JP2016148343A - Subcritical pressure high temperature thermal power generation plant and subcritical pressure high temperature variable pressure operation once-through boiler - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a thermal power generation plant which can attempt efficiency improvement effectively and of which the power output is small-middle scale capacity (power output of one power generator is 100,000-400,000 KW grade) and a boiler therefor.SOLUTION: A steam condition generated in a boiler and fed to a steam turbine is subcritical pressure and high temperature (higher than a turbine entry port temperature 593°C). For example, a subcritical pressure high temperature thermal power generation plant consists of combustion boiler facilities, steam turbine generator facilities and steam condensate water supply facilities, the boiler facilities consist of a coal pulverizer, a burner, a furnace, a spiral waterwall tube, a fuel economizer, a high temperature superheater, a high temperature reheater, and a steam separator, and the pitch angle of the spiral waterwall tube is set to 10-20 degrees.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a subcritical pressure high temperature thermal power plant and a subcritical pressure high temperature transformer operation once-through boiler, and more particularly to a subcritical pressure high temperature thermal power plant and a subcritical pressure high temperature transformer operation once-through boiler with a small and medium power output.

  In order to reduce CO2 emitted from a thermal power plant composed of a boiler and a steam turbine, the efficiency of the thermal power plant has been improved by increasing the steam pressure and increasing the temperature. Currently, mainly in coal-fired thermal power plants of 600,000 to 1 million KW class, main steam pressure 24.1-25.0MPa (supercritical pressure), main steam temperature 593-600 ° C, reheat steam temperature 593-620 ° C is adopted for commercial machines (for example, Non-Patent Document 1). In general, the vapor condition at a pressure of 24.1 MPa (3500 psi) or higher and a temperature of 593 ° C. (1,100 ° F.) or higher is called ultra-supercritical pressure (USC). The practical application of such super-supercritical steam conditions (steam temperature of 593 ° C. or higher) greatly contributes to the practical application of high-temperature materials with excellent high-temperature strength and corrosion resistance used in boiler tubes, valves, and turbines.

  On the other hand, for small and medium-capacity thermal power plants with a single unit power generation output of 400,000 kW or less, steam conditions of up to 566 ° C have been adopted so far, with the main steam pressure remaining at the subcritical pressure and the turbine inlet steam temperature at the maximum. Has been.

“Hitachi review”, Vol. 80, no. 2, Issued February 1998, pages 61-66

  Many small- and medium-capacity thermal power plants have many years of coal-fired thermal power plants and many are expected to be replaced or renovated. In the replacement and renovation of these existing thermal power plants, efficiency improvement is particularly desired from the viewpoint of CO2 reduction. Of course, improvement in efficiency is also desired when a small-to-medium capacity thermal power plant is newly established.

  Supercritical pressure coal-fired thermal power generation is more efficient and has a lower environmental impact than subcritical pressure coal-fired thermal power generation. As mentioned above, high-temperature materials have been put into practical use for large-capacity thermal power plants that operate under supercritical pressure steam conditions of 593 ° C or higher. If this steam condition is applied to a small- and medium-capacity thermal power plant, it can be expected to improve efficiency.

  However, according to the study by the present inventors, it has been found that in a small and medium-capacity thermal power plant, the assumed efficiency improvement cannot be expected even if the supercritical pressure steam condition is adopted. In other words, when the main steam pressure is raised above the supercritical pressure with a small and medium capacity machine, it approximates to the law of thermodynamics of ideal gas (pressure) × (volume) ÷ (temperature) = constant law, and the ratio increases with pressure rise. As a result, the high-efficiency design of a large-capacity machine becomes difficult due to the restrictions on the height and shape of the first stage cascade of the high-pressure turbine. For example, the first-stage cascade of the high-pressure turbine must be shortened due to the reduction in the steam volume, which increases the internal loss of the turbine and cannot be expected to improve the efficiency corresponding to the cost of supercritical pressure.

  An object of the present invention is to provide a thermal power plant with a small and small power generation output capable of effectively improving efficiency and a boiler used therefor.

