for example, in the form of an organic combustion chamber fuel and connected to a turbine installed behind it, the outlet from the latter is connected to the heating side of the heat exchanger-recuperator, then connected to the heating side of the last gas cooler of the cycle, the outlet of which is connected to the atmosphere, while the heated side, mainly of each gas cooler, is connected to the circulation circuit, providing the consumer with thermal energy, the connection of the heating side of the last gas cooler of the cycle with the atmosphere is made in parallel through a pipeline with shut-off and control fittings, as well as through a pipeline equipped with shut-off and control valves, connected to the heating side of an additional heat exchanger, made with the possibility of preheating the atmospheric air entering the first compressor of the installation. In addition, the heated side of the heat exchanger-recuperator at the inlet and outlet of the working fluid can be connected, for example, by pipelines through shut-off valves to the circulation heat-exchange circuit of the consumer of thermal energy, and pipelines or, for example, cavities connecting the input and output of the working fluid with the nearest compressor and heater, equipped with shutoff valves, while the said compressors and heater are interconnected bypassing the heat exchanger-recuperator, for example, a pipeline m, which is provided with a stop valve.

The essence of the invention is illustrated by drawings, which depict:
in FIG. 1 is a schematic thermal diagram of a power plant according to embodiment 1;
in FIG. 2 - TS diagram of the ideal cycle of operation of option 1 of a power plant during its operation in the mode with minimal (reduced) heat energy to the consumer;
in FIG. 3 - TS diagram of the ideal cycle of operation of option 1 of the power plant during its operation in the mode with maximum (increased) heat energy output to the consumer;
figure 4 is a schematic thermal diagram of a power plant according to embodiment 2;
in FIG. 5 - TS diagram of the ideal cycle of operation of option 2 of a power plant during its operation in a mode with minimal (reduced) heat energy to the consumer;
in FIG. 6 - TS diagram of the ideal cycle of operation of option 2 of the power plant during its operation in the mode with maximum (increased) heat energy output to the consumer
Fig.7 is a schematic thermal diagram of a power plant according to embodiment 3;
in FIG. 8 - TS diagram of the ideal cycle of operation of option 3 of a power plant during its operation in the mode with minimal (reduced) heat energy to the consumer;
in FIG. 9 - TS diagram of the ideal cycle of operation of option 3 of the power plant during its operation in the mode with maximum (increased) heat energy output to the consumer;
in FIG. 10 is a schematic thermal diagram of a power plant according to embodiment 4;
in FIG. 11 - TS diagram of the ideal cycle of operation of option 4 of a power plant during its operation in the mode with minimal (reduced) heat energy to the consumer;
in FIG. 12 - TS diagram of the ideal cycle of operation of option 4 of the power plant during its operation in the mode with maximum (increased) heat energy output to the consumer;
The proposed method of operating a power plant producing electric and thermal energy is carried out in the following sequence. During the operation of the power plant in the mode with maximum or increased heat energy output to the consumer, the compressed working fluid of the installation is sent to bypass the heat exchanger-recuperator to the heater, the power of which is increased according to the expanded temperature range of the heated working fluid, while the heat exchanger-recuperator is connected to the selection via the heated side heat for energy technology needs and / or heat supply of the consumer, for which at least one circulation the heat exchange circuit, and during operation of the installation in the mode with minimal or reduced heat energy to the consumer, the compressed working fluid is passed as a heated medium through the specified heat exchanger-recuperator, and the power of the heater installed behind it is reduced in accordance with the reduced temperature range of the heated working fluid .

 In addition, when operating a power plant in a closed or closed thermodynamic cycle, the cooled working fluid emerging from the last gas cooler of the cycle is sent for compression to the first compressor of the installation. Moreover, any inert gas or nitrogen, which is heated, for example, in a nuclear reactor, can be used as the working fluid of the installation. In addition, an inert gas, for example, helium, neon or argon with an ionizing additive made, for example, in the form of cesium, and which is heated, for example, in a nuclear reactor and then, before expansion in the turbine, can be used as the working fluid of the installation expand in an electric power generating magnetohydrodynamic generator.

 Option 1 of the execution of the power plant according to the claimed invention consists of the following basic units of equipment, combined by the corresponding pipelines or cavities of the hull structures (see figure 1). The first compressor, which draws in atmospheric air, is connected to the heating side of the gas cooler 2, which is then connected to the cooled side of the refrigerator 3, on the heated side of which the water circulating into it, for example, from a cooling tower, is circulated. Next, the outlet of the working fluid from the refrigerator 3 is connected to the gas inlet to the second compressor 4. The gas outlet from the compressor 4 is connected through shut-off valves 5 to the heated side of the heat exchanger-recuperator 6, which is connected through a shut-off valve 7 to the heater - combustion chamber 8, to which it is simultaneously supplied fossil fuels by compressor (if the fuel is gas) or by a pump if the fuel is liquid (not shown). In addition, the compressor 4 and the combustion chamber 8 are interconnected bypassing the heat exchanger 6 bypass pipe 9 with shutoff valves 10. The output of the heated working fluid from the combustion chamber 8 is connected to a gas turbine 11, which drives the compressors 1 to 4, as well as an electric generator 12, which in the start-up mode of a power plant can operate as a starting electric motor for the indicated compressors and turbines. The outlet of the working fluid from the turbine 11 is connected to the gas inlet to the heating side of the heat exchanger 6, the gas outlet from which is connected to the inlet to the heating side of the gas cooler 13. The gas outlet from the heating side of the gas cooler 13 is connected in parallel with the atmosphere directly through shut-off and control valves 14, and through shut-off and control valves 15 with then the heating side of the additional heat exchanger 16 connected to the atmosphere, configured to provide additional heating of the atmospheric air entering mpressor 1.

 To ensure the possibility of heat transfer to the consumer, the heated sides of the gas coolers 2 and 13 are connected to the circulation circuit of the heat consumer, including, in addition to them, a network circulation pump 17 and control valves 18, designed to regulate the balance of capacities provided by the gas coolers to the heat consumer.

 In order to provide additional heat transfer to the consumer from the electrical installation, the gas inlet and outlet from the heated side of the heat exchanger-recuperator 6 are connected through shut-off valves 19 and 20 to the second heat consumer circulation circuit, which also includes the network circulation pump 21. Characteristic points of change in the physical state of the plant’s working medium (inputs and exits from the main elements of the installation) are marked in FIG. 1 with the letters a, b, c, ... K. The same letters in FIG. 2, 3, the corresponding characteristic points of the T - S diagrams of the ideal operation cycles of the above-described installation variant in two main operating modes are marked.

тепло (удельное), подводимое к циклу в камере сгорания 8;
Q_рег. - тепло регенерации, передаваемое теплообменником 6 внутри цикла (направление теплопередачи показано стрелкой);
Q_т2 - тепло, выдаваемое потребителю через газоохладитель 13;
Q_ух - тепло, отдаваемое во внешнюю среду (атмосферу) с уходящим газом;
Q_т3 - тепло, выдаваемое потребителю через газоохладитель 2;
Q_х - тепло, отдаваемое во внешнюю среду через холодильник 3;
а, б, в, ... к - характерные точки изменения физического состояния рабочего тела в данном режиме работы установки.In FIG. Figure 2 shows the TS diagram of the ideal cycle of operation of option 1 of a power plant in a mode with minimal heat output to the consumer, for example, during the non-heating season (5 months in a year). In this case, the following notation is indicated on the diagram:

heat (specific) supplied to the cycle in the combustion chamber 8;
Q _reg. - heat of regeneration transmitted by the heat exchanger 6 inside the cycle (the direction of heat transfer is indicated by the arrow);
Q _t2 - heat supplied to the consumer through the gas cooler 13;
Q _uh - heat transferred to the external environment (atmosphere) with flue gas;
Q _t3 - heat supplied to the consumer through gas cooler 2;
Q _x - heat transferred to the external environment through the refrigerator 3;
a, b, c, ... k - characteristic points of change in the physical state of the working fluid in a given operating mode of the installation.

подведенное к циклу (в камере сгорания 8) тепло;
Q_т1 - тепло, выдаваемое потребителю через теплообменник-рекуператор 6.In FIG. Figure 3 shows the TS diagram of the ideal cycle of operation of option 1 of the claimed power plant in the mode of its operation with the maximum release of thermal energy to the consumer (for example, during the heating season, which lasts about 7 months a year). Moreover, in the diagram, in contrast to FIG. 2, the following additional designations are indicated:

heat supplied to the cycle (in the combustion chamber 8);
Q _t1 - heat supplied to the consumer through the heat exchanger-recuperator 6.

