WO2015037076A1 - Système de production d'énergie de chaudière - Google Patents

Système de production d'énergie de chaudière Download PDF

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Publication number
WO2015037076A1
WO2015037076A1 PCT/JP2013/074520 JP2013074520W WO2015037076A1 WO 2015037076 A1 WO2015037076 A1 WO 2015037076A1 JP 2013074520 W JP2013074520 W JP 2013074520W WO 2015037076 A1 WO2015037076 A1 WO 2015037076A1
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WIPO (PCT)
Prior art keywords
heat transfer
steam
temperature
boiler
transfer surface
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PCT/JP2013/074520
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English (en)
Japanese (ja)
Inventor
強 柴田
浩都 草加
雅人 半田
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株式会社日立製作所
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Priority to PCT/JP2013/074520 priority Critical patent/WO2015037076A1/fr
Publication of WO2015037076A1 publication Critical patent/WO2015037076A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B9/00—Steam boilers of fire-tube type, i.e. the flue gas from a combustion chamber outside the boiler body flowing through tubes built-in in the boiler body
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/02—Controlling, e.g. stopping or starting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H8/00—Fluid heaters characterised by means for extracting latent heat from flue gases by means of condensation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • F24H9/20—Arrangement or mounting of control or safety devices
    • F24H9/2007—Arrangement or mounting of control or safety devices for water heaters
    • F24H9/2035—Arrangement or mounting of control or safety devices for water heaters using fluid fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2200/00—Heat sources or energy sources
    • F24D2200/16—Waste heat
    • F24D2200/18—Flue gas recuperation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2220/00—Components of central heating installations excluding heat sources
    • F24D2220/06—Heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0024—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for combustion apparatus, e.g. for boilers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0056—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for ovens or furnaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2230/00—Sealing means
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]

Definitions

  • the present invention relates to a boiler power generation system that generates steam by burning fuel and drives a steam turbine power generation facility.
  • boiler power generation systems that generate high-temperature and high-pressure steam by transferring the heat of high-temperature combustion gas generated by burning fuel to water through heat transfer tubes and supplying it to a steam turbine have been developed in recent years.
  • the minimum load range is about 30% of the rated load, and stable power generation can be continued even in such a minimum load range. In comparison, a decline of about 4% is inevitable.
  • Such a decrease in efficiency is mainly due to a decrease in the flow rate of steam that can be supplied to the steam turbine power generation facility with a decrease in load, resulting in a decrease in power generation efficiency in the steam turbine.
  • the decline in efficiency is also a major factor in the deterioration of efficiency.
  • Patent Document 1 a partition is provided in a flue on the heat transfer surface of the rear part of a boiler where a primary reheater is installed, and divided into two flow paths.
  • Patent Document 1 A structure in which a flow rate adjusting damper is installed at the exit of a road is disclosed.
  • a primary reheater is installed in one of the divided flow paths, and a primary superheater, which is the heat transfer surface of the main steam system, is installed in the other, and the opening of the flow adjustment damper is adjusted during partial loads.
  • a means for suppressing a decrease in reheat steam temperature at low load by allowing a large amount of combustion exhaust gas to pass through the flow path on the primary reheater side is shown.
  • Patent Document 2 Japanese Patent Application Laid-Open No. 59-161603 (Patent Document 2) provides a steam piping system capable of supplying reheat system steam to the main steam system boiler water wall heat transfer surface. Means for increasing the heat recovery of the system are disclosed.
  • One effective means for this is to install a reheat system heat transfer surface in the boiler furnace wall or the flue above the furnace that can directly collect strong radiant heat from the burner flame. .
  • the heat recovery amount of the reheat system can be maintained by strong radiant heat transfer from the flame.
  • the thickness of the reheater heat transfer tube is generally designed to be thinner than that in the main steam system.
  • An object of the present invention is to provide a boiler power generation system that appropriately maintains a heat recovery amount of a reheat system during partial load operation and enables high-efficiency operation with partial load.
