RU2779808C1 - Method for operation of a universal gas turbine power unit - Google Patents

Abstract

FIELD: power engineering.

SUBSTANCE: method for operation is intended for use in gas turbine power units when converting thermal energy into electricity at thermal power plants operating on all, including solid, types of fuels, and on nuclear power plants with a level of temperature of heat removal from the primary circuit of at least 700 K, raising the efficiency due to the more rational arrangement of working processes. The characterising feature of the method for operation consists in the thermal energy source being distanced from the turbine operating in the mode of actual isothermal working gas expansion as close as possible to the ideal expansion, in accordance with the set isothermality coefficient value of at least 0.9. The basis of the method for operation is a closed Ericsson cycle supplemented by an open Brayton cycle utilising air from the external environment. With the compression ratio of the basic cycle compressor equals 3, additional cycle compressor — 2, and the working gas heating temperature in the heat source equals 1,200 K, the performance coefficient of the unit reaches 61.5% if exhaust heat is absent, and raises up to 65% if present in the amount of 10% of the working gas flow rate in the basic cycle. The actuality of the processes was considered from the indicators of the compression polytrope 1.45 and the expansion polytrope 1.35, the temperature difference at the hot end of the primary heat exchanger 10 K, hydraulic losses 0.1 atm, the temperature of working gas at the entry to the main heat exchanger 325 K and the environment 300 K.

EFFECT: increase in the efficiency of operation.

3 cl

Description

The proposed technical solution relates to the methods of operation of bladed heat engines with indirect heating of the working fluid, designed to convert thermal energy into useful mechanical energy, at thermal power plants that consume any type of fuel, including solid fuel, as well as nuclear ones, in which fast neutron reactors are used, or others with a sufficiently high level of heat removal temperature from the reactor core.

Of the known power gas turbine installations, binary steam-gas turbine installations are currently the most widely used [Zysin L.V. Combined-cycle and gas turbine installations. Ed. Petersburg Polytechnic Institute, 2010], in which the fuel is burned in the combustion chamber of a gas turbine plant at high temperature, and the heat of the working gas exhausted in the gas turbine is a low-temperature source of thermal energy for the steam turbine plant. They use two working bodies and obtain useful mechanical energy separately, by expanding the working gas in a gas turbine and water vapor in a steam turbine. At present, almost all plants in operation are of the binary type, in which the gas turbine part operates in accordance with the Brayton cycle. The efficiency of these installations is about 53%, mainly determined by the temperature of the working gas, which consists of the combustion products of fuel in a compressed air environment at the turbine inlet. Their maximum efficiency does not exceed 65%, it is achieved by burning fuel in liquid or gaseous form in the combustion chamber immediately before entering the gas turbine at a temperature of about 1800 K, which makes it fundamentally impossible to use them as part of thermal solid fuel and nuclear power plants, the maximum temperature in which no more than 120 K, especially since the heat source in them in the form of a boiler or heat exchanger has significant dimensions, is located outside the gas turbine, and mixing of the combustion products of the fuel or coolant of the primary circuit of a nuclear reactor with the working gas of the turbine is not allowed. As a result, at power plants of this type, only steam turbine installations with external heating of water vapor in relation to the turbine are used. At the same time, the maximum efficiency in the case of thermal power plants is 47% and nuclear 33%. As a solution to the problem of increasing the efficiency of coal-fired power plants, the national energy program of Japan for 2020 provides for the creation of a powerful combined-cycle gas turbine plant, the fuel of which was gas obtained as a result of coal gasification. This plant was supposed to achieve an efficiency of 66% at a gas turbine inlet temperature of about 2000K. There is no information about its creation. Obviously, even in this case, the overall efficiency, taking into account losses during coal gasification and gas transportation, will be significantly lower.

The task that the author solves by the proposed method of operation of a universal gas turbine power plant is to create a unified method of plant operation that allows for the most efficient conversion of thermal energy received from any heat source located outside the turbine, which has a relatively low temperature, the implementation of both open and closed cycles, use any gas as an optimal working gas, reduce the dimensions and cost of the units by increasing the pressure at the inlet to the compressor of the gas turbine part of the plant, the possibility of implementing it with a set of fairly simple units, the principles of operation and design of which are widely known.