 Depicted in FIG. 4 option 2 power plants, implemented according to the claimed invention, is arranged as follows. In contrast to that depicted in FIG. 1 of option 1, this option of the installation operates in a closed thermodynamic cycle with a two-stage heat supply in two heaters made in the form of gas-cooled nuclear reactors 22 and 23, the outputs of the working fluid from which are connected respectively to gas turbines 24 and 25. In the late 1980s, such high-temperature gas-cooled nuclear reactors have been recognized in the world as the most promising options for safe and efficient reactors for the coming decades (see, for example, the book "Nuclear gas turbine and combined s installation ", ed. E.A.Manushin, M, Energoatomisdat, 1993, p. 262).

 The turbine 24 is designed to drive an additional electric generator 26. For example, a monoatomic inert gas (helium) or nitrogen is used as the working fluid of the installation. In addition, in this embodiment, unlike the first, there is no gas cooler 2 that gives heat to the consumer, and due to the closed cycle before the working fluid enters, an additional water-cooled refrigerator 27 is installed in the compressor 1, which transfers the heat of the working fluid to the external environment.

 The gas inlet and outlet from the heated side of the heat exchanger-heat exchanger 6 installed after the last turbine 25 are connected via shut-off valves 28 and 29 to a gas intermediate heat exchange circuit, which also includes a gas circulator, for example, a gas blower 30 and a heating side of an additional heat exchanger 31, the heated side of which is made in the form of an integral element of the network circulation heat exchange circuit, providing the consumer with thermal energy. A pump or a gas blower 32 can serve as a network circuit circulator. A gas intermediate heat exchange circuit is also designed to exclude the possibility of radioactive substances entering the network circuit of a heat consumer. As the coolant of this gas circuit, the same gas was used as for the working fluid of the installation. For the same purpose, to prevent the release of radioactivity into the network circuit, the heated side of the gas cooler 13 is connected to the second network circuit of the heat consumer through another, for example, gas intermediate circuit, including, in addition to the gas cooler 13, a gas circulator 33 and a heat exchanger 34, through the heated side of which the circulator 33 It pumps the coolant of the network circuit (e.g. water).

 The characteristic points of change in the physical state of the working fluid of this installation option are marked in FIG. 4 letters a, b, c, ... l. The same letters indicate the corresponding characteristic points of the T-S diagrams (see Figs. 5, 6) of ideal cycles of operation of this installation option in dibasic modes of its operation. The remaining symbols shown in FIG. 4 are the same as in FIG. 1.

тепло, подводимое к циклу в первом нагревателе - реакторе 22;

тепло, подводимое к циклу во втором нагревателе - реакторе 23;
Q_рег. - тепло регенерации, передаваемое теплообменником 6 внутри цикла (направление передачи тепла показано стрелкой);
Q_т2 - тепло, выдаваемое потребителю (например, для горячего водоснабжения) через газоохладитель 13;
Q_х1 - тепло, отдаваемое во внешнюю среду через холодильник 27;
Q_х2 - тепло, отдаваемое во внешнюю среду через холодильник 3;
а, б, в, ... л - характерные точки изменения физического состояния рабочего тела в данном режиме работы установки.In FIG. 5 is a TS diagram of an ideal cycle of operation shown in FIG. 4 options 2 of the proposed power plant in the mode of its operation with minimal heat output to the consumer (for an analogue, see Fig. 2). In this case, the following notation is indicated on the diagram:

heat supplied to the cycle in the first heater - reactor 22;

heat supplied to the cycle in the second heater - reactor 23;
Q _reg. - heat of regeneration transmitted by the heat exchanger 6 inside the cycle (the direction of heat transfer is shown by the arrow);
Q _t2 - heat supplied to the consumer (for example, for hot water supply) through gas cooler 13;
Q _x1 - heat transferred to the external environment through the refrigerator 27;
Q _x2 - heat transferred to the external environment through the refrigerator 3;
a, b, c, ... l are characteristic points of change in the physical state of the working fluid in a given operating mode of the installation.

тепло, подводимое к циклу в первом нагревателе - реакторе 22;
Q_т1 - тепло, выдаваемое потребителю через теплообменник 6.In FIG. Figure 6 shows a TS diagram of the ideal cycle of operation of option 2 of the proposed power plant in the mode of its operation with maximum heat output to the consumer (for an analogue, see Fig. 3). In this case, the diagram shows the following additional designations not shown in FIG. 5:

heat supplied to the cycle in the first heater - reactor 22;
Q _t1 - heat supplied to the consumer through the heat exchanger 6.

 Presented in FIG. 7, option 3 of the power plant implemented according to the claimed invention has the following differences from option 2 of the installation, the thermal diagram of which is shown in FIG. 4.

 In this embodiment, an inert gas, for example, helium, neon or argon with an ionizing additive made, for example, in the form of cesium, is used as a working fluid. If necessary, the installation can be equipped with known devices for input and output of an ionizing additive (not shown). Heating of the working fluid to the maximum heat of the cycle is carried out in one reactor 22, the gas outlet from which is connected, for example, by a pipe to the entrance to the magnetohydrodynamic generator (MHD generator) 36, which produces electricity and which can be considered as a high-temperature gas turbine. It should be noted that according to the proposed technical solution, it is possible to create a power plant using an MHD generator that operates on an open thermodynamic cycle (not shown). The gas outlet from the MHD generator 36 is connected to the inlet to the turbine 25. The operating cycle of the installation is supplemented by a third compressor 37, in front of the inlet of the working fluid into which a water-cooled refrigerator 38 is installed, with which heat is transferred to the external environment.

 Due to the fact that the first circuit of the working fluid of the installation can be radioactive, especially when using argon as the main working fluid, this installation option is equipped with an additional protective intermediate heat exchange circuit of the consumer of thermal energy, which is connected to the heated side of the heat exchanger 31 and includes also a gas blower or compressor 39 and a heat exchanger 40. Finally, heat is transferred to the heat consumer through the heat exchanger 40 by means of a circulator 41. As the heat carrier of the intermediate heat exchange circuit, the same inert gas was used as in the working fluid of the installation.

 The characteristic points of change in the physical state of the working fluid of the installation (gas inlet and outlet from the main elements of the installation) are marked on the thermal diagram with the letters a, b, c, ... m. These letters also indicate the corresponding characteristic points of the TS diagrams (see Fig. 8, 9) ideal cycles of operation of the above option 3 installation in two main modes of its operation. The remaining symbols shown in FIG. 7 are the same as in FIG. 4.

тепло, подводимое в цикле в реакторе 22;
Q_рег. - тепло регенерации, передаваемое теплообменником-рекуператором 6 внутри цикла;
Q_т2 - тепло, выдаваемое потребителю через газоохладитель 13;
Q_х1, Q_х2, Q_х3 - тепло, отдаваемое во внешнюю среду через холодильники 27, 3 и 38;
а, б, в, ... м - характерные точки изменения физического состояния рабочего тела в данном режиме работы.In FIG. 8 shows a TS diagram of the operation of option 3 of a power plant in a mode with minimal heat output to the consumer. At the same time, the following notation is presented on the diagram:

heat supplied in a cycle in the reactor 22;
Q _reg. - heat of regeneration transmitted by the heat exchanger-recuperator 6 inside the cycle;
Q _t2 - heat supplied to the consumer through the gas cooler 13;
Q _x1 , Q _x2 , Q _x3 - heat transferred to the external environment through refrigerators 27, 3 and 38;
a, b, c, ... m - characteristic points of change in the physical state of the working fluid in a given operating mode.

тепло, подводимое в цикле в реакторе 22 (для данного режима эксплуатации);
Q_т1 - тепло, выдаваемое потребителю через теплообменник-рекуператор 6.In FIG. Figure 9 shows the TS diagram of the ideal cycle of operation of option 3 of a power plant in the mode of its operation with maximum output of thermal energy to the consumer. Moreover, in contrast to FIG. 8, the following additional symbols are indicated in this diagram:

heat supplied in a cycle in the reactor 22 (for a given operating mode);
Q _t1 - heat supplied to the consumer through the heat exchanger-recuperator 6.

 Presented in FIG. 10, option 4 of the power plant implemented by the claimed invention has the following differences from option 3 of the installation, the thermal diagram of which is shown in FIG. 7.