  • the boiler power generation system of the present invention has a burner that burns fuel to generate high-temperature combustion gas, and heat generated by the high-temperature combustion gas is collected by a plurality of heat transfer surfaces of the furnace to generate high-temperature and high-pressure steam.
  • a steam turbine power generation system having a steam turbine power generation facility having a steam turbine driven by high-temperature and high-pressure steam generated in the boiler furnace, the high-temperature and high-pressure steam supplied to the high-pressure turbine constituting the steam turbine
  • the water wall heat transfer tube constituting the heat transfer surface of the main steam system provided in the boiler furnace
  • the composite heat transfer surface which is integrally formed structure and reheater heat transfer tube constituting the heat transfer surface of the reheat steam system, characterized by being installed in the furnace wall of the boiler furnace.
  • the equipment block diagram which shows the coal fired boiler electric power generation system which is 1st Example of this invention.
  • the partial view which shows the boiler furnace of the coal fired boiler electric power generation system which is 1st Example shown in FIG.
  • the partial view which looked at the composite heat-transfer surface applied to the boiler furnace of the coal fired boiler power generation system which is 1st Example shown to FIG. 2A from the AA direction.
  • the characteristic view which shows the relationship between the power transmission output in the coal fired boiler power generation system of a comparative example and the Example of this invention, and high temperature reheat steam temperature.
  • the fragmentary figure which shows an example of the composite heat-transfer surface applied to the boiler furnace of the coal burning boiler electric power generation system which is 1st Example shown in FIG.
  • the fragmentary figure which shows another example of the composite heat-transfer surface applied to the boiler furnace of the coal burning boiler electric power generation system which is 1st Example shown in FIG. The fragmentary figure which shows another example of the composite heat transfer surface applied to the boiler furnace of the coal burning boiler electric power generation system which is 1st Example shown in FIG.
  • FIG. 8B is another partial view of the composite heat transfer surface applied to the boiler furnace of the coal fired boiler power generation system according to the second embodiment shown in FIG. 8A as viewed from the direction AA.
  • the apparatus block diagram which shows the coal fired boiler electric power generation system which is 3rd Example of this invention.
  • coal-fired boiler power generation system that is an embodiment of the present invention will be described below with reference to the drawings.
  • present invention is not limited to the examples, and in particular for fuel supplied to the boiler, in addition to coal, liquid fuel such as heavy oil, light oil, kerosene, solid fuel such as biomass chip, natural gas, propane gas, etc. Of gaseous fuel.
  • coal as fuel is finely pulverized by a coal pulverizer (not shown) and then supplied to the burner 4 installed in the boiler furnace 1. Combustion is performed by the supplied air, and high-temperature combustion gas is generated inside the boiler furnace 1.
  • Coal combustion air is distributed and supplied to the burner 4 and the after-air port 3 installed in the boiler furnace 1 from the viewpoint of reducing unburned components and suppressing generation of nitrogen oxides.
  • the heat of the combustion gas generated inside the boiler furnace 1 is received by a plurality of heat transfer surfaces installed in the furnace water wall 30 constituting the boiler furnace 1 and in the boiler furnace 1 and the boiler rear heat transfer surface 2. Then, high-temperature and high-pressure steam is generated by heating water and steam flowing through the heat transfer tubes constituting these heat transfer surfaces.
  • the high-temperature and high-pressure steam generated in the boiler furnace 1 is supplied to a steam turbine power generation facility including a high-pressure turbine 12, an intermediate-pressure turbine 13, a low-pressure turbine 14 and a generator 40, and the steam turbine power generation facility uses the energy of the steam. Convert to electricity.
  • the high temperature generated in the boiler furnace 1 is used.
  • High-pressure steam is supplied to the high-pressure turbine 12 and driven, and the reheated steam that is reheated by recirculating the exhaust steam exhausted from the high-pressure turbine 12 to the boiler furnace 1 has a lower pressure than the high-pressure turbine 12.