The present invention is characterized in that the superheated steam generated by the boiler and supplied to the steam turbine has a subcritical pressure / high temperature (turbine inlet temperature of 593 ° C. or higher). More specifically, the superheated steam with a subcritical pressure of 593 ° C. or higher is a superheated steam with a steam pressure of 16.6 Mpa or higher.

  ADVANTAGE OF THE INVENTION According to this invention, the efficiency of a thermal power plant with a small and small capacity | capacitance power generation output can be improved effectively.

  Problems, configurations, and effects other than those described above will be clarified by the following description of embodiments.

1 is a schematic system diagram showing a system configuration of a subcritical pressure high-temperature thermal power plant according to a first embodiment of the present invention. Sectional drawing which shows the outline of the boiler structure of the Example of this invention. The pressure enthalpy curve figure which shows the characteristic of the Example of this invention. The figure which shows the effect of the efficiency improvement amount in the Example of this invention. The figure which shows the effect of the steam temperature control in the Example of this invention. The figure which shows an example of the steam pressure control in the Example of this invention. The schematic system diagram which shows the system configuration | structure of the subcritical pressure high temperature thermal power plant of Example 2 of this invention.

  Embodiments of the present invention will be described below with reference to the drawings.

  Supercritical pressure thermal power generation is more efficient and has a lower environmental impact than subcritical pressure thermal power generation.However, as described above, the present invention is a thermal power plant with a medium-to-small capacity power generation output targeted by the present invention. We found that even if the steam conditions (rated steam conditions) were changed to ultra-supercritical pressure, we could not expect the improvement in efficiency, and we decided to stop the supercritical pressure of the steam conditions (rated steam conditions) and keep the subcritical pressure. The temperature is increased (the turbine inlet temperature is 593 ° C. or higher) so that the efficiency is effectively improved.

  In the present invention, steam with subcritical pressure and high temperature (turbine inlet temperature of 593 ° C or higher) is supplied to the steam turbine for power generation. It is called a thermal power plant, and a boiler that generates steam under this steam condition is called a subcritical pressure high-temperature transformer operation once-through boiler. In addition, in a thermal power plant with a small-to-medium capacity power generation output to which the present invention is applied, specifically, the power generation output (rated output) of a single power generation device (one of the power generation devices) is 100,000 kW class to 400,000 It is a KW-class thermal power plant. If it exceeds 400,000 KW class, it can be expected that the steam condition will be over 593 ° C and supercritical pressure to effectively improve the efficiency, and there is little need to dare to make the steam condition subcritical pressure. . Moreover, if it is less than 100,000 KW class, the ratio of the amount of heat absorption in the furnace described later becomes too large, and the boiler configuration for realizing a high steam temperature becomes complicated and expensive.

  FIG. 1 shows a schematic diagram of a system configuration of a subcritical pressure high-temperature thermal power plant that is one embodiment of the present invention. The subcritical pressure high-temperature thermal power plant includes a combustion boiler facility 10, a steam turbine generator facility 20, a condensate water supply facility 30, and the like. In the present embodiment, a thermal power plant is constituted by one power generator.

  The combustion boiler facility 10 includes a pulverized coal machine 11, a burner 12, a furnace 13, a spiral water wall tube 14, a economizer 15, a high-temperature superheater 16, a high-temperature reheater 17, a steam-water separator 18, and the like. The detailed configuration of the boiler equipment will be described later.

  The steam turbine generator facility 20 includes a high-temperature high-pressure turbine 21, a high-temperature reheat intermediate-pressure turbine 22, a low-pressure turbine 23, a generator 24, and the like. Reference numerals 25 and 26 denote a main steam stop valve and a steam control valve, respectively.

  The condensate water supply facility 30 includes a condenser 31, a condensate pump 32, a low pressure feed water heater 33, a deaerator 34, a feed water pump 35, a high pressure feed water heater 36, and the like.