 The output of the working fluid from the MHD generator 36 is connected, for example, by a pipeline to the heating side of the second heat exchanger 42, the output of the heating medium from which is connected to the input of the working fluid into the gas turbine 25, then connected to the heating side of the first heat exchanger-recuperator 6, which is constantly operating, for example , as a cycle recuperator. The second heat exchanger-recuperator 42 is configured to transmit high potential heat energy to the consumer through an additional circulation heat exchange circuit connected to the heated side of this heat exchanger through shut-off valves 43 and 44. In addition, the pipelines for connecting the input and output of the heated side of the heat exchanger-recuperator 42, respectively, exit from of the heated side of the heat exchanger 6 and with the entrance to the reactor 22 are equipped with shutoff valves 45 and 46. In this case, the outlet of the working fluid from the heated the first side of the first heat exchanger-recuperator 6 and the gas inlet to the reactor are connected bypass pipe 47 bypassing the second heat exchanger-recuperator 42, which is equipped with shutoff valves 48. The high-temperature heat received from the heat exchanger-recuperator 42 can be transferred to the intermediate “protective” heat-exchange circuit further through the heat exchanger 49. The circulator of the additional heat exchange circuit, the heat carrier of which is the same gas used in the working fluid of the installation, is made in in the form of a compressor or gas blower 50. The above-mentioned intermediate "protective" gas heat exchange circuit includes, in addition to the heated side of the heat exchanger 49, a circulator 51 and the heating side of the network heat exchanger 52, which is the heat source in the consumer circuit.

 At least one gas blower or compressor 53 serves as a consumer circuit circulator, and a gas having acceptable thermophysical properties (for example, helium) or a mixture of chemically reacting gases providing long-distance (more than 100 km) transportation through a heat pipeline from a heat source (known chemothermal method of transferring thermal energy).

 The characteristic points of change in the physical state of the working fluid of this variant of the power plant are marked in FIG. 10 letters a, b, c, ..., p. The same letters indicate the corresponding characteristic points of the T-S diagrams (see Figs. 11, 12) of ideal cycles of operation of this installation option in two main modes of its operation. The remaining symbols shown in FIG. 10 are the same as in FIG. 7.

тепло, подводимое в цикле в реакторе 22;
Q_р2, Q_р1 - тепло регенерации, передаваемое теплообменниками-рекуператорами 6 и 42 внутри цикла;
Q_т - тепло, выдаваемое потребителю через газоохладитель 13;
Q_х1, Q_х2, Q_х3 - тепло, отдаваемое во внешнюю среду соответственно через холодильники 27, 3 и 38;
а, б, в, ... п - характерные точки изменения физического состояния рабочего тела в данном режиме работы.In FIG. 11 is a TS diagram of an ideal cycle of operation shown in FIG. 10 options 4 of the proposed power plant in the mode of its operation with a minimum supply of thermal energy to the consumer. In this case, the following notation is indicated on the diagram:

heat supplied in a cycle in the reactor 22;
Q _p2 , Q _p1 - heat of regeneration transmitted by heat exchangers-recuperators 6 and 42 inside the cycle;
Q _t - heat supplied to the consumer through the gas cooler 13;
Q _x1 , Q _x2 , Q _x3 - heat transferred to the external environment, respectively, through refrigerators 27, 3 and 38;
a, b, c, ... p - characteristic points of change in the physical state of the working fluid in a given operating mode.

тепло, подводимое в цикле в реакторе 22 (в данном режима эксплуатации);
Q_вт - высокопотенциальное тепло, выдаваемое потребителю через теплообменник-рекуператор 42.In FIG. Figure 12 shows a TS diagram of the ideal cycle of operation of option 4 of a power plant in the mode of its operation with maximum output of thermal energy to the consumer. Moreover, in contrast to FIG. 11 in this diagram, the following additional symbols are indicated:

heat supplied in a cycle in the reactor 22 (in this operating mode);
Q _W - high potential heat supplied to the consumer through the heat exchanger-recuperator 42.

 Four of the above options for the implementation of power plants (EU), operating on the proposed method of operation, operate in two main modes of operation as follows.

 Option 1.

The operating mode of option 1 EA with a minimum (reduced) heat supply to the consumer (see Fig. 1, 2)
During this operating mode of the EA (for example, during the non-heating season, etc.), the position of the valves in the circulation paths of the working fluid and coolant is as follows: shut-off valves 10, 19, 20 are closed; stop valves 14, 15 - both are covered or at least one of them is closed; shut-off and control valves 18 - ajar.

The start-up of the compressors 1, 4 and the turbine 11 is carried out by an electric generator 12, operating at that time with a starting electric motor. Thus, the compressor 1 draws in atmospheric air (for example, with a temperature T _d = 30 ^o C) and compresses it to a certain pressure, as a result of which the air temperature rises to a value (T _e = 210 ^o C), sufficient to cooling it in gas cooler 2 to an acceptable temperature (T _W = 110 ^o C) to transfer heat to the consumer, for example, for public heating. Next, after leaving the heating side of the gas cooler 2 under the action of the compressor 1, the air enters the refrigerator 3, where it is even more cooled (up to T _c ≈30 ^o C) due to the transfer of heat Q _{x to the} external environment. Then, the cooled air is even more compressed in the compressor 4 (for example, up to 26.8 ata, heating up to T _and = 210 ^o C) and then through the open shutoff valve 5 it enters the heated side (for example, in the annular space) of the heat exchanger-recuperator 6, serving in this operating mode of the installation as a regenerator. In the heat exchanger-recuperator 6, due to the heat of the gas leaving the turbine 11, the air is heated (for example, to T _k = 510 ^o C) at a temperature of the gas exiting the turbine T _b = 530 ^o C) and then fed through an open valve 7 into the chamber combustion 8, where, simultaneously with air, gaseous or liquid organic fuel is supplied for combustion. The combustion of fuel (heat input Q) occurs in the combustion chamber 8 at a constant increased pressure. The gaseous products of combustion, as a result of expansion due to their kinetic energy, rotate the gas turbine 11, which accordingly drives compressors 1, 4, as well as an electric generator 12 that produces electricity supplied to consumers. As a result of doing useful work in the turbine 11, the expansion temperature of the working fluid of the installation decreases (for example, from T _a = 1250 ^o C to T _b = 530 ^o C). Then, the gas working fluid exiting the turbine 11 enters the heating side of the heat exchanger 6, where, as a result of the above regenerative heating of the gas compressed in the compressor 4 (Q _reg. ), It is cooled to a temperature (T _at = 230 ^o C), which is high enough for use in heat consumption. Thus, the gas with the specified temperature (T _in ) enters the gas cooler 13 as a heating medium, where it is cooled (giving off heat Q _t2 ) by the heat carrier of the consumer circuit to an acceptable temperature (T _g = 110 ^o C). After the gas cooler 13, the working fluid of the installation is cooled (Q in _. ) To the minimum temperature of the cycle T _d by discharging gas into the atmosphere through one open shut-off and control valve 14 or through shut-off and control valve 15, or through both valves 14 and 15 opened ajar accordingly. The above open positions of the valves 15 are provided if it is necessary to increase the supply to the consumer (with a slight decrease in the electrical efficiency of the installation) of thermal energy through the gas cooler 2, for example, in periods with a low (T _d <0 ^o C) rate ambient air temperature. In this mode, the part of the gas flow passing through the valve 15 (or its entire flow rate) then, when passing through the heating side of the additional heat exchanger 16, will preheat the total atmospheric air sucked by the compressor 1 to the initial temperature T _d , which ensures compression of the inlet air temperature the heating side of the gas cooler 2 T _e = 210 ^o C, which will provide increased heat transfer power to the consumer gas cooler 2. To cool the working fluid of the installation and the corresponding reception and heat (Q _t3 and Q _t2 ) by the consumer through the heated sides of gas coolers 2 and 13, pump 17 pumps water with an inlet temperature of gas coolers ≥ 70 ^o C. To match the power of gas coolers 2 and 13, as a result of which the outlet temperature of the network water will be the specified control valve 18 serves as a value of 150 - 180 ^o C. As a result, the consumer's heating system receives network water of heating parameters (see, for example, the book "Heating Systems", L. S. Khrilev, M, Energoatomizdat, 1988, p. 179 - 181).

 Considering the temperatures of the working fluid of the cycle given above for an example (see Fig. 2), we present the results of a quantitative assessment of the operation of this variant of a power plant in the considered mode of its operation with minimal (reduced) heat energy output to the consumer (for example, during a 5-month non-heating year the season in which heat is consumed for a constant hot water supply throughout the year and other technological needs.

 The absolute electrical efficiency of the EU is 44%.

 We take the thermal power of the combustion chamber in this mode - 600 MW (t).

 Then the electric power of the EU is - 264 MW (e).

 The heat output to the consumer by gas coolers 2 and 13 is 156 MW (t).

 The fuel heat utilization coefficient is 70%.

 The thermodynamic efficiency coefficient of the cycle is 53.1%.

 The operating mode of option 1 EU at the maximum (increased) heat supply to the consumer.

 This mode (see Fig. 1, 3) of the operation of the power plant (for example, during the heating season, etc., most fully reflects the essence of the claimed technical solution. The differences between the operation of the EA in this mode from the foregoing are as follows.

