WO2012018004A1 - 発電プラント設備およびその運転方法 - Google Patents
発電プラント設備およびその運転方法 Download PDFInfo
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- WO2012018004A1 WO2012018004A1 PCT/JP2011/067659 JP2011067659W WO2012018004A1 WO 2012018004 A1 WO2012018004 A1 WO 2012018004A1 JP 2011067659 W JP2011067659 W JP 2011067659W WO 2012018004 A1 WO2012018004 A1 WO 2012018004A1
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- WIPO (PCT)
- Prior art keywords
- steam
- exhaust heat
- heat recovery
- generator
- steam turbine
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Classifications
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- 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
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- 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
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D19/00—Starting of machines or engines; Regulating, controlling, or safety means in connection therewith
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D17/00—Regulating or controlling by varying flow
-
- 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
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
- F01K23/065—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
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- 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
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
- F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
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- 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
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
- F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
- F01K23/101—Regulating means specially adapted therefor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting from exhaust energy
- F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting from exhaust energy the devices using heat
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C9/00—Controlling gas-turbine plants; Controlling fuel supply in air- breathing jet-propulsion plants
- F02C9/16—Control of working fluid flow
- F02C9/18—Control of working fluid flow by bleeding, bypassing or acting on variable working fluid interconnections between turbines or compressors or their stages
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
- F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
- F02G5/02—Profiting from waste heat of exhaust gases
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/30—Application in turbines
- F05D2220/31—Application in turbines in steam turbines
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- 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
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/14—Combined heat and power generation [CHP]
-
- 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
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the present invention relates to a power generation plant facility including a steam turbine driven by steam obtained by exhaust heat recovery from the diesel engine in addition to a diesel engine for power generation, and an operation method thereof.
- a power plant facility using a diesel engine includes a steam turbine that is driven using steam generated by exhaust heat from the diesel engine (see, for example, FIG. 2 of Patent Document 1 below).
- the steam turbine generator is driven by the steam turbine to generate power using the energy recovered from the exhaust heat.
- the steam turbine generator for exhaust heat recovery is provided separately from the main diesel engine generator connected to the diesel engine.
- This invention is made
- the power plant equipment and the operation method thereof according to the present invention employ the following means. That is, the power plant equipment according to the first aspect of the present invention is a diesel engine, a main generator that generates electric power by the driving force obtained from the diesel engine and supplies power to the system, and is discharged from the diesel engine.
- a steam generator that recovers exhaust heat from the exhaust gas to generate steam, a steam turbine that is driven by the steam generated by the steam generator, and that generates electric power using the driving force obtained from the steam turbine and supplies power to the system
- An induction heat recovery generator to be supplied an exhaust heat recovery side circuit breaker disposed on a power line between the exhaust heat recovery generator and the system, and a steam flow path upstream of the steam turbine
- the control unit includes: When the steam turbine is started, the steam flow rate adjustment valve is increased from the closed state to increase the frequency of the steam turbine and the exhaust heat recovery generator, and the frequency of the exhaust heat recovery generator is After reaching the frequency, the exhaust heat recovery side circuit breaker is connected to supply power to the system, and the opening of the steam flow rate adjusting valve is substantially fully opened, and the steam turbine is operated depending on the frequency of the system. Is.
- the exhaust heat of the diesel engine is recovered by the steam generator, and the steam turbine is driven by the steam generated by the recovered exhaust heat.
- the exhaust heat recovery generator generates electricity by the driving force obtained from the steam turbine.
- the opening of the steam flow rate adjustment valve is increased from the closed state to increase the frequency of the steam turbine and the exhaust heat recovery generator (induction generator), and the exhaust heat
- the exhaust heat recovery side circuit breaker is connected to supply power to the system, and the opening of the steam flow rate adjustment valve is substantially fully opened, depending on the system frequency, and the steam turbine It was decided to operate. That is, it controls so that the rotation speed of a steam turbine is dominated by the frequency of a system
- the cost can be reduced.