  • -Stage reheat-type coal adopting a reheat system in which power generation efficiency is improved by supplying the medium pressure turbine 13 and the low pressure turbine 14 to be steam turbines of the turbine and driving the intermediate pressure turbine 13 and the low pressure turbine 14 A fired boiler power generation system is shown.
  • the water supplied to the boiler furnace 1 is pressurized to about 25 MPa by a boiler feed pump 17 and supplied to the high-pressure feed water heater 18. After being heated to about 300 ° C. by the heater 18, it is supplied to the economizer 9 installed in the boiler rear heat transfer surface 2 of the boiler furnace 1.
  • the heating source that heats the water with the high-pressure feed water heater 18 is covered by extracted steam (not shown) from the steam turbine power generation facility.
  • the water heated by the economizer 9 of the boiler furnace 1 is supplied from below to the furnace water wall 30 constituting the boiler furnace 1, and rises in the heat transfer tube constituting the furnace water wall 30 while the boiler furnace 1 It is heated by receiving the heat of the high-temperature combustion gas generated therein, and further passes through the boiler rear heat transfer surface cage wall 31 and becomes steam.
  • a composite heat transfer surface 32 is provided in the middle of the furnace water wall 30.
  • the boiler furnace 1 is provided with a nose 1b for reducing the cross-sectional area of the combustion gas flowing in the boiler furnace 1 in order to promote mixing of the combustion gas generated inside.
  • the steam that has passed through the boiler rear heat transfer surface cage wall 31 then passes through the low temperature superheater 8 installed in the boiler rear heat transfer surface 2 of the boiler furnace 1 and the high temperature superheater 5 installed in the boiler furnace 1.
  • the heating further proceeds while passing and becomes high-temperature high-pressure steam at about 600 ° C., and the high-temperature high-pressure steam is supplied from the high-temperature superheater 5 through the main steam pipe 23 to the high-pressure turbine 12 constituting the steam turbine power generation facility.
  • the turbine 12 is driven.
  • the high-temperature high-pressure steam supplied from the high-temperature superheater 5 through the main steam pipe 23 is exhausted from the high-pressure turbine 12 after driving the high-pressure turbine 12. It is again supplied to the boiler through the hot steam pipe 25.
  • the exhaust steam of the high-pressure turbine 12 supplied from the high-pressure turbine 12 to the boiler through the low-temperature reheat steam pipe 25 is connected to the reheater heat transfer tube of the low-temperature reheater 6 installed in the boiler rear heat transfer surface 2 and the boiler furnace 1.
  • the reheater heat transfer tubes distributed and supplied to the reheater heat transfer tubes respectively provided on the composite heat transfer surface 32 installed in the low temperature reheater 6 and the composite heat transfer surface 32. After being heated in each of the above, after being mixed and mixed in the vicinity of the inlet of the high-temperature reheater 7 installed on the boiler rear heat transfer surface 2, it is supplied to the high-temperature reheater 7 on the boiler rear heat transfer surface 2 and heated. And generate hot reheat steam.
  • FIGS. 2A and 2B show the structure of the boiler composite heat transfer surface 32 in the coal-fired boiler power generation system of this embodiment.
  • the composite heat transfer surface 32 installed in the boiler furnace 1 includes a water wall heat transfer tube 32a and a reheater.
  • the heat transfer tube 32b is configured to be an integral structure.
  • One reheater heat transfer tube 32b constituting the composite heat transfer surface 32 has a membrane structure in which a metal strip 33 is installed so as to seal a gap between adjacent heat transfer tubes.
  • the other water wall heat transfer tube 32a constituting the composite heat transfer surface 32 has a slit-like shape with the metal strip 33 removed between adjacent heat transfer tubes. An opening is provided.
  • a reheater heat transfer tube 32b is disposed on the back surface of the water wall heat transfer tube 32a constituting the composite heat transfer surface 32, and the reheater heat transfer tube 32b has a low temperature reheat steam pipe 25.