  The fuel coal is pulverized into pulverized coal by a pulverized coal machine 11, and then supplied to a burner 12 arranged in a furnace 13, and burns with oxygen in the air to generate heat. The burners 12 are installed and arranged so as to reduce differences in temperature distribution in the furnace 13 and metal temperature of the spiral water wall pipe 14 as much as possible. For example, the burners 12 are arranged opposite to each corresponding pulverized coal machine 11, and the burners 12 are arranged in the same row on both sides of the furnace 13 to burn the pulverized coal as fuel.

  Coal is mainly used as the fuel, but it is also possible to plan the specifications so that oil, biomass, by-product gas, etc. can be co-fired in the furnace 13. For example, when using biomass, the biomass is supplied to the pulverized coal machine 11 and supplied to the burner 12 together with the coal. When using by-product gas, a burner for by-product gas is installed separately. The furnace 13 is provided with a starting oil tank burner (not shown).

  Radiation heat and convection heat due to combustion are used for heating (evaporation / overheating) of pressurized water in the spiral water wall pipe 14 constituting the water wall of the furnace 13. The steam (steam at the furnace outlet) from the spiral water wall pipe 14 is led to the high-temperature superheater 16 through the steam separator 18 as superheated steam.

  The high temperature superheater 16 supplies superheated steam (subcritical pressure superheated steam) having a steam temperature (high temperature high pressure turbine inlet temperature) of 593 ° C. or higher to the high temperature high pressure turbine 21. High-temperature superheated steam having a subcritical pressure of 593 ° C. or higher drives the high-temperature and high-pressure turbine 21. The high-pressure turbine exhaust steam whose pressure and temperature are reduced by working in the high-temperature high-pressure turbine 21 is guided to the high-temperature reheater 17 and reheated to 593 ° C. or higher. The reheated high-temperature steam of 593 ° C. or higher (subcritical pressure superheated steam) is guided to the high-temperature reheat / intermediate pressure turbine 22 to drive the high-temperature reheat / intermediate pressure turbine 22. The exhaust steam after working in the high-temperature reheat intermediate pressure turbine 22 is guided to the low-pressure turbine 23 to drive the low-pressure turbine 23. The generator 24 is driven by the power of the high-temperature high-pressure turbine 21, the high-temperature reheat intermediate-pressure turbine 22, and the low-pressure turbine 23 to obtain an electrical output.

  The exhaust steam from the low-pressure turbine 23 is guided to the condensate water supply facility 30. The condensate water supply system 30 cools the exhaust steam of the low-pressure turbine 23 by the condenser 31, cools and recovers the latent heat of steam, and returns it to the condensate. The condensate is pressurized by the condensate pump 32, heated by the low-pressure feed water heater 33, deaerated by the deaerator 34, and becomes feed water. The feed water is pressurized by the feed water pump 35, heated by the high pressure feed water heater 36, and then supplied to the economizer 15 as hot pressurized water. In the economizer 15, the water supply before entering the spiral water wall pipe 14 is preheated in advance by the boiler exhaust gas.

  As described above, the practical use of supercritical pressure steam conditions (turbine inlet temperature of 593 ° C. or higher) has been achieved by the practical use of high-temperature materials such as boiler tubes, valves, and turbine materials. Therefore, increasing the steam temperature (turbine inlet temperature of 593 ° C or higher) in a medium- and small-capacity (100,000-400,000kW class) thermal power plant with subcritical pressure steam conditions is a high-temperature material with supercritical pressure. This can be easily realized by applying the above technique.

  In a combined cycle system where steam is generated by an exhaust heat recovery boiler using gas turbine exhaust gas and power is generated by both the gas turbine and the steam turbine, the high pressure main steam part of the subcritical pressure of the exhaust heat recovery boiler flows through Benson. It is known that the steam condition is 600 ° C. However, this is steam generation by an exhaust heat recovery system in which steam is generated by heating a heat exchanger with exhaust gas after driving a gas turbine, and is a technology different from a combustion boiler such as coal. In other words, the exhaust heat recovery system is not a technology that presupposes a supercritical pressure from the viewpoint of the temperature and heat quantity of the exhaust gas, and does not intentionally maintain the subcritical pressure.