Valves 10, 19 and 20 switch to the “open” position, and valves 5, 7 to the “closed” position. As a result, the gas working medium of the unit compressed in the last (in the second) compressor 4 enters at the same flow rate as in the previous mode of operation of the EA, bypassing the heat exchanger-recuperator 6, into the heater - the combustion chamber 8, the power of which is increased (by supplying additional fuel) according to the expanded temperature range of the heated working fluid (that is, for the selected quantitative example, it is heated to T _a = 1250 ^o C not with T _k = 510 ^o C, but with a temperature T _and = 210 ^o C). Thus, through the gas turbine 11, the same flow rate of the working fluid with the same input temperature and pressure passes through the gas turbine 11, as a result of which the electric generator 12 generates the same electric power in this mode (N _el = const). As in the above-described operating mode, the gas exiting the turbine 11 passes through the heating sides of the heat exchanger 6 and the gas cooler 13, after which it is finally released into the atmosphere.

The difference between the operation of the heat exchanger-recuperator 6 in this mode is that with the help of the opening fittings 19 and 20, the heat carrier, which can be made in the form of water (steam) or gas, is pumped through the consumer circulator 21 of the heat exchange circuit through the heated side of this heat exchanger. Thus, in this mode, (without the need of an additional heat exchanger) the consumer is given an additional significant amount of heat without a high capacity (working installation body cools _b = 530 ^o C to _T = 230 ^o C during heat transfer to the consumer with T). These parameters of the generated heat energy can satisfy a wider circle of consumers than in the first mode of operation of the electric power plants. For example, an analysis of the heat consumption of the main industries shows that more than 60% of the heat consumed is accounted for by water vapor. Depending on the nature and conditions of the process, the parameters of the consumed steam vary in a wide range: pressure from 0.2 to 10.0 MPa, temperature - from 150 to 500 ^o C (see, for example, the book "Heating systems", M, Energoatomizdat 1988, p. 223 - 225). Moreover, in most technological processes, water vapor with a pressure of 0.5 - 4.0 MPa is used.

 For a steam consumer heating system, for example, one-pipe and two-pipe systems with condensate return can be used, which include: steam heating plants according to a dependent scheme; independent water heating systems; hot water installations; technological devices - steam consumers, etc. (see, for example, the book "Thermal Engineering Handbook", ed. V.N. Yurenev and P.D. Lebedev, M, Energy, 1975, v. 1, pp. 578-580).

 A quantitative assessment of the operation of power plants in the considered mode of operation and comparison with indicators of the previous operating mode of the installation.

 The absolute electrical efficiency of the EU is 32%.

 Due to the expanded temperature range of the heated gas, the power of the combustion chamber 8 will increase from 600 to 824 MW.

 Electric power of EU - 264 MW (e) - const.

 The heat output to the consumer by gas coolers 2 and 13 is 156 MW (t).

 Additional heat output of a higher potential given to the consumer by heat exchanger 6 is 224 MW (t).

 The total heat output in this mode to the consumer is 380 MW (t).

 The fuel heat utilization rate is 78.1%.

 The thermodynamic efficiency coefficient of the cycle is 53.9%.

 Thus, when a power plant switches from an operating mode with a minimum heat energy output (a prototype technical solution corresponds to this mode) to an operating mode with the maximum heat energy output to a consumer, the following positive factors of the claimed technical solution are revealed.

 While maintaining the electric power of the generator, the coefficient of fuel heat utilization increases from 70 to 78.1% (by 8.1 abs.%); the thermodynamic efficiency coefficient of the cycle increases from 53.1 to 53.9% (by 0.8 abs.%), and the total heat output to the consumer increases by 2.43 times (by 224 MW).

Therefore, in order to meet the consumer’s needs for periodically increasing heat supply to him, the proposed technical solution eliminates the need for a sufficiently large cost for the construction and operation of an additional boiler house that produces average potential heat with a temperature> 300 - 400 ^o C. necessary for the consumer during periods of maximum consumption. taking into account the fact that the efficiency of modern boiler plants using fossil fuels is 90%, the rated power of the heater is additional boiler room should be 11% more than the amount of additional heat capacity that can be provided to the consumer from a single power plant that produces electric and thermal energy by the proposed method. That is, to produce the same amount of additional heat as in the claimed power plant, the heater of the above-mentioned additional boiler should be unproductive to burn more fuel than in the claimed EU by 11% (1 / 0.9 = 1.11).

 For the above quantitative example of EU, the above factors determine the following production and business indicators.

Rated thermal power of the additional boiler room N _k = 224 / 0.9 = 249 MW (t). Taking into account the current specific capital costs in the construction of a fossil fuel boiler house, the cost of building such a boiler house will be ≈20 million US dollars.

At the same time, the annual consumption of additional gas fuel burned for 5500 hours a year in the boiler room heater (11% of the nominal gas consumption) will be ≈20.3 million m ³ / year, which will be ≈1.1 million at current natural gas prices. dale US / year (additional operating expenses).

 The cost of building the main well-known heat and power plant (CHP) producing electricity with a capacity of 264 MW (electric) and thermal energy with a capacity of 156 MW (see the regime with a minimum delivery of thermal energy to a consumer) will be ≈ 132 million. USA.

 Consequently, the total capital expenditures for the construction of an additional boiler house and a fossil fuel power plant based on the well-known technical solutions will amount to 20 + 132 = 152 million dollars. USA.

 At the same time, capital expenditures for the construction of a single CHPP created for the implementation of the proposed method, which provides solutions to the tasks set for the above-mentioned well-known boiler houses and CHPPs, is less, that is, 135 million USD.

 In connection with the above, for the considered option 1 of the proposed power plant, the saving of only capital costs as a result of the implementation of the declared technical solution will be (152 - 135/152) • 100% = 11.2% of the amount of capital costs required for the construction of a thermal power plant and an additional boiler house, created by well-known technical solutions.

 In addition, taking into account the above (11%) saving of fuel irrationally burned in an additional boiler room, the annual savings in operating costs resulting from the implementation of the proposed technical solution will be at least ≈25% of the total annual operating costs required for the operation of a thermal power plant and additional boiler room, created by well-known technical solutions.

 Option 2

The operating mode of option 2 EU with a minimum (reduced) heat supply to the consumer
During this mode (see Fig. 4, 5) of the operation of electric power units (for example, during the non-heating season, etc.), the position of the valves on the circulation paths of the working fluid and coolant are as follows: stop valves 5, 7 - open; stop valves 10, 28 and 29 are closed. The start-up of compressors 1, 4, turbines 25, as well as turbines 24, are carried out by electric generators 12 and 26, respectively, operating at that time as starting motors from an external power supply network. Thus, in the process of operation of the EC, the compressor 1 sucks in the gaseous working fluid of the installation (for example, helium) cooled in the refrigerator 27 (up to _Тl = 30 ^o C) with the initial pressure, for example, 20 ata and compresses it to a pressure of 31 ata, as a result whereby the temperature of helium rises to a value of T _s (88 ^o C). Next, helium enters the refrigerator 3, where it is again cooled to T _and (≈30 ^o C), and then enters the compressor 4, which compresses the gas, for example, to 121.3 at. As a result of this compression, gas with a temperature T _k = 250 ^° C is released from the compressor 4. Then, under the action of compressors 1 and 4, this gas through the open shutoff valve 5 enters the heated side of the heat exchanger-recuperator 6, which serves as a regenerator in this operating mode of the EA. In the heat exchanger-recuperator 6, due to the heat of the gas exiting the turbine 25, the helium is regeneratively heated (for example, to T _l = 490 ^o C at a temperature of the gas exiting the turbine T _g - 510 ^o C) and then through the open valve 7 enter the first EU heater - nuclear reactor 22, where it is heated at constant pressure (for example, to T _a = 850 ^o C). Next, the compressed and heated working fluid of the installation enters the gas turbine 24 and, as a result of expansion, rotates it due to its kinetic energy. The turbine 24 transfers its mechanical energy to the generator 26 generating electricity. As a result of useful work in the turbine, the temperature of the expanded working fluid of the installation decreases (for example, from T _a = 850 ^o C to T _b = 510 ^o C). Further, the working fluid exiting the turbine 24 with a pressure of 49 atm enters for reheating in the second EU heater - a nuclear reactor 23, where it is heated, for example, to a temperature T _at = 850 ^o C. After the reactor 23, the heated helium enters the turbine 25 similarly to the above. bringing it into rotation. As a result, the turbine 25 drives, in addition to compressors 1 and 4, also a second electric generator 12. Then, cooled (for example, to T _g = 510 ^o C) and expanded to a pressure of 20 ata, helium enters the heating side of the heat exchanger-recuperator 6, where As a result of the aforementioned regenerative heating of the working fluid compressed in the compressor 4, it is cooled to a temperature (for example, to T _d = 270 ^o C), sufficient for use in heat consumption. In this regard, the gas with the specified temperature T _d enters as a heating medium in the gas cooler 13, where it is cooled by the heat carrier of the intermediate heat exchange circuit to an acceptable temperature (T _e = 110 ^o C). After gas cooler 13, the working fluid is cooled in the cooler 27 to the lowest cycle temperature (e.g., up to T _x = 30 ^o C), after which the gas is again routed to the suction of the compressor 1. Thus changes in the working fluid cycle installation state closes. For the above-described cooling of the working fluid from the temperature T _d to T _e (see Fig. 5), a coolant (for example, the same gas that is used for the working fluid of the installation) is pumped through the circulator 33 through the heated side of the gas cooler 13, which transfers received from the working fluid is heat to the heat carrier (for example, water) of the network circuit of the heat consumer, along which the said coolant is pumped by the circulator 35.