  • the reheater heat transfer tube 32b has a low temperature reheat steam pipe 25.
  • a metal strip 33 is installed between adjacent heat transfer tubes, and this is connected to the membrane structure of the furnace water wall 30, so that the reheater heat transfer tube Even if there is a slit-like opening 32b, the boiler furnace 1 is kept sealed.
  • the steam is heated to about 620 ° C. at the outlet of the high temperature reheater 7 installed in the boiler furnace 1, and the high temperature reheat steam reheated by the high temperature reheater 7 is the high temperature reheater. 7 is supplied to the intermediate pressure turbine 13 constituting the steam turbine power generation facility through the reheated steam pipe 24 to drive the intermediate pressure turbine 13.
  • the exhaust steam after driving the intermediate pressure turbine 13 is sent from the intermediate pressure turbine 13 to the low pressure turbine 14 to drive the low pressure turbine 14, and the steam energy is recovered.
  • a generator 40 is connected to the high-pressure turbine 12, the intermediate-pressure turbine 13, and the low-pressure turbine 14 constituting the steam turbine power generation facility, and thereby steam energy is converted into electric power.
  • the exhaust steam discharged from the low-pressure turbine 14 is cooled by the condenser 15 and returned to water.
  • a cooling source supplied to the condenser 15 from the outside in order to cool the condenser 15 water taken from the ocean or river near the power generation system (not shown) is used.
  • the water generated in the condenser 15 is supplied from the condenser 15 to the low-pressure feed water heater 16 disposed on the downstream side and heated to about 150 ° C. by the low-pressure feed water heater 16, and is supplied by the boiler feed water pump 17. After being pressurized and further heated by the high-pressure feed water heater 18 disposed on the downstream side, it is circulated and reused as feed water to the boiler furnace 1 again.
  • More than 80% of the amount of heat transferred from the high-temperature combustion gas generated by burning fuel in the boiler furnace 1 to each heat transfer surface is due to such radiant heat transfer.
  • the high-temperature combustion gas generated by the combustion of coal is deprived of heat energy by the surrounding heat transfer surface and gradually decreases in temperature, and then passes through the gap of the high-temperature superheater 5 after rising in the furnace, and the rear heat transfer of the boiler Enter face 2.
  • the flue is divided into two by the partition wall 11, and the low-temperature reheater 6 and the low-temperature superheater 8 are provided in each flue passage.
  • economizers 9 are installed downstream of the low-temperature reheater 6 and the low-temperature superheater 8, respectively.
  • An exhaust gas flow rate control damper 10 is installed on the downstream side of the economizer 9 of the two flow paths divided by the partition wall 11, and the flow rate distribution of the exhaust gas passing through both flow paths can be changed.
  • convective heat transfer is the dominant heat transfer form that gives heat energy from the combustion gas to each heat transfer surface, so the flow rate of the exhaust gas flowing around the heat transfer tubes on each heat transfer surface is The larger the size, the more efficiently heat can be transferred.
  • the exhaust gas flow rate adjustment damper 10 adjusts the distribution of the amount of heat collected between the main steam system to which the low-temperature superheater 8 belongs and the reheat system to which the low-temperature reheater 6 belongs by changing the flow velocity around the heat transfer tubes in both flow paths. It has a function.
  • the exhaust gas that has passed through the boiler rear heat transfer surface 2 is discharged from the boiler, and after being subjected to treatments such as denitration, dedusting, desulfurization, and exhaust heat recovery in an exhaust gas treatment facility (not shown), it enters the atmosphere from a chimney (not shown). Dissipated.
  • the ratio of the supply amount of combustion air to the coal supply amount of fuel should not be changed beyond a certain range.
  • the temperature of the flame formed in 1 is small even when the load is partial.
  • the heat transfer efficiency greatly decreases as the flow velocity of the combustion gas decreases on the heat transfer surface installed on the rear heat transfer surface 2 of the boiler where convective heat transfer is dominant.