  Next, the boiler used for the subcritical pressure high temperature thermal power plant of the present invention will be described in detail.

  2. Description of the Related Art Conventionally, drum boilers are generally used in small and medium capacity sub-critical pressure thermal power plants. However, in a drum boiler that generates saturated steam with an evaporation pipe and a drum and generates superheated steam with a superheater, the steam temperature at the drum outlet is uniquely determined by the saturated steam temperature of the drum operating pressure, and 593 ° C class steam Higher temperature depends on the increase in the heat transfer area of the superheater or the higher temperature of the gas at the inlet of the superheater, and in particular, there are many difficult design issues in the case of coal-fired combustion boilers. Not. That is, in the drum boiler adopted in the conventional subcritical pressure thermal power plant, the steam turbine inlet temperature after the superheater / reheater was highest at 566 ° C / 566 ° C.

  On the other hand, once-through boilers (transformer-operated once-through boilers) used in supercritical pressure thermal power plants are continuously superheated steam without boiling phenomenon in the supercritical pressure state of high-load operation area, Saturated and superheated steam can be generated without the use of a pressure drum by effectively utilizing the nucleate boiling phenomenon in the evaporator tube in the subcritical pressure state of the partial load operation region due to transformer operation (start-stop operation) A steam separator is provided for the transitional response).

  Therefore, in the present invention, a once-through boiler is used in place of the drum boiler in order to realize a high-temperature steam condition with a subcritical pressure and a steam turbine inlet temperature of 593 ° C./593° C. or higher after the superheater / reheater.

The challenge in adopting small- and medium-capacity transformer-operated once-through boilers (particularly coal-fired transformer-operated once-through boilers) is that the rate of heat absorption of the furnace increases as the plant output decreases. The following problems arise when the heat absorption amount of the furnace increases.
(1) The gas temperature at the furnace outlet tends to decrease, and it is necessary to take measures to increase the heat absorption amount of the superheater.
(2) It is necessary to keep the furnace metal temperature rise accompanying the increase in the furnace heat absorption amount within an allowable value.
(3) Since the amount of heat absorbed by the furnace increases, the temperature rise in the superheater is advantageous, but the degree of superheat in the steam / water separator increases and may become excessive.
(4) In order to perform sub-critical pressure once-through operation in the full load operation region of the plant, it is necessary to always maintain the nucleate boiling state to prevent film boiling.

  For example, it is considered that special consideration for increasing the furnace outlet gas temperature and an increase in the heat transfer area of the superheater are necessary for the decrease in the furnace outlet gas temperature. In this case, the heat transfer area of the boiler plant, Care must be taken not to cause a significant increase in volume, weight, etc. and an associated increase in cost. In particular, in the case of plant construction by replacement or renovation of an existing small and medium-capacity thermal power plant (drum boiler), it is desirable that the arrangement space and weight can be planned within the same scale as the existing drum boiler.

  Therefore, in the present invention, a spiral-type once-through boiler that is also used in a supercritical pressure transformer operation once-through boiler is used. A spiral once-through boiler uses a spiral water wall tube as a water wall tube of a furnace. In a large-capacity supercritical thermal power plant, partial load operation is performed by transformation operation, but in order to prevent the vapor pressure from becoming a subcritical pressure during partial load and the nucleate boiling state from becoming a film boiling state, a spiral is used. A water wall pipe is used. In general, the inclination of the spiral water wall pipe (inclination angle of the spiral water wall pipe viewed from the horizontal direction, spiral angle) is about 25 degrees.