From this point of view, RU No. 2252323 and multi-cylinder steam turbine plants are defined as analogues of the proposed method [Zlobin V.G. Steam turbine installations of thermal and nuclear power plants. Higher School of Technology and Energy. St. Petersburg State University of Industrial Technology and Design. St. Petersburg, 2020].

RU No. 2252323 describes a binary type gas turbine plant similar to the well-known ones, in which the compressor for compressing the air coming from outside, which is part of the gas turbine part, is made in the form of two separate low and high pressure compressors, between which the compressed air is cooled. However, this not only does not lead to an increase in efficiency, but even slightly reduces it, and the beneficial effect is to increase the specific power. As an analogue, a multi-cylinder steam turbine plant is also considered, in which inter-cylinder intermediate heating is used to eliminate the condensation of water vapor during its expansion in a steam turbine, which is used in nuclear power plants.

The closest to the proposed method of operation, taken as a prototype, is the method of operation of a gas turbine engine, described in RU No. 2726861, the main advantage of which is due to the actual implementation of the Erickson cycle, which makes it possible to achieve an extremely high efficiency of about 68% at a working gas temperature in the turbine of not more than 1200K, in any power range, in contrast to the most well-known modern steam-gas turbine plants having a working gas temperature in the turbine up to 1800K and operating with a sufficiently high efficiency only at powers above 300 MW.

In the method of operation of a gas turbine engine according to RU No. 2726861, atmospheric air from the environment is compressed to the required pressure by a stepwise cooled compressor operating in a mode close to isothermal, enters a heat exchanger, where it is heated due to heat exchange with the working gas exhausted in the turbine, after which the heated compressed air passes through the reheating chamber, in which additional heating takes place to a predetermined temperature due to the combustion of the fuel supplied to the compressed air, after which the formed working gas, consisting of a mixture of combustion products and compressed air, enters the turbine inlet, in which it initially passes through a stationary a grate installed relative to the turbine housing, in which, as a result of adiabatic expansion, the working gas acquires an angular velocity of rotation equal to the angular velocity of rotation of the turbine shaft, and moves to the isothermal part of the turbine, consisting of a number of successively installed stages, each and of which, in turn, is formed from sequentially arranged components, including a block of nozzles fixed relative to the turbine housing, through which fuel is supplied in the amount necessary to implement the process of expanding the working gas in a given stage of the turbine, set close to isothermal, mounted rigidly on the shaft turbine of a rotating nozzle apparatus, in which the working gas is accelerated increasing its kinetic energy in the axial direction by an amount equal to the thermal energy received by it during the combustion of fuel at the stage inlet, and radially directed airfoils installed rigidly on the turbine shaft, through which the kinetic energy of the movement of the working When flowing around them, the gas is converted into useful mechanical energy in the amount equal to the thermal energy from the combustion of the fuel supplied to the stage at its inlet. At the same time, the amount of fuel supplied to each stage, the degree of expansion of the working gas in each and the number of stages as a whole in this part, are interconnected by the condition of sufficient proximity of the process of expansion of the working gas to the isothermal setting of the value of the isothermal coefficient, in the form of the ratio of the mechanical energy produced as a whole in the turbine at the actual expansion of the gas to the same energy produced in the case of an ideal isothermal process of spreading, with the degrees of expansion and inlet temperatures being equal in both cases. Having passed the isothermal part of the turbine, the finally expanded working gas is sent to the active impeller to convert the energy of its rotation into useful mechanical energy, and then, at the outlet of the turbine, it enters the heat exchanger, where, cooling, it heats the air compressed by the compressor, after which it is discharged into the environment.

The main disadvantages of this method, excluding its use in the gas turbine part of the universal power plant of solid fuel thermal and nuclear power plants, is, first of all, the lack of fundamental possibility of heating the working gas in the source of thermal energy outside the turbine, as well as the need to provide stepwise cooling of the compressor and sufficiently large heat exchanger dimensions.