  • the decrease in the heat collection efficiency is small because the decrease in the flame temperature that determines the radiant intensity is small.
  • FIG. 3 shows the relationship between the power generation load and the reheat steam temperature of the high-temperature reheater in the comparative example having no composite heat transfer surface and the coal fired boiler power generation system according to the embodiment of the present invention.
  • the characteristic diagram of the result of the trial calculation using the tool is shown.
  • the composite heat transfer surface 32 having the structure shown in FIGS. 2A and 2B is installed on the wall surface of the boiler furnace 1 to easily secure heat collection at the time of partial load.
  • Reheat steam temperature reheated by the high temperature reheater 7 even in the lowest load zone (partial load) as shown in FIG. Can be maintained at a high temperature, and the power generation efficiency of the boiler power generation system can be maintained high.
  • FIG. 4 is a partial view showing an example of a composite heat transfer surface applied to the boiler furnace of the coal fired boiler power generation system according to the first embodiment shown in FIG. 1, wherein the boiler furnace 1 is disposed at the upper part of the furnace, and the boiler furnace It is the figure which showed the installation position of the composite heat-transfer surface 32 suitable when the structure of the nose 1b which reduces the flow-path cross-sectional area of the combustion gas which flows through the inside of 1 is provided.
  • the conditions that should be taken into consideration as a suitable installation position of the composite heat transfer surface 32 are: 1) Stable radiant heat can be received from the flame formed in front of the burner even during partial load. 2) Avoid areas that are constantly exposed to high heat loads near the flame, 3) There is little or no ash flying / attaching, and it is easy to detach even if attached.
  • FIG. 5 is a partial view showing another example of the composite heat transfer surface 32 applied to the furnace of the coal fired boiler power generation system according to the first embodiment shown in FIG. .
  • the plate is opposed to the plate surface of the high temperature superheater 5 perpendicularly, and It is preferable to install the composite heat transfer surface 32 on the upper wall surface of the furnace water wall 30 which is also perpendicular to the ground surface.
  • the radiant light easily reaches from the plate gap of the high-temperature superheater 5 so that the condition 1) is satisfied. Moreover, since it stands upright near the uppermost part of the boiler furnace 1, there is little ash flying and the condition 3) is satisfied.
  • FIG. 6 shows the installation position of the composite heat transfer surface 32 which is a partial view showing another example of the composite heat transfer surface 32 applied to the boiler furnace of the coal fired boiler power generation system of the first embodiment shown in FIG. .
  • FIG. 7 is a partial view of the composite heat transfer surface 32 suitable for the boiler furnace 1 of the coal fired boiler power generation system according to the first embodiment shown in FIG. 6 as viewed from the direction AA. As shown in FIG. By using such a complex heat transfer surface 32 structure, an effective composite heat transfer surface can be formed.
  • the furnace water wall heat transfer tube 32a and the reheater heat transfer tube 32b constituting the composite heat transfer surface 32 are alternately arranged so as to form the same surface, and the furnace water wall heat transfer tube 32a is formed.
  • a regenerator heat transfer tube 32b, a metal strip 33 is installed in the gap to form a membrane structure.
  • coal-fired boiler power generation system of the present embodiment it is possible to realize a boiler power generation system that enables high-efficiency operation at a partial load by appropriately maintaining the heat recovery amount of the reheat system during the partial load operation.
  • FIG. 8A is a partial view showing a boiler furnace of a coal fired boiler power generation system according to a second embodiment of the present invention
  • FIG. 8B shows a boiler furnace of the coal fired boiler power generation system as a second embodiment shown in FIG. 8A. It is the fragmentary figure which looked at the applied composite heat-transfer surface from the AA direction.
  • the coal-fired boiler power generation system of this embodiment shown in FIGS. 8A and 8B has the same basic configuration and operational effects as the coal-fired boiler power generation system of the first embodiment shown in FIGS.
  • the description of the configuration and the operational effect common to both will be omitted, and the different configuration and operational effect will be described below.