- the output capacity of the steam turbine is smaller than that of the diesel engine (for example, 20% or less, typically 10%). degree). Therefore, the main generator driven by the diesel engine is hardly affected even if the rotational speed of the steam turbine is not controlled by the governor governor.
- a pressure control valve is provided on the upstream side of the steam flow rate adjusting valve, and the control unit is configured such that the pressure of the steam flow path becomes a predetermined value or less.
- the pressure control valve is closed.
- control unit bypasses the steam turbine and moves to the downstream side of the steam turbine when the pressure in the steam flow path exceeds a predetermined value. It is preferable to switch the steam flow to the provided condenser.
- the steam flow is switched to the condenser bypassing the steam turbine in order to protect the steam flow path.
- the operation method of the power plant equipment includes a diesel engine, a main generator that generates electric power by the driving force obtained from the diesel engine and supplies power to the system, and the diesel engine.
- a steam generator that recovers exhaust heat from exhausted exhaust gas to generate steam
- a steam turbine that is driven by the steam generated by the steam generator, and a system that generates electric power using the driving force obtained from the steam turbine
- An exhaust heat recovery generator that is inductive to supply electric power, an exhaust heat recovery circuit breaker disposed on a power line between the exhaust heat recovery generator and the system, and an upstream side of the steam turbine
- An operation method for power plant equipment comprising: a steam flow rate adjusting valve provided in a steam flow path; and a control unit for controlling the exhaust heat recovery side circuit breaker and the steam flow rate adjusting valve.
- the control unit increases the frequency of the steam turbine and the exhaust heat recovery generator by increasing the opening degree of the steam flow rate adjustment valve from the closed state when the steam turbine is started, and the exhaust heat recovery generator After the frequency of the system reaches the frequency of the system, the exhaust heat recovery side circuit breaker is connected to supply power to the system, and the opening of the steam flow rate adjustment valve is substantially fully opened, depending on the frequency of the system.
- the steam turbine is operated.
- the exhaust heat of the diesel engine is recovered by the steam generator, and the steam turbine is driven by the steam generated by the recovered exhaust heat.
- the exhaust heat recovery generator generates electricity by the driving force obtained from the steam turbine.
- the opening of the steam flow rate adjustment valve is increased from the closed state to increase the frequency of the steam turbine and the exhaust heat recovery generator (induction generator), and the exhaust heat
- the exhaust heat recovery side circuit breaker is connected to supply power to the system, and the opening of the steam flow rate adjustment valve is substantially fully opened, depending on the system frequency, and the steam turbine It was decided to operate. That is, it controls so that the rotation speed of a steam turbine is dominated by the frequency of a system
- the cost can be reduced.
- the output capacity of the steam turbine is smaller than that of the diesel engine (for example, 20% or less, typically 10%). degree). Therefore, the main generator driven by the diesel engine is hardly affected even if the rotational speed of the steam turbine is not controlled by the governor governor.
- the present invention eliminates the need for a governing governor for adjusting the rotational speed of the steam turbine by controlling the rotational speed of the steam turbine to be governed by the frequency of the system. Thereby, cost can be reduced.
- a power plant facility 1 installed on land includes a diesel engine 5, a main generator 11 connected to the diesel engine output shaft 3, and a high temperature exhausted by the diesel engine 5. It has a steam generator 6 that generates steam from exhaust gas, a steam turbine 7 that is driven by steam generated by the steam generator 6, and an exhaust heat recovery generator 10 that is driven by the steam turbine 7 to generate electric power. Yes.
- the diesel engine 5 includes a supercharger 14 and an exhaust gas pipe 8. One end of a diesel engine output shaft 3 that is an output shaft of the diesel engine 5 is directly connected, and the diesel engine output shaft 3 is rotationally driven. A generator input shaft 4 serving as an input shaft of the main generator 11 is fixed to the other end of the diesel engine output shaft 3 via a coupling 21.