These shortcomings are eliminated by the fact that, according to the proposed method of operation, the working cycle consists of the main gas turbine, close to the closed Erickson cycle, and an additional one, which is used as the Brayton gas turbine cycle, the working gas of which is ambient air, which is heated by the heat released due to cooling. spent in the main cycle of the working gas. Similar to RU No. 2252323, in which the compressor is divided into two parts, between which the heat released during compression is taken, in the proposed method of operation, the gas turbine of the main cycle is divided into a number of series hydraulically connected parts to implement a sufficiently close isothermal expansion process, and if the condition sufficient isothermality of the process of full expansion in the turbine is carried out only when the number of parts is greater than one, then in a multi-cylinder steam turbine, in order to prevent condensation of water vapor during its expansion, the working gas exhausted in the first part of the gas turbine is sent for heating to the maximum possible temperature in the external a source of thermal energy to the turbine, after which it is fed to the input of the second part of the gas turbine, and so on. At the same time, the number of turbine parts, the degree of expansion of the working gas in each part of the gas turbine, to ensure sufficient efficiency of the turbine as a whole, is determined based on the isothermal coefficient of the entire turbine required for this, at least 0.9. The task to be solved by applying an additional cycle to the main one is the production of additional mechanical energy to compensate for the increase in the cost of operating a real uncooled compressor of the main cycle, compared with the stepwise cooled one provided in the prototype, due to the thermal energy obtained during further cooling of the exhausted heat exchanger in the main cycle after the main heat exchanger working gas. In order to increase the compactness of the heat exchangers of the main cycle and its other units, as well as to optimize the properties of the working gas, a closed cycle is provided as the main one, in which, by increasing the pressure at the inlet to the compressor of the main cycle, it is possible to reduce the volumetric flow rate of the working gas required at a given power, mainly cycle. Unlike the prototype, the proposed method of operation provides for a separate heating of the compressed working gas of the main cycle after it leaves the compressor with waste heat from the combustion products of the fuel in the heat source.

Universal power plant, made in accordance with the proposed method, operates as follows. The working gas at a given temperature and pressure enters the compressor, in which it is adiabatically compressed, then goes to a heat exchanger, in which it is heated due to waste heat with a sufficient temperature level, for example, released during cooling of the fuel combustion products in a heat source located outside the gas turbine or other similar, and then enters the main heat exchanger, in which the compressed working gas is heated as a result of heat exchange with the working gas exhausted in the gas turbine, and at the exit from the heat exchanger, having a temperature slightly lower than the temperature of the exhausted working gas at the outlet of the gas turbine, is sent for final heating up to the maximum temperature in the heat source. Upon exiting the heat source, the working gas is directed to the first part of the gas turbine, in which it expands adiabatically and performs mechanical work. From the first part of the gas turbine, the working gas cooled as a result of adiabatic expansion is sent to a heat source, in which it is reheated to the maximum temperature and then enters the next part of the gas turbine, in which it is also adiabatically expanded to the required pressure, and so on. The number of hydraulically connected parts of the turbine in series, which ensure the expansion of the working gas to a given pressure, and, accordingly, intermediate heatings, is determined based on the condition for implementing the required value of the isothermal coefficient to ensure a sufficiently effective expansion process as a whole in the gas turbine. From the outlet of the last part of the gas turbine, the exhaust working gas moves to the main heat exchanger, where it is cooled, thereby heating the compressed working gas entering the main heat exchanger from the waste heat heat exchanger installed at the compressor outlet. At the exit from the main heat exchanger, the exhaust gas is sent to the heat exchanger of the additional cycle, where it is cooled, thereby heating the air from the external environment, compressed by the compressor of the additional cycle before it enters the turbine of the additional cycle, expanding in which it produces useful mechanical energy, after which it is discharged into the environment, and the cooled exhaust gas, in the case of a closed main cycle, is sent to the final heat exchanger to optimize the working gas temperature by exchanging it with a third-party coolant before supplying it to the main cycle compressor; in the case of an open cycle of the gas turbine part of the plant, it is discharged into the environment. Wednesday.