  • the difference between the coal-fired boiler power generation system of the present embodiment and the coal-fired boiler power generation system of the first embodiment is that the structure of the composite heat transfer surface 32 absorbs the difference in heat elongation generated during boiler operation. In the point.
  • the furnace water wall heat transfer tube 32a and the reheater heat transfer tube 32b are configured to form the composite heat transfer surface 32.
  • the heat pipe 32b has an integral structure, a large thermal stress is repeatedly generated. Therefore, in order to ensure the structural reliability, it is preferable to introduce an absorption structure for the difference in thermal elongation in advance.
  • the structure of the composite heat transfer surface 32 shown in FIG. 8B shows a heat expansion difference absorption structure effective when the composite heat transfer surface 32 adopts the structure of the composite heat transfer surface 32 as shown in FIG. 2B.
  • the part of the membrane structure of the reheater heat transfer tube 32 b constituting the composite heat transfer surface 32 and the membrane structure of the furnace water wall heat transfer tube 32 a constituting the composite heat transfer surface 32 are provided.
  • the part to be made is not connected by a metal member, and a flexible structure member 20 having a sealing property composed of a cloth made of fireproof fiber or the like is installed in the gap between the two, so that the boiler furnace 1 It is configured to effectively absorb the difference in thermal elongation that occurs at the same site while maintaining airtightness.
  • FIG. 9A shows another partial view of the composite heat transfer surface 32 applied to the boiler furnace 1 of the coal fired boiler power generation system according to the second embodiment shown in FIG. 8A as viewed from the direction AA
  • FIG. FIG. 9B shows a partial view of the composite heat transfer surface 32 applied to the boiler furnace 1 of the coal fired boiler power generation system of the second embodiment shown in FIG. 9A as viewed from the direction BB.
  • the furnace water wall heat transfer tube 32a and the reheater heat transfer tube 32b constituting the composite heat transfer surface 32 are not membrane structures.
  • Heater heat transfer tubes 32b are installed in such a way as to pass through holes opened up and down the shielding box 21.
  • the shielding box 21 is made of metal and connected to the furnace water wall 30, the connection between the furnace water wall 30 and the shielding box 21 is prevented so that a high thermal stress is not generated even when the furnace water wall 30 is heated.
  • the structure of the part is composed of a metal member (the detailed structure is not shown) provided with a movable part a shown by a broken line, and as shown in FIG. 9B, It is comprised by the metal member (illustration of detailed structure is omitted) provided with the movable part b shown, and the structure where the shielding box 21 was supported in the form suspended from the furnace water wall 30 is employ
  • the reheater heat transfer tube 32b and the shielding box 21 are not in direct contact with each other, they are not affected by the thermal expansion on the reheater side.
  • the gap between the shielding box 21 and the furnace water wall 30 and the gap between the upper and lower penetrating portions of the shielding box 21 through which the reheater heat transfer pipe 32b penetrates are configured with a cloth made of fireproof fiber as shown in FIGS. 9A and 9B.
  • a flexible structure member 20 having a sealing property is installed, and the airtightness of the boiler furnace 1 and the thermal expansion difference absorption are both compatible.
  • coal-fired boiler power generation system of the present embodiment it is possible to realize a boiler power generation system that enables high-efficiency operation at a partial load by appropriately maintaining the heat recovery amount of the reheat system during the partial load operation.
  • FIG. 10 shows the equipment and piping configuration of a coal-fired boiler power generation system that is the third embodiment of the present invention. Since this embodiment has the same basic configuration and operational effects as the coal-fired boiler power generation system of the first or second embodiment, the description of the configuration and operational effects common to both is omitted and different. A structure and an effect are demonstrated below.
  • the exhaust steam discharged from the high-pressure turbine 12 is supplied in parallel to both the composite heat transfer surface 32 and the low-temperature reheater 6 through the low-temperature reheat steam pipe 25.