 Quantitative assessments of the above option 2 of the proposed EA in the mode of its operation with a minimum supply of thermal energy to the consumer.

 The absolute electrical efficiency of the EU is 46%.

Причем такую же, как в примере для варианта 1 ЭУ максимальную мощность нагревателей ЭУ - 600 МВт (т). Например, известно, что с такой же тепловой мощностью в настоящее время американской фирмой "Дженерал Атомик" совместно с российскими специалистами проектируется однореакторная ядерная газотурбинная установка, предназначенная для производства только электрической энергии (см. , например, журнал "Nuclear Europe Worldocan", N 7/8, 1993, p. 71).The ratio of heat output to the consumer through the gas cooler 13 (Q _t2 ), to the power of the heating installation

And the same as in the example for option 1 of the EA maximum power of the EU heater is 600 MW (t). For example, it is known that, with the same heat output, the General Atomic American company is currently developing, together with Russian specialists, a single-reactor nuclear gas turbine unit designed to produce only electric energy (see, for example, the journal Nuclear Europe Worldocan, N 7 / 8, 1993, p. 71).

 Then the electric power produced by the EU will be - 276 MW (e).

 The heat output to the consumer (via gas cooler 13) is 137.2 MW (t).

 The fuel heat utilization coefficient is 68.9%.

 The thermodynamic efficiency coefficient of the cycle is 54.8%.

 The operating mode of option 2 EI with a maximum (increased) heat supply to the consumer.

 The differences in the operation of the power plant in this mode from the above are the following (see figures 4 and 6).

Stop valves 5 and 7 are switched to the "closed" position, and valves 10, 28 and 29 to the "open" position. As a result, the working fluid of the installation, compressed in the last (in the second) compressor 4, with the same flow rate as in the previous mode of operation of the EA, bypasses the heat exchanger 6 through the bypass pipe 9 through the open fittings 10 to the first heater of the EA - a nuclear reactor 22. When this, the power of the reactor 22 is increased correspondingly expanded in this mode, the temperature range of the heated working fluid. That is, for the selected quantitative intake, the gel is heated in the reactor 22 to T _a = 850 ^o C not from the temperature T _l = 490 ^o C, but from the temperature T _k = 250 ^o C. As a result, through gas turbines 24 and installed after the reactor 23 the turbine 25 passes the same as in the previous mode of operation, the flow of the working fluid with the same values of the input temperature and pressure, as a result of which the electric generators 26 and 12 generate the same total electric power.

The difference between the operation of the heat exchanger-recuperator 6 in this operating mode from the previous one is that with the help of the opened valves 28 and 29, gas is pumped through the gas intermediate heat exchanger circuit 30 by the circulator 30 of the gas intermediate, which transfers the heat received in the heat exchanger-recuperator 6 to the consumer’s heat transfer medium heat through the heat exchanger 31. As a result, the circulator 32 of the network circuit, pumping the coolant (for example, water vapor or water) through the heated side of the heat exchange nick 31 further network delivers heated coolant to the thermal energy consumers. Thus, through the heat exchanger 31 to the consumer can be issued thermal energy of medium potential, that is, with a temperature of more than 400 ^o C.

 Quantitative assessment of the operation of option 2 EA in the considered mode of its operation.

 The absolute electrical efficiency of the EU is 34.2%.

За счет расширившегося диапазона температур нагреваемого газа суммарная тепловая мощность нагревателей в этом режиме увеличивается с 600 МВт до 808 МВт(т).The ratio of the values of the additional thermal power supplied to the consumer in this mode through the heat exchanger 6 (Q _t1 ), to the total power of the unit heaters in the previous mode of operation

Due to the expanded temperature range of the heated gas, the total thermal power of the heaters in this mode increases from 600 MW to 808 MW (t).

 Electric power of EU - 276 MW (e) - const.

 The heat output to the consumer through gas cooler 13 is 147.2 MW (t).

 The additional heat output of a more average potential given to the consumer through the heat exchanger 6 is 206 MW (t).

 The total heat output to the consumer is 343.2 MW (t).

 The fuel heat utilization rate is 76.8%.

 The coefficient of thermodynamic efficiency of the EU cycle is 55.4%.

 Thus, when the option 2 of the EA is switched from the operating mode with the minimum supply of thermal energy to the consumer in the operating mode with the maximum thermal energy output to the consumer, the following positive factors of the claimed technical solution are realized.

 While maintaining the electric power (276 MW) produced by electric power generators of the EU, the coefficient of fuel heat use increases from 68.9 to 76.8% (by 7.9 abs.%); the coefficient of thermodynamic efficiency of the EU cycle increases from 54.8 to 55.4% (by 0.6 abs.%), and the total heat output to the consumer increases by 2.5 times (by 206 MW). At the same time, the potential of heat supplied to the consumer increases by 2 times.

Therefore, by analogy with the above-mentioned option 1 EI, the proposed solution eliminates the need for the construction and operation of an additional boiler house that produces the average potential heat with a temperature of more than 300 - 400 ^o C. during the periods of maximum consumption.

 The efficiency of nuclear-fired boiler plants is slightly higher than that of fossil-fired boiler plants and is between 0.92 and 0.95. In this regard, the nominal thermal power of the additional boiler house on nuclear fuel should be 1 / 0.95 - 1 / 0.92 = 1.05 - 1.08 times the value of the additional thermal power that is issued to the consumer by the proposed method of operation from a single power plant producing electric and thermal energy.

 As a result, for the quantitative example of option 2 of the EU under consideration, the above factors determine the following production and business indicators.

Nominal thermal power of an additional nuclear boiler plant producing medium potential heat will be N _k = 1.08 • 206 = 222 MW (t). The cost of building the specified additional nuclear boiler plant will be 95 million dollars. USA.

 The cost of building the main well-known nuclear heat and power plant (APEC) producing electricity with a nominal capacity of 276 MW and low-potential thermal energy with a capacity of 137.2 MW (corresponds to the operating mode of the proposed electric power plant with a minimum output of thermal energy to the consumer) will be ≈260 million USD.

 Consequently, the total capital cost of building based on the well-known technical solutions of the additional nuclear boiler room and the main nuclear power plant will be 95 + 260 = 355 million dollars. USA.

 At the same time, capital expenditures for the construction of a unified thermal power station created according to the proposed method, which will solve the problems posed to the above-mentioned well-known boiler houses and nuclear power plants, will amount to ≈ 275 million dollars. USA, that is, a smaller value than 355 million dollars.

 In connection with the foregoing, for a single APEC, based on the considered option 2 of the proposed EU, the saving of only capital costs as a result of the implementation of the claimed invention can be (355 - 275/355) • 100% = 22.5% of the amount of capital costs required for construction APEC and an additional nuclear boiler house, created according to well-known technical solutions.

 In addition, taking into account the above (8%) economy of fuel that is irrationally “burned” in an additional nuclear boiler house, the annual savings in operating costs resulting from the implementation of the proposed technical solution will be at least 25% of the total annual operating costs required during the operation of the nuclear power station and additional nuclear boiler room, created by well-known technical solutions.

 It should be noted that, in addition to stationary use in industry, it seems very promising to use the proposed technical solution (based on option 2 of electric power plants) for floating nuclear power plants that are needed for electricity and heat supply to the basins of northern rivers, the coasts of the northern and Far Eastern seas, as well as, for example, for desalination of sea water.

 Option 3

 The operating mode of option 3 EA with a minimum (reduced) heat supply to the consumer.

 During this operating mode (see Figs. 7 and 8), the actuator positions of the valves in the circulation paths of the working fluid and coolants are as follows: stop valves 5 and 7 are open, and valves 10, 28 and 29 are open. For example, helium with an ionizing additive (up to 0.1%) made, for example, in the form of cesium, is used as the working fluid of the installation.