The author has calculated a universal power gas turbine plant operating in accordance with the proposed method in a closed cycle mode. A fuel boiler unit was adopted as a heat source, which provides heating of the working gas to a temperature of 1200K due to the combustion of mineral fuel. The real nature of the processes is taken into account by accepting the value of the compression polytrope 1.45 and the expansion polytrope 1.35, the temperature difference at the hot end of the main heat exchanger is 10 degrees, the value of the pressure drop due to hydraulic losses in the heat exchanger is 0.1 atm. The compression ratio of the main compressor is assumed to be 3, the compressor of the additional cycle is 2. The main cycle turbine consists of six hydraulically connected parts in series, in each of which the expansion ratio corresponds to the value of the expansion isothermal coefficient in the turbine of at least 0.95. At the inlet to the main compressor, the temperature of the working gas, which is taken as nitrogen, is 325 K, which is achieved by cooling it with water in the final heat exchanger; In the absence of waste heat, the working gas exhausted in the main cycle with a temperature of 465 K enters the heat exchanger of the additional cycle and leaves it at 380 K. heat source, the amount of which is taken as 10% of the mass flow rate of the working gas of the main cycle, and decreases to 61.5% in their absence, for example, for a nuclear power plant. According to the results of the calculations, it was also established that the efficiency of the plant operating in accordance with the proposed method exceeds the efficiency of the most modern steam turbine plants at a heating temperature in the heat source above 700K. For comparison, in the above sources, the maximum efficiency of a steam turbine plant reaches 47% at a heating temperature of 850K, the proposed method of operating a gas turbine plant makes it possible to obtain an efficiency of at least 49%.

It follows from the above data that the proposed method of operation of a universal power gas turbine plant, having a slightly lower temperature level of thermal energy sources, can significantly increase, compared to the modern world level, the efficiency of converting thermal energy into useful mechanical energy for all types of power plants using a single principle of organizing processes, makes it possible to maximize the use of already developed and tested units, while ensuring their optimal layout as part of gas turbine plants. The ability to work both in open and closed cycles allows not only the use of inert gas as an optimal working gas in the main cycle, but also to reduce hydraulic losses and flow sections by increasing the pressure at the compressor inlet, and also makes it possible to use in a number of cases, the same units at different capacities, thereby ensuring a high level of unification.

The problem was solved mainly due to the optimal combination of the main cycle, based on the Erickson cycle, and an additional one in the form of a Brayton cycle, operating using air from the environment, the maximum temperature of which in the additional cycle is close to the temperature of the compressed working gas at the outlet of the of the main cycle compressor, by implementing the process of expanding the working gas without changing its chemical composition in the main cycle turbine, sufficiently close to isothermal when the working gas is heated in a heat source located outside the turbine, by controlling the power of the plant by changing the pressure of the working gas at the inlet to the main cycle compressor. This solution has significant novelty and usefulness necessary to be recognized as a patentable invention of the method of operation of a universal gas turbine power plant, which makes it possible to replace with great efficiency not only combined-cycle, but also, in most cases, extremely expensive steam turbine plants.