  • the exhaust steam discharged from the high-pressure turbine 12 through the low-temperature reheat steam pipe 25 branches from the low-temperature reheat steam pipe 25 so as to reach the heat transfer pipe of the low-temperature reheater 6 installed on the boiler rear heat transfer surface 2.
  • the low-temperature reheater 6 and the composite heat transfer surface 32 are supplied in parallel.
  • the low-temperature reheat steam pipe 25 just before branching into the branch pipe 25a leading to the low-temperature reheater 6 and the branch pipe 25b leading to the composite heat transfer surface 32 includes the low-temperature reheater 6 and the composite
  • a steam temperature measuring device 51 for measuring the steam temperature of the exhaust steam exhausted from the high-pressure turbine 12 supplied to the heat transfer surface 32 and supplied to the low-temperature reheat steam pipe 25 is installed.
  • the branch pipe 25a that branches from the low-temperature reheat steam pipe 25 and reaches the low-temperature reheater 6, and the branch pipe 25b that reaches the composite heat transfer surface 32 are provided with a steam flow rate adjusting valve 52 for adjusting the flow rate of the exhaust steam flowing through the branch pipe 25a and a steam flow rate measuring device 53 for measuring the flow rate of the exhaust steam, respectively, and the branch pipe leading to the composite heat transfer surface 32.
  • a steam flow rate adjusting valve 54 for adjusting the flow rate of the exhaust steam flowing through the branch pipe 25b and a steam flow rate measuring device 55 for measuring the flow rate of the exhaust steam are installed.
  • the exhaust steam is reheated by the low-temperature reheater 6 and reheated steam that has passed through the low-temperature reheater 6, and the exhaust steam is heated by the composite heat transfer surface 32 and passed through the composite heat transfer surface 32.
  • Vapor temperature measuring devices 56 and 57 for separately measuring the reheat steam temperatures are installed in the pipes through which the reheat steam just before the junction where the hot steam merges are respectively installed.
  • the reheat steam that has passed through the low temperature reheater 6 and the reheat steam that has passed through the composite heat transfer surface 32 are merged at the junction and supplied to the high temperature reheater 7.
  • a steam temperature measuring device 58 for measuring the steam temperature of the reheated steam supplied to the intermediate pressure turbine 13 is installed.
  • the steam temperature measuring device 51 for measuring the steam temperature of the exhaust steam exhausted from the high-pressure turbine 12 and supplied to the low temperature reheat steam pipe 25, the steam of the exhaust steam.
  • a steam temperature measuring device 51 for measuring the temperature a steam temperature measuring device 56 for measuring the reheat steam temperature reheated by the low temperature reheater 6 and supplied to the high temperature reheater 7 through the junction, and the composite heat transfer surface 32
  • Steam temperature measuring device 57 for measuring the temperature of the reheated steam supplied to the high-temperature reheater 7 through the junction and the reheated steam supplied to the intermediate pressure turbine 13 after being reheated by the high-temperature reheater 7.
  • a steam temperature measuring device 58 for measuring the temperature is installed.
  • a steam flow measuring device a steam flow measuring device 53 that measures the flow rate of exhaust steam that flows down the branch pipe 25a branched from the low-temperature reheat steam pipe 25 and reaches the low-temperature reheater 6;
  • a steam flow rate measuring device 55 that measures the flow rate of the exhaust steam that flows down the branched branch pipe 25 b and reaches the composite heat transfer surface 32 is installed.
  • a steam flow rate adjusting valve a steam flow rate adjusting valve 52 that adjusts the flow rate of exhaust steam that flows down the branch pipe 25a and reaches the low-temperature reheater 6, and an exhaust steam that flows down the branch pipe 25b and reaches the composite heat transfer surface 32.
  • a steam flow rate adjusting valve 54 for adjusting the flow rate of the steam is installed.
  • the reheat steam temperature control for controlling the temperature of the reheat steam, and the flow distribution control of the reheat steam supplied to the low temperature reheater 6 and the composite heat transfer surface 32.
  • a reheat heat recovery amount control device 60 that performs the above is installed.