In the present invention, it is necessary to always maintain a nucleate boiling state to prevent film boiling in order to perform subcritical pressure once-through operation in the full load operation region of the plant. That is, it is necessary to ensure a nucleate boiling state in the full load operation region of the plant and to ensure a value equal to or higher than the minimum flow velocity in the pipe necessary for preventing film boiling so that stable evaporation control is possible. In addition, in the present invention, in addition to this, as the capacity of the boiler becomes smaller, the ratio of the water pipes constituting the furnace water wall increases, so it is necessary to cope with a decrease in the pipe flow velocity. For this reason, according to the study by the present inventors, in the sub-critical pressure / high temperature spiral-type once-through boiler having a small and medium capacity, the inclination of the spiral water wall pipe is changed to that of the once-through boiler of the supercritical pressure thermal power plant. must be smaller than the inclination of the spiral water wall tubes (by reducing adjusting the inclination angle of the scan Pairaru waterwall tubes, reducing the tubes constituting the furnace waterwall, the flow velocity of the spiral water wall tubes is increased.).

  However, when the inclination of the spiral water wall pipe is reduced, the stress in the vertical direction tends to increase, so it is considered difficult to reduce the inclination from the viewpoint of the spiral pipe water wall strength. In this regard, the present inventors paid attention to the fact that the vapor pressure is a subcritical pressure, and as a result of various studies, the present inventors have reduced the weight even if the inclination of the spiral water wall pipe is reduced (for example, the supercritical pressure is exceeded. It was found that sufficient strength can be ensured by reducing the pipe wall thickness compared to the critical pressure) and lowering the spiral water wall pipe internal pressure.

  Therefore, in the present invention, the inclination of the spiral water wall pipe is made smaller than the inclination (about 25 degrees) of the spiral water wall pipe of the transformer operation once-through boiler of the supercritical pressure thermal power plant. Specifically, the angle of the spiral water wall tube is set within a range of 10 to 20 degrees when viewed from the horizontal direction. Such an inclination of the spiral water wall tube cannot be derived without the knowledge of the present inventors as described above. According to the study by the present inventors, in a trial calculation example of a spiral-type transformer operation once-through boiler of a coal-fired coal whose plant output is 150 MW class to 250 MW class, the angle of the spiral water wall tube is 10 to 20 when viewed from the horizontal direction. It was confirmed that the flow stability was obtained by preventing the film from boiling by setting the temperature within the range. In addition, the effect of improving the reliability of the water wall metal was also confirmed. It was also confirmed that the water wall structure strength could be secured within the range of this inclination.

  FIG. 2 shows an outline of the boiler structure of the embodiment of the present invention. An outline of the range of adoption of the spiral water wall pipe 14 in the boiler furnace 13 is shown. The hatched area including the burner 12 at the lower part of the furnace 13 constitutes a furnace using a spiral water wall pipe. The spiral water wall tube 14 that forms the water wall of the furnace 13 stably generates steam at a subcritical pressure (water critical pressure is approximately 22.0 MPa), thus preventing film boiling in the spiral water wall tube 14 However, in order to ensure a high flow rate and perform a stable operation, it is installed at the above-described inclination angle.

In this embodiment, the steam temperature control boiler of the parallel damper system without gas recirculation is used. The high temperature superheater 16 includes a primary superheater 16a, a secondary superheater 16b, and a tertiary superheater 16c. The high temperature reheater 17 includes a primary reheater 17a and a secondary reheater 17b. ing. Primary superheater 16a and a primary reheater 17a is installed in parallel damper, secondary superheater 16b, tertiary superheater 16c and the secondary reheater 17 b is a high-temperature portion of the combustion exhaust gas of the furnace 13 outlet Has been placed. These arrangements are natural arrangements in terms of conventional boiler design and layout, but are merely examples, and the present invention is not limited thereto. In the secondary superheater 16b and the tertiary superheater 16c in the high-temperature superheater 16, steam is heated by high-temperature combustion exhaust gas at the furnace outlet, and steam with a subcritical pressure of 593 ° C. or higher is generated. Further, in the secondary reheater 17b in the high-temperature reheater 17, the steam is heated by the high-temperature combustion exhaust gas at the furnace outlet, and steam having a subcritical pressure of 593 ° C. or higher is generated.