The start-up of the compressors 1, 4, 37 and the turbine 25 is carried out by an electric generator 12, which at this time works by a starting electric motor from an external power source. Thus, in the process of operation of the EC, the compressor 1 draws in the working fluid of the installation (for example, up to T _e = 30 ^o C) cooled in the refrigerator 27 (initial pressure, for example, 2 ata) and compresses it to, for example, 2.8 ata, in causing the temperature to rise to a value (T _x = 75 ^o C. Further, helium is successively cooled to T _s = 30 ^o C in a refrigerator 3, compressed to a pressure of 4 atm in compressor 4 _(and to T = 75 ^o C), to cool in the refrigerator 38 to T ₌ 30 ^o C and finally compressed (10.9 psia) in compressor 37. Further, under the action of the compressors working eating installation through the open valve 5 is supplied to the heated side of the heat exchanger-recuperator 6 serving in this mode of operation EI regenerator. In the heat exchanger-recuperator 6 due to gas heat released from the turbine 25, the helium is heated (e.g., to T _m = 607 ^o C at a temperature of the gas emerging from the turbine _T = 627 ^o C) and then through the open valve 7 is supplied to the heater EI (the nuclear reactor 22) where it is heated at constant pressure (e.g., up to _Ta = 1500 ^o C). Next, the compressed and heated working fluid of the installation enters the magnetohydrodynamic generator (MHD generator) 36, which produces electricity as a result of the direct conversion of part of the thermal energy of the working fluid into electrical energy, at which the temperature of the expanded working fluid decreases (for example, to T _b = 1027 ^o C) . Next, the working fluid enters the turbine 25 and rotates it as a result of its further expansion. Thus the mechanical energy of the turbine 25, rotating compressors 1, 4 and 37, transmits the generating electric power generator 12. As a result, useful work in the turbine 25, the temperature of the expanded working fluid is reduced (e.g., with T _b = 1027 ^o C to _T = 627 ^o C). Next, the working fluid of the EH exiting from the turbine enters the heating side of the heat exchanger-recuperator 6, where, as a result of the aforementioned regenerative heating of the working fluid coming out of the compressor 37, it is cooled to a temperature (for example, to T _g = 200 ^o C), sufficient for use in heat supply. In this regard, the gas with the indicated temperature T _g enters the gas cooler 13 as a heating medium, where it is cooled by the heat carrier of the intermediate heat exchange circuit to an acceptable temperature (T _d = 110 ^o C). After the gas cooler 13, the working fluid of the installation is cooled in the refrigerator 27 to the minimum temperature of the cycle T _e (for example, T _e = 30 ^o C), after which the gas is again sent to the compressor inlet 1. Thus, the cycle of changing the physical state of the working fluid of the power plant is closed. For the above-described cooling of the working fluid from the temperature T _g to T _d, a coolant is pumped through the circulator 33 through the heated side of the gas cooler 13 (for example, the same as the gas that serves as the main component of the operating fluid of the EA), which transfers heat received from the operating medium of the ES in the heat exchanger 34 a coolant (e.g. water) of a consumer circuit, through which said coolant is pumped by a circulator 35.

 Quantitative assessments of the above option 3 of the proposed EA in the mode of its operation with a minimum supply of thermal energy to the consumer.

 Taking into account the data of the book "Nuclear Gas Turbine Combined Installations" (ed. E. A. Manushin, M, Energoatomizdat, 1993, p. 83 - 84), the absolute electric efficiency of the electric power for the above parameters of the thermodynamic cycle is 50%.

The ratio of the thermal power supplied to the consumer through the gas cooler 13 (Q _t2 ), to the power of the heater EU (Q ' ₁ ) - 10%.

 As for the previous options 1 and 2 of EU, we will accept the maximum power of reactor 22 in this mode - 600 MW (t).

 Then the electric power of the EU will be - 300 MW (e).

The heat output (Q _t ) given to the consumer is 60 MW (t).

 The fuel heat utilization coefficient is 60%.

 The thermodynamic efficiency coefficient of the cycle is 53.4%.

 The operating mode of option 3 EU at maximum (increased) heat energy output to the consumer.

 The differences in the operation of the EU in this mode from the above are as follows (see Fig. 7, 9).

Stop valves 5 and 7 are switched to the “closed” position, and valves 10, 28 and 29 are in the “open” position. As a result, the working fluid of the installation, compressed in the last (in the third) compressor 37, with the same flow rate as in the previous mode of operation of the electric power unit, enters the bypass pipe 9 through the open valve 10 through the open fitting 10 to the electric heater - a nuclear reactor 22. In this case, the power of the reactor 22 is increased correspondingly to the expanded temperature range of the heated working fluid. That is, for the selected quantitative example, the working fluid is heated in the reactor to T _a = 1500 ^o C not from the temperature T _m = 607 ^o C, but from the temperature T _l = 180 ^o C. As a result, through the MHD generator 36 and installed after the turbine 25 passes, doing useful work, the same as in the previous mode of operation, the flow of the working fluid with the same input temperatures and pressures, as a result of which the MHD generator 36 and turbine 25 generate the same total electric power (const).

The difference between the operation of the heat exchanger-recuperator 6 in this operating mode from the previous one is that with the help of the opened fittings 28 and 29, gas (for example, helium) is pumped through the gas intermediate heat exchanger circuit by the circulator 30 of the gas intermediate heat exchanger, which transfers the resulting gas to the heat exchanger 31 heat exchanger 6 heat transfer medium additional "protective" intermediate heat transfer circuit. In this circuit, using the circulator 39, the heat received in the heat exchanger 31 is transferred to the heating side of the heat exchanger 40, which is the heat source of the network circuit of the thermal energy consumer, through which the network coolant is pumped by the circulator 41. Thus. through the heat exchanger 40 to the consumer can be issued thermal energy of medium potential, that is, with a temperature of more than 300 - 400 ^o C.

 Quantitative assessment of the operation of option 3 EA in the considered operation mode.

 The absolute electrical efficiency of the EU is 33.8%.

.The ratio of the additional thermal power supplied to the consumer in this mode through the heat exchanger 6 (Q _t1 ), to the maximum power of the EA heater in the previous (initial) mode of operation

.

 Due to the expanding temperature range of the heated operating fluid of the EA, the maximum thermal power of the reactor 22 in this mode will increase from 600 MW to 887 MW (t).

 Then the electric power of the EU in this mode is 300 MW (e) - const.

 The heat output to the consumer through gas cooler 13 is 60 MW (t).

 Additional heat output to the consumer through heat exchanger 6 is 287 MW (t).

 The total capacity issued in this mode to the consumer is 347 MW (t).

 The fuel heat utilization coefficient is 73%.

 The coefficient of thermodynamic efficiency of the EU cycle is 55%.

 Thus, when variant 3 of the proposed power plant is switched from an operating mode with a minimum supply of thermal energy to a consumer in an operating mode, the following positive factors are realized when the maximum thermal energy is delivered to a consumer.

 While maintaining the electric power (300 MW. El.) Produced by the EA, the coefficient of heat utilization of the fuel of the EA increases from 60 to 73% (by 13 abs.%); the thermodynamic efficiency coefficient of the EU cycle increases from 53.4 to 55.0% (by 1.6 abs.%), and the total heat output to the consumer increases by 4.78 times (by 287 MW). In this case, the potential of the generated heat increases by 2 times.

Therefore, by analogy with the above-mentioned option 2 EI, the proposed solution of option 3 EI eliminates the need for the construction and operation of an additional boiler house that produces average potential heat with a temperature of more than 300 - 400 ^o C. necessary for the consumer during the period of maximum consumption.

 We take the heat source for this additional boiler room as the same as for the main EU - that is, nuclear, due to the fact that the efficiency of the atomic boiler room is 0.92 - 0.95, the rated power of the additional boiler room should be more than 1.05 - 1 , 08 times the amount of additional thermal power that is supplied to the consumer (through heat exchanger-recuperator 6) according to the proposed method of operation from a single power plant that produces electric and thermal energy.

 For the above quantitative example, the above factors will determine the following production and economic indicators of EU.

Nominal thermal power of the secondary nuclear boiler generating average potential heat N _k = 1.08 • 287 = 310 MW (t).

 The cost of building the specified additional nuclear boiler plant will be ≈ 135 million dollars. USA.

 The cost of building the main well-known nuclear power plant producing electricity with a capacity of 300 MW (corresponds to the operating mode of the proposed electric power plant with a minimum supply of thermal energy to the consumer) will be ≈ 280 million dollars. USA.

 Consequently, the total capital costs for the construction based on the well-known solutions of the nuclear boiler house and APEC (which together provide the consumer with the minimum and maximum generation of thermal energy) will amount to 135 + 280 = 415 million dollars. USA.

 At the same time, capital expenditures for the construction of a single nuclear power plant created on the basis of the proposed method of operation, which provide solutions to the production problems posed to the above known boiler houses and nuclear power plants, will be less, namely ≈305 million dollars. USA.

 In connection with the above, for considered option 3 of the proposed power plant, only capital costs savings as a result of the implementation of the proposed technical solution will be (415 - 305/415) • 100% = 26.5% of the total capital costs required for the construction of the nuclear power station and additional nuclear boiler room created according to well-known technical solutions.