- the supercharger 14 provided in the diesel engine 5 includes a turbine 14A and a compressor 14B provided on the same axis.
- the turbine 14 ⁇ / b> A is driven and rotated by the exhaust gas discharged from the diesel engine 5.
- a compressor 14B provided on the same axis rotates to compress the air. The compressed air is supplied to the diesel engine 5 as combustion air.
- An exhaust gas pipe 8 is connected to the downstream side of the turbine 14 ⁇ / b> A, and the exhaust gas that has finished work in the turbine 14 ⁇ / b> A is guided to the exhaust gas economizer 15 through the exhaust gas pipe 8.
- the diesel engine 5 includes a governor governor (not shown) that adjusts the output rotational speed. The input fuel amount is adjusted by the governor governor, and the output rotational speed is adjusted. The governor governor is controlled by a control unit (not shown).
- the main generator 11 generates power by the rotational output transmitted from the diesel engine output shaft 3 to the generator input shaft 4.
- the electrical output of the generator 11 is guided to the system 40 via an output electric wire 23 and a main circuit breaker (for example, ACB (auto circuit breaker)) 25.
- a main circuit breaker for example, ACB (auto circuit breaker)
- the steam generator 6 includes an exhaust gas economizer 15 and a brackish water separator 16.
- the exhaust gas economizer 15 has a superheater 15A and an evaporator 15B in its flue.
- the superheater 15A and the evaporator 15B are installed in parallel in order from the bottom to the top (from the upstream side to the downstream side of the exhaust gas flow) in the exhaust gas economizer 15.
- High-temperature exhaust gas flows in the flue of the exhaust gas economizer 15 and is released to the atmosphere through a chimney (not shown) connected to the downstream side thereof. Steam is led from the upper part of the brackish water separator 16 to the superheater 15A.
- Water is led from the lower part of the brackish water separator 16 to the evaporator 15B.
- the brackish water separator 16 is supplied with water from the condensate pipe 33.
- Water in the brackish water separator 16 is guided to an evaporator 15B in the exhaust gas economizer 15 by a boiler water circulation pump 17.
- wet steam containing water from the evaporator 15B of the exhaust gas economizer 15 is guided and separated into water and steam.
- the separated steam is led to the superheater 15A in the exhaust gas economizer 15 to be superheated steam.
- the steam turbine 7 includes a turbine 7A, a turbine output shaft 7B, and a steam flow rate adjusting valve 20.
- the turbine 7A is rotationally driven by steam and rotates a turbine output shaft 7B connected to the turbine 7A.
- a steam flow rate adjusting valve 20 provided in the superheated steam pipe (steam flow path) 30 between the exhaust gas economizer 15 and the steam turbine 7 controls the flow rate of steam supplied from the superheater 15A in the exhaust gas economizer 15 to the steam turbine 7. In addition to being fully closed and fully open, it is also possible to adjust the opening at a midway position between fully closed and fully open.
- the steam flow rate adjusting valve 20 is controlled by a control unit (not shown).
- the steam flow rate adjusting valve 20 has a role as a steam stop valve and a role as an acceleration valve for increasing the rotational speed of the steam turbine 7 in accordance with the amount of steam generated. However, it does not have a role as a governor for maintaining the rotation speed of the steam turbine 7 at a predetermined value. Therefore, the opening degree adjustment of the steam flow rate adjusting valve 20 is mainly performed at the time of startup for increasing the speed to the rotational speed of the system.
- a pressure control valve 22 is provided upstream of the steam flow rate adjustment valve 20.
- the opening degree of the pressure control valve is controlled by a control unit (not shown), and the control unit closes the pressure control valve 22 when the steam pressure in the superheated steam pipe 30 becomes a predetermined value or less. This is considered that when the steam pressure becomes a predetermined value or less, the output of the diesel engine 5 decreases and the exhaust heat recovery heat amount decreases, and in such a case, the effect of recovering exhaust heat is sufficient. This is because the steam flow is shut off by the pressure control valve 22 and the operation of the steam turbine 7 is stopped.