  In the steam temperature control of the parallel damper system, the gas distribution damper 19 is opened and closed, for example, the passage gas flow rate on the primary reheater 17a side of the parallel damper is increased (decreased), the primary superheater 16a, the economizer By decreasing (increasing) the passing gas amount on the 15th side, heat absorption on the primary reheater 17a side is increased (decreased), and the reheat steam temperature is increased (decreased).

  FIG. 3 shows how subcritical pressure high temperature steam is generated in an embodiment of the present invention. This figure is a pressure-enthalpy diagram for more visually explaining the production of subcritical high temperature steam by the transformer operation once-through boiler of the subcritical high temperature thermal power plant in the embodiment of the present invention. In this figure, for example, a diagram is shown from the feed water point A at the entrance of the economizer 15 to 593 ° C. at the outlet of the high-temperature superheater 16 under the rated conditions of the main steam pressure 16.6 MPa and the main steam temperature 593 ° C.

In the economizer 15, heating is performed in a range that does not cause steaming, and then heating (evaporation / overheating) is performed in the spiral water wall pipe 14 surrounding the boiler furnace 13, and the furnace 13 (spiral water wall pipe 14). At the outlet of the steam / water separator 18 after exiting, the temperature of the point C is reached. In conventional drum boilers, the temperature at the drum outlet is suppressed to the saturation point B of the drum pressure, so it is necessary to heat the temperature difference from point B to point D with the high-temperature superheater 16, but this is technically and economically From the viewpoint, the upper limit is 566 ° C. In this embodiment, a heated from point C in the high temperature superheater 16 to 593 ° C. at the point D, easily be heated up to 593 ° C. at the point D without significantly increasing the heat transfer area of the high temperature overheating 16 Can do.

  FIG. 4 shows an example of the effect of the efficiency improvement amount in the embodiment of the present invention. This figure shows the results of trial calculation of plant efficiency during operation at the rated output. Also, when the steam pressure of a coal-fired thermal power plant with subcritical pressure less than the critical pressure (about 22.0MPa), for example 16.6MPa, the main steam / reheat steam temperature is 538/538 ℃ based on E point 1.00. This is a trial calculation result of the relative improvement in power generation efficiency.

  In this example (F point where the vapor pressure is the same subcritical pressure and the vapor temperature is 600/600 ° C.), an improvement of about 3% in relative value can be expected. Moreover, the efficiency improvement amount of the present embodiment (point F) can be expected to be higher than that of the point G at the same vapor temperature 538/538 ° C. at a supercritical pressure, for example, 25.0 MPa. In other words, while maintaining the steam temperature at 538 ° C and increasing only the pressure from a subcritical pressure of 16.6 MPa to a supercritical pressure of 25.0 MPa, for example, the steam temperature remains at the same subcritical pressure. When the temperature is increased only to 600/600 ° C, the effect of improving the power plant efficiency is greater. The improvement in efficiency in the case of a supercritical pressure with an increased pressure and temperature, for example, 25.0 MPa and a steam temperature of 600/600 ° C. is shown at point H in the figure. However, even if this steam condition is applied to a small- and medium-capacity thermal power plant, as described above, it is not possible to expect an improvement in efficiency due to the internal loss on the turbine side. Note that the steam temperature is 600 ° C, but if the temperature is 593 ° C or higher, an effect almost proportional to the temperature difference can be expected.

  FIG. 5 shows the effect of steam temperature control in the embodiment of the present invention. This figure shows a plant partial load operation region in the case of a subcritical pressure high temperature thermal power plant (subcritical pressure transformer operation once-through boiler) and a conventional drum boiler thermal power plant (drum boiler) according to an embodiment of the present invention. The control characteristics of main steam and reheat steam temperature are shown.

  In this embodiment, the steam temperature holding range is wider than that of the drum boiler, and the efficiency at the same partial load of the plant is improved. That is, in this embodiment, the control characteristic of the main steam / reheat steam temperature can be made constant up to 100 to 50% load, improving the tendency of the reheat temperature to decrease in the drum boiler, and at the time of partial load The effect of plant power generation efficiency can be expected.