 In addition, taking into account the above (8%) annual saving of fuel “burned” in an additional boiler house, the annual savings in operating costs resulting from the implementation of the proposed technical solution will be at least ≈25% of the sum of annual operating costs required during operation of the nuclear power station and additional nuclear boiler room, created according to well-known technical solutions.

 Option 4

 The operating mode of option 4 EU with a minimum (reduced) heat supply to the consumer.

 During this operation mode of a power plant (see FIGS. 10 and 11), the position of the valves on the circulation paths of the working fluid and the coolants of the installation are as follows: stop valves 45 and 46 are open; and valves 43, 44 and 48 are closed.

The start-up of the compressors 1, 4.37 of the turbine 25 is carried out by an electric generator 12, which at this time works by a starting electric motor from an external power supply network. Thus, during operation of the compressor 1 sucks EI cooled in cooler 27 (e.g., to T _x = 30 ^o C) working installation body (initial pressure helium 2 ata) and compresses it to a pressure of 2.98 ata, whereby the working temperature body rises to a value _of T = 82 ^o C. Further, helium is successively cooled to T _u = 30 ^o C in a refrigerator 3, compressed to a pressure of 4.41 psia in compressor 4 (T _c = 82 ^o C), cooled in a refrigerator 38 to T _l = 30 ^o C and finally compress (up to 12.05 ata) in the compressor 37 (T _m = 180 ^o C. Further under the action of the compressors the working fluid of the installation enters the heated side of the first heat exchanger-recuperator 6, which serves as a permanent regenerator of the installation. In the heat exchanger-recuperator 6 due to the heat of the gas exiting the turbine 25, the working fluid is heated (for example, to T _n = 430 ^o C at a temperature of gas turbines T _g = 450 ^o C and then through the open fittings 45 enters the heated side of the second heat exchanger-recuperator 42, which serves as the regenerator of the installation only in this mode of operation.

In the heat exchanger-recuperator 42, due to the heat of the working fluid leaving the MHD generator 36, the gas is once again heated (for example, to T _p = 630 ^o C at the temperature of the gas leaving the MHD generator T _b = 1000 ^o C) and then through open fittings 46 are sent to the EU heater (nuclear reactor 22), where it is heated at constant pressure (for example, up to T _a = 1500 ^o C). From the reactor 22, the compressed and heated working fluid of the installation enters the MHD generator 36, which generates electricity as a result of the direct conversion of part of the thermal energy of the working fluid into electrical energy, at which the temperature of the expanded working fluid decreases (for example, to T _b = 1000 ^o C). Next, the working fluid enters the heating side of the heat exchanger-recuperator 42, where as a result of the aforementioned regenerative heating, the gas exiting the heat exchanger-recuperator 6 is cooled (for example, to T _at = 800 ^o C). Then the working fluid of the installation enters the turbine 25 and rotates it as a result of its expansion and corresponding cooling to T _g = 450 ^o C. In this case, the turbine transfers its mechanical energy to the compressors 1, 4, 37, as well as to the electric generator 12, which, like MHD generator 36, produces electricity. Then, the working fluid of the installation exiting the turbine 25 enters the heating side of the heat exchanger-recuperator 6, where, as a result of regenerative heating of the working fluid emerging from the compressor 37, it is cooled to a temperature (for example, T _d = 200 ^o C), sufficient for its use in heat consumption. In this regard, the gas with the specified temperature T _d enters as a heating medium in the gas cooler 13, where it is cooled by the coolant of the intermediate circuit to an acceptable temperature (T _e = 110 ^o C). After the gas cooler 13, the working material is cooled in the refrigerator 27 to the minimum cycle temperature T _W , after which the gas is again sent to the compressor inlet 1. Thus, the circular thermodynamic cycle of the change in the state of the working fluid of the power plant is closed.

For the aforementioned cooling of the working fluid from the temperature T _d to the temperature T _e through the heated side of the gas cooler 13, a coolant (for example, the same gas that serves as the main component of the installation’s working fluid) is pumped through the circulator 33, which transfers the received heat to the coolant in the heat exchanger 34 (for example, water) of the consumer circuit, through which this coolant is pumped by the circulator 35.

 Quantitative assessments of the above option 4 of the proposed EA in the mode of its operation with a minimum supply of thermal energy to the consumer.

 The absolute electrical efficiency of the EU is 48.3%.

.The ratio of thermal power supplied to the consumer through the gas cooler 13 (Q _t ), to the power of the heater EU - reactor

.

 As for the previous options 1, 2, and 3 EU, we will accept the maximum thermal power of the reactor 22 in this mode - 600 MW (t).

 Then the electric power of the EU will be - 290 MW (e).

 The heat output given to the consumer is 61.8 MW (t).

 The fuel heat utilization rate is 58.6%.

 The coefficient of thermodynamic efficiency of the EU cycle is 51.8%.

 The operating mode of option 4 EI with the maximum output of thermal energy to the consumer.

 The differences between the operation of the power plant in this mode from the above are as follows.

Shut-off valves 45 and 46 are switched to the “closed” position, and valves 43, 44 and 48 are switched to the “open” position. As a result, the working fluid of the unit that exited the heat exchanger-recuperator 6 with the same flow rate as in the previous mode of operation of the electric power unit, bypasses the heat exchanger-heat exchanger 42 through a bypass pipe 47 through open fittings 48 to the electric heater - a nuclear (or thermonuclear) reactor 22 In this case, the power of the reactor 22 is increased correspondingly to the temperature range of the heated working fluid expanded in this mode. That is, for the quantitative example under consideration, helium is heated in the reactor to T _a = 1500 ^o C not from the temperature T _p = 630 ^o C, but from the temperature T _n = 430 ^o C. As a result, it passes through the MHD generator 36 and turbine 25, making useful work, the same as in the previous mode of operation of EI, the flow of the working fluid with the same values of input temperatures and pressures, as a result of which the MHD generator 36 and the electric generator 12 generate the same total electric power together (but with a slightly lower efficiency due to delivery of additional heat to the consumer).

The difference between the operation of the heat exchanger-recuperator 42 in this EU operation mode from the previous one is that with the help of the opened fittings 43 and 44, gas (for example, helium) is pumped through the intermediate heat exchanger circuit circulator 50 through the heated side of this heat exchanger, which transfers the received heat to the heat exchanger 49 coolant of an additional (protective) intermediate heat exchange circuit. In this protective circuit, with the help of the circulator 51, the heat received in the heat exchanger 49 is transferred to the heating side of the heat exchanger 52, which is the heat source of the heat consumer network, through which the heat carrier is pumped by the circulator 53. Thus, high potential heat energy with a temperature can be transmitted through the heat exchanger 52 800 - 950 ^o C, which is necessary for many energy technology industries. The indicated high potential of the heat released to the consumer can, for example, also be used for efficient transportation over long distances (for example, more than 100 km) of heat in a chemically bound state. This so-called chemothermal method of transmitting medium and high potential thermal energy over long distances is based on the property of reversible chemical reactions. For example, CH ₄ + H ₂ O + heat -> CO + 3H ₂ and CO + 3H ₂ -> CH ₄ + H ₂ O + heat (see, for example, the book "Heating systems", L.S. Khrilev, M , Energoatomizdat, 1988, pp. 259-260). The efficiency of energy conversion and transportation according to such a scheme can reach 70 - 90%.

 Quantitative assessment of the operation of option 4 EA in the considered mode of its operation.

 The absolute electrical efficiency of the EU is 39.3%.

The ratio of the values of the additional thermal power issued to the demand in this mode through the heat exchanger-recuperator 42 (Q _W ) to the maximum power of the EA heater in the previous (initial) mode of its operation is 0.23.

 Due to the expanded temperature range of the heated working fluid of the electric power unit, the maximum thermal power of the reactor 22 in this mode will increase from 600 MW to 738 MW (t).

 Then the electric power of the EU in this mode will be - 290 MW (e) - const.

 The heat output to the consumer through gas cooler 13 is 61.8 MW (t).

 The heat output to the consumer through heat exchanger 42 is 138 MW (t).

 The total thermal power supplied to the consumer in this mode of electric power plants is 200 MW (t).

 The fuel heat utilization coefficient is 66.4%.

 The coefficient of thermodynamic efficiency of the EU cycle is 56.3%.

 Thus, when variant 4 of the proposed EA is switched from the operating mode with the minimum supply of thermal energy to the consumer in the operating mode, the following positive factors are realized when the maximum thermal energy is delivered to the consumer.

 While maintaining the electric power (290 MW el.) Produced by the electrical installation, the coefficient of heat utilization of fuel for electric power plants increases from 58.6 to 66.4% (by 7.8 abs.%); the thermodynamic efficiency coefficient of the EU cycle increases from 51.8 to 56.3% (by 4.5 abs.%), and the total heat output to the consumer increases by 3.24 times (by 138 MW). In this case, the potential of the generated heat increases by 3-4 times.