The method of operation of a universal power gas turbine plant, which is based on the Erickson cycle, in which the air of the external environment enters the compressor inlet, is compressed and sent to a heat exchanger to heat the working gas exhausted in the gas turbine, then additionally heats up, going to the gas turbine for expansion into in a process close enough to isothermal, in which thermal energy is converted into mechanical energy, the exhaust gas from the turbine outlet is sent to a heat exchanger, where, giving off its heat to the air compressed in the compressor, it is finally cooled, after which it is removed from the gas turbine plant. At the same time, the working gas, which during the entire cycle of operation of the universal power plant is unchanged in chemical composition, is supplied at a given pressure and temperature to the main cycle compressor inlet, after compression it enters the heat exchanger for heating due to the heat of the fuel combustion products in the heat source, after which is heated in the main heat exchanger due to the heat of the working gas exhausted in the turbine of the main cycle, then heated to the maximum temperature in the heat source, the energy to which is supplied as a result of fuel combustion or from the reactor cooling circuit, after which the working gas is supplied to the inlet of the gas turbine, consisting from a series of hydraulically connected parts, in each of which the working gas is partially expanded, generating mechanical energy, in the intervals between which the working gas, after adiabatic expansion in the previous part, is sent to the heat source, in which it is heated to a maximum temperature, after Why does it enter the next part, moreover, the number of parts of the gas turbine, the degree of expansion in each of them are interconnected with the total degree of expansion in the turbine of the main cycle by the condition for the implementation of sufficient isothermality of the general expansion process in the turbine in the form of an isothermal coefficient value that provides the necessary efficiency of the installation in general, after the final expansion to a predetermined pressure in the final part of the turbine, the working gas exhausted in the gas turbine enters the main heat exchanger, passing through which it is cooled as a result of heat exchange with the working gas compressed in the compressor, is sent for further cooling to the additional cycle heat exchanger, thereby heating the compressed compressor of the additional cycle, air from the external environment, which, after heating, expands in the turbine of the additional cycle, generating useful energy, after which it is discharged into the external environment, thereby closing the additional cycle, the cooled working the gas is sent to the final heat exchanger, in which its temperature, as a result of heat exchange with an additional heat carrier, reaches a predetermined value, after which it is sent to the compressor at a predetermined pressure, thereby closing the main cycle.

The essential features of a universal power gas turbine plant, in which the proposed method of operation is implemented, is that the working cycle is based on a real version of the Erickson cycle, in which the working gas entering the uncooled compressor at a given temperature and pressure is adiabatically compressed in it to the required pressure, enters the heat exchanger, where it is heated by waste heat, after which it is sent to the main heat exchanger to heat it with the heat of the working gas exhausted in the gas turbine, then it is sent to the heat source for final heating to the maximum temperature, it is fed into the first part of the gas turbine, where the working gas is adiabatically expanding, it produces mechanical energy. From the first part of the gas turbine, cooled during the expansion process, the working gas is sent to heat up to the maximum temperature in the heat source, then it is fed to the next part of the gas turbine, in which it also adiabatically expands to the required pressure, and so on, expanding to a given pressure with an intermediate heated between parts of the turbine. In this case, the number of turbine parts and the degree of expansion in each is determined based on the total degree of expansion of the working gas in the gas turbine and the value of the isothermal coefficient of the turbine, which ensures sufficient efficiency of the installation as a whole.

From the outlet of the last part of the gas turbine, the exhaust working gas is sent to the main heat exchanger, cooling in which it heats the working gas compressed by the compressor of the main cycle, after which, having a temperature higher than the temperature of the compressed working gas at the outlet of the waste heat heat exchanger installed at the outlet of the working gas from the compressor of the main cycle, is sent to the heat exchanger of the additional cycle, where, cooling, it heats the air compressed by the compressor of the additional cycle from the external environment, which, expanding adiabatically in the turbine of the additional cycle, produces useful energy, is then discharged into the external environment, and the working gas of the main cycle with from the outlet of the heat exchanger of the additional cycle is sent to the final heat exchanger to optimize its temperature, after which it is fed to the compressor inlet, thereby closing the main cycle.