  FIG. 6 shows an example of steam pressure control in the embodiment of the present invention. This figure shows the change characteristic of the main steam pressure at the time of partial load operation of the subcritical pressure high-temperature thermal power plant according to the embodiment of the present invention. In this example, the range from the high load zone of the plant to the minimum through-flow load J point is that the steam control valve 26 “open (substantially fully open)” shown in FIG. In the following load zone, the steam control valve 26 performs constant steam pressure throttle operation. In addition, by the control valve control called the nozzle governing method, the change characteristic of the main steam pressure in the partial load operation region by another transformation operation method that maintains the rated steam pressure in the high load region can be applied.

  Moreover, in the Example of this invention, the weight of the water wall of a furnace water wall or a cage wall is settled in the same weight compared with a drum boiler irrespective of a spiral structure by diameter reduction of a water wall pipe. The weight of the heat transfer tubes of the superheater and reheater is that the steam temperature at the outlet of the steam separator at the furnace outlet can be higher than that of the drum boiler by adopting a transformer once-through boiler. Despite the high temperature of 593 ° C. or higher, the weight can be kept at the same level as a drum boiler. The drum, which is a heavy weight of the drum boiler, is omitted, and the weight minus the additional steam / water separator required at start-up is reduced. A reduction effect of about 10% can be expected.

  In addition, by obtaining sufficient superheated steam in the furnace through the application of a once-through boiler for transformer operation, it is possible to eliminate the installation of a gas recirculation device, etc., which is one of the means of steam temperature control in a small and medium capacity coal-fired power plant. Can do. This eliminates the recirculation gas, thereby reducing the amount of combustion gas, making it possible to reduce the weight and volume of the boiler as compared to the existing drum boiler.

  In addition, in the replacement of an existing subcritical pressure drum boiler medium- and small-capacity thermal power plant, there are construction restrictions such as installation area and boiler weight, but according to the embodiment of the present invention, as described above, Since it can be made smaller than the plant, replacement or the like can be performed without any problem.

  FIG. 7 shows a schematic diagram of a system configuration of a subcritical pressure high-temperature thermal power plant according to another embodiment of the present invention.

  The basic configuration is the same as that of the subcritical pressure high-temperature thermal power plant shown in FIG. This embodiment is characterized by the installation and arrangement of the burners 12 for burning the pulverized coal of fuel supplied from the pulverized coal machine 11 in the furnace 13. Fuel is supplied from the same pulverized coal machine 11 to the burners 12 arranged in the same row on both sides of the furnace 13. Although not shown in the figure, two or three pulverized coal machines are provided. The fuel supply from each pulverized coal machine is burner combustion facing two rows and two stages or three rows and three stages, and the fuel is distributed from one pulverized coal machine to the front and rear burners of each burner stage. By configuring in this way, the pulverized coal of fuel can be burned so as to effectively reduce the difference in temperature distribution in the furnace 13, the metal temperature of the once-through spiral water wall tube 15, and the like.

  The present invention is applied to a subcritical pressure high-temperature thermal power plant with medium to small capacity (100,000 to 400,000 kW class) using fossil fuels such as coal and heavy oil, biomass, and by-product gas in steelworks. Is possible. In particular, it can be applied to the replacement and renovation of an existing coal-fired thermal power plant, and the effect is great. Small- and medium-capacity coal-fired thermal power plants are used for industrial private power generation facilities and IPP (independent power generation / wholesale power business), and renewal of these power plants can contribute to efficiency improvement and CO2 reduction. . For example, by applying to the replacement and renovation of old coal-fired power plants with drum-type small and medium capacity that have been operating for more than 40 years, by adding higher temperature of steam conditions and efficiency improvement by the latest technology of the steam turbine body, A relative 3-5% reduction in CO2 due to improved efficiency can be expected.