 The foregoing allows us to conclude that, in comparison with the known (prototype) power plants, the proposed solution (as well as for options 1, 2, and 3 power plants) eliminates the need for the construction and operation of an additional boiler house that produces what the consumer needs during periods of maximum high potential heat consumption.

 The heat source for this additional boiler room is the same as for the main power plant - that is, a nuclear one. Due to the fact that the efficiency of an atomic boiler house with a gas-cooled nuclear reactor will be 0.92 - 0.95, the rated power of the additional boiler should be 1.05 - 1.08 times the value of the additional thermal power that is supplied through the heat exchanger-recuperator 42 according to the proposed method of operation from a single power plant producing electrical and thermal energy of specified parameters.

 For the above quantitative example, the above factors determine the following production and economic indicators.

Nominal thermal power of the additional nuclear boiler room N _k = 1.08 • 138 = 150 MW (t).

 The construction cost (capital cost) of the specified boiler house producing high potential heat will be ≈80 million dollars. USA.

 The cost of building the main well-known nuclear power plant, generating electricity with a capacity of 290 MW (e) and low-grade thermal energy with a capacity of 61.8 MW (operating mode with a minimum supply of thermal energy to the consumer) ≈270 million dollars. USA.

 Consequently, the total capital expenditures for the construction of the main ones on the basis of the well-known solutions of the nuclear boiler house and APEC will amount to 80 + 270 = 350 million US dollars.

 In contrast, the capital cost of building a unified nuclear power plant created by the proposed method of operation, which will solve the production problems posed to the aforementioned well-known nuclear boiler plants and nuclear power plants, will be ≈285 million dollars. USA.

 Thus, for the considered option 4 of the proposed EA, the savings only in capital costs as a result of the implementation of the proposed technical solution will be (350 - 285/350) • 100% = 18.6% of the total capital costs required for the construction of the nuclear power station and additional nuclear boiler room created according to well-known technical solutions.

 In addition, taking into account the above (8%) annual saving of fuel that is irrationally “burned” in an additional nuclear boiler room, the annual savings in operating costs resulting from the implementation of the claimed technical solution under option 4 of electric power plants will be at least ≈25% of the total annual operating costs, required during the operation of alternative nuclear power plants and an additional nuclear boiler room, created according to well-known technical solutions.

 Thus, taking into account the considered 4 options for electric power plants, the implementation of the proposed method of operating a power plant that simultaneously produces electric and thermal energy ensures the achievement of the following positive production and economic indicators in various industries.

 While maintaining a constant value of the effectively produced electrical energy, the claimed power plants will operate economically in modes with a minimum (increased) output of thermal energy to the consumer of the specified parameters (low, medium and high potential).

 Regardless of the type of fuel used, and in accordance with modern parameters of closed or open thermodynamic cycles for the claimed options for power plants, when they switch to operation mode with a maximum output of thermal energy to the consumer, the coefficient of heat utilization of fuel of the EA increases from 60 to 80%; the coefficient of thermodynamic efficiency of plant cycles increases from 52 to 56%, and the total heat output to the consumer increases by 2.5–5.0 times (with an increase in the potential of heat generated by 2–4 times).

 In this case, the total maximum thermal power supplied to the consumer can be up to ≈ 40 - 50% of the maximum power of the heater (or heaters) of the installation in the initial mode of its operation with minimal (reduced) heat output to the consumer.

 In addition, in comparison with the known analogues, the claimed technical solution, ensuring the implementation of the task of simultaneous efficient production of electric and thermal energy of the specified parameters while maintaining the nomenclature and the number of basic units of equipment of known power plants, eliminates the need for the construction and appropriate operation of an additional well-known boiler house that produces what the consumer needs periods of maximum heat consumption are medium and high potential heat.

In this regard, the following economic indicators are provided for the implementation of the proposed "Method of operating a power plant and installations for its implementation":
- savings in capital costs during the construction of a heat and power plant (CHP) based on the proposed technical solution will be at least 10 - 25% of the amount of capital costs required for the construction of a CHP and an additional boiler house created according to well-known technical solutions;
- the annual savings in operating costs of the CHPP built on the basis of the proposed power plants will be at least ≈ 25% of the sum of the annual operating costs required for the operation of the above-mentioned CHPPs and an additional boiler house based on well-known technical solutions.

 In addition, it should also be expected that, compared to thermal power plants based on well-known combined-cycle power plants, the combined heat and power plants created on the basis of the proposed technical solution and solving the same production problems (in terms of the amount of generated electric and thermal energy) will also be more economical in terms of capital and operating costs, since the composition of the proposed CHPs does not include steam turbine parts of power plants and numerous systems serving them.

 The above production and economic indicators of the implementation of the proposed technical solution allow us to conclude that it is quite competitive in comparison with the known analogues.

Claims (7)

 1. A method of operating a power plant, in which the working fluid of the plant is compressed in one or, mainly, in two or more compressors with intermediate cooling in a gas cooler, configured to provide heat removal for heating, and / or in the refrigerator due to the transfer of heat to the external environment , then the working fluid is directed to at least one heater, where it is heated to the working temperature, then the working fluid is expanded into compressors and, for example, an electric generator, for driving a turbine, then the working fluid of the installation that worked in the turbine is passed as a heating medium through at least one heat exchanger-recuperator and then through the last gas cooler, made, for example, with the possibility of transferring thermal energy to the consumer, characterized in that during operation of the installation in the maximum or by increased generation of thermal energy to the consumer, the compressed working fluid of the installation is sent to bypass the heat exchanger-recuperator in the heater, the power of which is increased accordingly by expanding the wider temperature range of the heated working fluid, while the heat exchanger-recuperator is connected on the heated side to the selection of heat for energy technology needs and / or heat supply of the consumer, for which at least one circulation heat exchange circuit is used, and during operation of the installation in the mode with minimal or reduced by supplying thermal energy to the consumer, the compressed working fluid is passed as a heated medium through a heat exchanger-recuperator, and the power of the heater installed behind it reduced in accordance with the reduced temperature range of the heated working fluid.  2. The method according to claim 1, characterized in that during the period of increased delivery of thermal energy to the consumer when it is taken from the gas cooler installed behind the first compressor, and when atmospheric air is used as a working fluid in an additional heat exchanger, at least atmospheric air entering the compressor is heated as a part of the flow rate of the working fluid spent in the turbine after passing through the last gas cooler of the cycle, after which the cooled working fluid is released into the atmosphere, while the remaining part of the flow rate of the working fluid spent in the turbine is released into the atmosphere, bypassing the additional heat exchanger.  3. The method according to claim 1, characterized in that the cooled working fluid emerging from the last gas cooler of the cycle is sent for compression to the first compressor of the installation.  4. The method according to claims 1 and 3, characterized in that inert gas or nitrogen, which is heated, for example, in a nuclear reactor, is used as the working fluid of the installation.  5. The method according to claims 1 and 3, characterized in that an inert gas, for example helium, neon or argon with an ionizing additive made, for example, in the form of cesium, and which is heated, for example, in a nuclear reactor, is used as the working fluid of the installation and then, before expansion in the turbine, it is expanded in the electric power generating magnetohydrodynamic generator.  6. A power plant, comprising one or, mainly, two or more compressors combined with, for example, circulation pipes of the working fluid of the installation, with a gas cooler installed between them, configured to provide heat removal for heating, and / or a refrigerator, providing heat transfer to the external environment, the heated side of at least one heat exchanger-recuperator, at least one working fluid heater, made, for example, in the form of an organic fuel combustion chamber and connected to a turbine installed behind it, the outlet from the latter is connected to the heating side of the heat exchanger-recuperator, then connected to the heating side of the last gas cooler of the cycle, the outlet of which is connected to the atmosphere, while the heated side of mainly each gas cooler is connected to the circulation circuit, providing the consumer with a heat energy, characterized in that the connection of the outlet of the working fluid of the installation from the heating side of the last gas cooler of the cycle with the atmosphere is made in parallel flax through a pipeline with shut-off and control valves, as well as through a pipeline equipped with shut-off and control valves connected to the heating side of an additional heat exchanger configured to provide preheating of atmospheric air entering the first compressor of the installation.  7. Installation according to claim 6, characterized in that the heated side of the heat exchanger-recuperator at the inlet and outlet of the working fluid is connected, for example, by pipelines through shut-off valves to the circulating heat-exchange circuit of the heat energy consumer, and pipelines or, for example, cavities connecting its inlet and outlet with the nearest compressor and heater are equipped with shutoff valves, while the specified compressor and heater are interconnected bypassing the heat exchanger-recuperator, for example, a pipeline m, which is equipped with valves.

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