The distinctive essential features of the proposed method of operation, valid in all cases, is that the working gas, unchanged in composition, when moving inside the plant at a given temperature and pressure, enters an uncooled compressor, in which it is adiabatically compressed to the required pressure, after which it is sent to the first heat exchanger, in which it is heated by the waste heat of the fuel combustion products in the heat source, moves to the main heat exchanger for further heating as a result of heat exchange with the working gas exhausted in the gas turbine, after exiting from it, the compressed and heated working gas is supplied to the heat source, for the final heating to the maximum temperature, upon reaching which it is sent to the inlet of the gas turbine, which produces the mechanical energy necessary for the operation of the compressor and useful for generating electricity, consisting of a series of hydraulically connected parts in series, in each of which p the working gas expands adiabatically to the required pressure, after which, with the exception of the latter, it is directed to an external heat source for subsequent heating to the maximum temperature before being fed into the next part of the gas turbine, while the number of parts of the gas turbine, expansion degrees in each of them, respectively, intermediate heating, is determined based on the value of the isothermal coefficient of the entire expansion process in the gas turbine, which ensures sufficient efficiency of the entire installation as a whole, after the final expansion in the last part to a predetermined pressure, the working gas exhausted in the turbine is sent to the main heat exchanger, in which it is cooled, due to heat exchange with the compressed working gas coming from the compressor to a temperature that is higher than the temperature of the compressed working gas at the outlet of the waste heat exchanger, then, at the exit from the main heat exchanger, the exhaust working gas enters the heat exchanger additionally th cycle, cooling in which it heats the air compressed by the compressor of this cycle from the external environment, for its subsequent adiabatic expansion with the production of useful energy, and subsequent discharge into the external environment. Upon exiting the heat exchanger of the additional cycle, the working gas enters the final heat exchanger where, as a result of heat exchange with the additional heat carrier, it acquires a predetermined temperature, at which, having a predetermined pressure, it is supplied to the compressor inlet, thereby closing the main cycle.

The distinctive essential features of the proposed method of operation are valid in some cases is that when using a closed cycle in the gas turbine part of the installation, its power is controlled by changing the pressure of the working gas at the inlet to the compressor, that is, changing the mass flow rate of the working gas through the compressor. As heat to ensure the operation of the waste heat exchanger and the final heat exchanger, any sources of thermal energy and heat carriers with a sufficient temperature level can be used.

Literature

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Claims (3)

1. The method of operation of a universal power gas turbine plant, which is based on the Erickson cycle, in which the air of the external environment enters the compressor inlet, is compressed and sent to a heat exchanger to heat the working gas exhausted in the gas turbine, then additionally heats up, going to the gas turbine for expansion in a process close enough to isothermal, in which thermal energy is converted into mechanical energy, from the outlet of the turbine, the exhaust working gas is sent to a heat exchanger, where, giving off its heat to the air compressed in the compressor, it is finally cooled, after which it is removed from the gas turbine plant, characterized in that that the working gas, which during the entire cycle of operation of the universal power plant is unchanged in chemical composition, is supplied at a given pressure and temperature to the inlet of the compressor of the main cycle, after compression it enters the heat exchanger for heating due to the heat of the fuel combustion products to the source e heat, after which it is heated in the main heat exchanger due to the heat of the working gas exhausted in the turbine of the main cycle, then it is heated to the maximum temperature in the heat source, energy to which is supplied as a result of fuel combustion or from the reactor cooling circuit, after which the working gas is supplied to the inlet gas turbine, consisting of a series of hydraulically connected parts, in each of which the working gas is partially expanded, generating mechanical energy, in the intervals between which the working gas, after adiabatic expansion in the previous part, is sent to a heat source, in which it is heated to a maximum temperature, after which it enters the inlet to the next part, and the number of parts of the gas turbine, the degree of expansion in each of them are interconnected with the total degree of expansion in the turbine of the main cycle by the condition for the implementation of sufficient isothermality of the general expansion process in the turbine in the form of the value of the isothermal coefficient and, providing the necessary efficiency of the plant as a whole, after the final expansion to a predetermined pressure in the final part of the turbine, the working gas exhausted in the gas turbine enters the main heat exchanger, passing which is cooled as a result of heat exchange with the working gas compressed in the compressor, is sent for further cooling to the additional heat exchanger cycle, thereby heating the air compressed by the compressor of the additional cycle from the external environment, which, after heating, expands in the turbine of the additional cycle, generating useful energy, after which it is discharged into the external environment, thereby closing the additional cycle, the cooled working gas is sent to the final heat exchanger, in which it the temperature as a result of heat exchange with an additional coolant reaches a predetermined value, after which, at a predetermined pressure, it is sent to the compressor, thereby closing the main cycle. 2. The method of operation according to claim 1, characterized in that the power of the installation during its operation in a closed cycle is controlled by changing the pressure of the working gas at the inlet to the compressor of the main cycle. 3. The method of operation according to claim 1, characterized in that when the unit is operating in an open cycle, air from the environment is supplied to the compressor inlet.