  In addition, this invention is not limited to an above-described Example, Various modifications are included. For example, the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described. Further, a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment. Moreover, it is possible to add, delete, and replace other configurations for a part of the configuration of each embodiment.

  10 ... combustion boiler equipment, 11 ... pulverized coal machine, 12 ... burner, 13 ... furnace, 14 ... spiral water wall pipe, 15 ... carbonizer, 16 ... high temperature superheater, 16a ... primary superheater, 16b ... secondary Superheater, 16c ... 3rd superheater, 17 ... High temperature reheater, 17a ... 1st reheater, 17b ... 2nd reheater, 18 ... Air / water separator, 19 ... Gas distribution damper, 20 ... Steam turbine Generator equipment, 21 ... High temperature high pressure turbine, 22 ... High temperature reheat medium pressure turbine, 23 ... Low pressure turbine, 24 ... Generator, 30 ... Condensate water supply equipment, 31 ... Condenser, 32 ... Condensate pump, 33 ... Low pressure Feed water heater, 34 ... Deaerator, 35 ... Feed water pump, 36 ... High pressure feed water heater, A ... Water saver inlet water, B ... Drum outlet steam, C ... Steam separator outlet steam, D ... High temperature superheater Outlet steam, E ... 538/538 ℃, F ... 600/600 ℃, G ... 538/538 ℃, H ... 600/600 ℃, J ... Minimum once-through load.

Claims (7)

A subcritical high-temperature thermal power plant composed of combustion boiler equipment, steam turbine generator equipment, and condensate water supply equipment,
The combustion boiler equipment includes superheated steam having a steam condition of subcritical pressure 593 ° C or higher, a superheater that supplies superheated steam having a steam pressure of 16.6 MPa or higher, and reheat steam having a steam condition of 593 ° C or higher. A high temperature reheater to supply,
The steam turbine generator facility includes a high-pressure steam turbine driven by superheated steam having a steam condition of sub-critical pressure of 593 ° C or higher and a steam pressure of 16.6 MPa or higher, and a regenerator having a steam condition of 593 ° C or higher. A reheat medium pressure steam turbine driven by thermal steam,
The subcritical pressure high temperature thermal power plant has a rated output in the range of 100,000 kW to 400,000 kW.   2. The subcriticality according to claim 1, wherein the combustion boiler equipment is a pulverized coal combustion boiler using coal as a main fuel, and a transformer operation once-through boiler using a boiler furnace water wall portion as a once-through spiral system. High pressure thermal power plant.   3. The subcritical pressure high-temperature thermal power plant according to claim 2, wherein the combustion boiler facility co-fires biomass and iron-produced by-product gas as the fuel.   3. The combustion burner according to claim 2, wherein the combustion burners are arranged in a plurality of stages and are arranged to face each other, and the fuel is distributed to the combustion burners provided corresponding to each of the stages and arranged to face each other. Subcritical pressure high-temperature thermal power plant characterized by having a plurality of pulverized coal machines.   The subcritical pressure high-temperature thermal power plant according to claim 2, wherein an inclination of the spiral water wall pipe constituting the furnace water wall portion is set to 10 to 20 ° from a horizontal direction. A sub-critical pressure high-temperature transformer operation once-through boiler used in a thermal power plant with a high-pressure steam turbine and a reheated intermediate-pressure steam turbine and a rated output of a single power generator in the range of 100,000 kW to 400,000 kW,
Equipped with pulverized coal machine, burner, furnace, furnace water wall pipe, economizer, high temperature superheater, high temperature reheater, steam separator,
The furnace water wall pipe is a once-through spiral system,
The high-temperature superheater generates superheated steam having a steam condition of a subcritical pressure of 593 ° C. or higher and a steam pressure of 16.6 Mpa or higher. A sub-critical pressure high-temperature transformer operation once-through boiler characterized by generating hot steam.   The subcritical pressure high-temperature transformer operation once-through boiler according to claim 6, wherein an inclination of the spiral water wall pipe of the furnace water wall pipe is set to 10 to 20 ° from a horizontal direction.

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