  • reheat system heat recovery amount control device 60 among the steam temperature measuring devices, at least a steam temperature measuring device 51 that measures the steam temperature of exhaust steam that is exhausted from the high-pressure turbine 12 and supplied to the low-temperature reheat steam pipe 25; A measured value of the steam temperature measured by the steam temperature measuring device 57 that measures the temperature of the reheated steam reheated at the composite heat transfer surface 32 and supplied to the high temperature reheater 7 through the junction, and the high temperature reheater 7
  • Each of the steam temperatures measured by the steam temperature measuring device 58 that measures the temperature of the reheated steam that is reheated and supplied to the intermediate pressure turbine 13 and the branch pipe 25 b branched from the low-temperature reheated steam pipe 25 are combined.
  • the flow rate of the exhaust steam supplied to the composite heat transfer surface 32 through the branch pipe 25b Based on the measured value of the steam flow rate measured by the steam flow measuring device 55 that measures the flow rate of the exhaust steam reaching the heat transfer surface 32, the flow rate of the exhaust steam supplied to the composite heat transfer surface 32 through the branch pipe 25b.
  • the steam flow rate adjustment valve 52 for adjusting the flow rate of the exhaust steam supplied to the low temperature reheater 6 through the quantity adjustment valve 54 and the branch pipe 25a Even during a load operation, the combined reheat steam temperature that is reheated by the high temperature reheater 7 and supplied to the intermediate pressure turbine 13 can be maintained at a desired reheat steam temperature at which the steam turbine obtains high efficiency. The amount of heat collected on the heat transfer surface 32 is ensured.
  • the flow rate adjusting valves 52 and 54 are operated by the reheat system heat recovery amount control device 60 based on the measured values measured by the steam temperature measuring device and the steam flow measuring device. Then, the flow rate of the exhaust steam supplied to the low-temperature reheater 6 and the composite heat transfer surface 32 is adjusted so that the heat recovery amount of the reheat system in the coal fired boiler power generation system is always in an optimum state. It becomes possible.
  • each transmission is caused by a change in coal properties, a change in combustion state, a change in the ash adhesion state on the transmission surface, etc.
  • the amount of heat collected on the hot surface changes constantly.
  • coal-fired boiler power generation system of the present embodiment it is possible to realize a boiler power generation system that enables high-efficiency operation at a partial load by appropriately maintaining the heat recovery amount of the reheat system during the partial load operation.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)

Abstract

La présente invention concerne un système de production d'énergie de chaudière, qui comprend un équipement de production d'énergie pour turbine à vapeur, qui présente une turbine à vapeur entraînée par une vapeur haute température et haute pression générée par une chaudière. Le système est caractérisé en ce qu'une face de transfert thermique composite, conçue afin que des tubes d'écran d'eau à transfert thermique d'un système de vapeur principal prévu dans un four de chaudière, afin de générer une vapeur haute température et haute pression à fournir à une turbine haute pression qui constitue la turbine à vapeur soient unis structurels à des tubes de transfert thermique de réchauffeur d'un système de vapeur de réchauffage, est installée sur une face de paroi de four du four de chaudière. Il est possible d'obtenir un système de production d'énergie de chaudière, capable de fonctionner efficacement avec une charge partielle, par le maintien adapté de la quantité d'absorption de chaleur du système de réchauffage pendant un fonctionnement en charge partielle.
PCT/JP2013/074520 2013-09-11 2013-09-11 Système de production d'énergie de chaudière WO2015037076A1 (fr)

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PCT/JP2013/074520 WO2015037076A1 (fr) 2013-09-11 2013-09-11 Système de production d'énergie de chaudière

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Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61289205A (ja) * 1985-06-18 1986-12-19 三菱重工業株式会社 多種燃料を使用する変圧運転形貫流ボイラ

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61289205A (ja) * 1985-06-18 1986-12-19 三菱重工業株式会社 多種燃料を使用する変圧運転形貫流ボイラ

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