- the steam that has finished work in the steam turbine 7 is led to the condenser 18 to be condensed and liquefied.
- the water liquefied in the condenser 18 is pumped up by the condensate pump 19 and guided to the brackish water separator 16 through the condensate pipe 33.
- a bypass pipe 31 branched from the superheated steam pipe 30 and led to the condenser 18 is provided on the upstream side of the pressure control valve 22.
- the bypass pipe 31 is provided with a dump valve 24.
- the opening and closing of the dump valve 24 is controlled by a control unit (not shown).
- the control unit opens the dump valve 24 when the steam pressure on the upstream side of the dump valve 24 exceeds a predetermined value, and the pressure control valve 22 and steam The flow regulating valve 20 is closed.
- the superheated steam in the superheated steam pipe 30 is guided to the condenser 18 bypassing the turbine 7A.
- the exhaust heat recovery generator 10 is an induction generator and is rotated by the driving force of the steam turbine 7 obtained through the turbine output shaft 7B.
- the output power of the exhaust heat recovery generator 10 is guided to an output electric wire 23 on the main generator 11 side through an exhaust heat recovery side circuit breaker (for example, ACB (auto circuit breaker)) 26.
- ACB auto circuit breaker
- the diesel engine 5 starts operation, the diesel engine output shaft 3 directly connected to the diesel engine 5 and the generator input shaft 4 of the main generator 11 rotate.
- the diesel engine 5 is operated at a rated speed (for example, about 514 rpm) so that the generator 11 operates in conformity with the power specifications required by the system 40.
- the governor governor is controlled by a control unit that obtains the rotational speed of the generator 11 and performs feedback control, and thereby the rotational speed of the diesel engine 5 is controlled.
- the power generation output of the generator 11 is sent to the system 40 through the output breaker 25 and the main circuit breaker 25.
- the exhaust gas discharged from the diesel engine 5 is guided to the exhaust gas economizer 15 through the exhaust gas pipe 8.
- the exhaust gas passes through the exhaust gas ecomizer 15, it exchanges heat with the superheater 15A and the evaporator 15B.
- the water in the evaporator 15B becomes wet steam by exchanging heat with the exhaust gas.
- This wet steam is guided to the superheater 15A of the exhaust gas economizer 15 after the moisture is separated by being guided to the brackish water separator 16.
- the steam in the superheater 15A becomes superheated steam by exchanging heat with the exhaust gas.
- the superheated steam is guided to the superheated steam pipe 30.
- the superheated steam guided to the superheated steam pipe 30 is supplied to the inlet side of the steam turbine 7 through the steam flow rate adjusting valve 20.
- the steam turbine 7 is rotationally driven by the introduced steam.
- the turbine output shaft 7B rotates.
- the exhaust heat recovery generator 10 generates electric power by obtaining the rotational force of the turbine output shaft 7B.
- the power generation output of the exhaust heat recovery generator 10 is sent to the output electric wire 23 via the exhaust heat recovery side circuit breaker 26 and finally supplied to the system 40.
- the operation is as follows. First, before starting, the steam flow rate adjusting valve 20 and the pressure control valve 22 are fully closed, and the dump valve 24 is fully opened. When steam is generated by the steam generator 6 and the amount of superheated steam supplied from the superheated steam pipe 30 exceeds a predetermined amount, the steam flow rate adjusting valve 20 is changed from a fully closed state to a slightly opened state. At this time, the pressure control valve 22 is opened and the dump valve 24 is closed. And the opening degree of the steam flow rate adjusting valve 20 is gradually increased, and the rotational speed of the steam turbine 7 is increased. As a result, the rotational speed of the turbine output shaft 7B increases, and the frequency of the exhaust heat recovery generator 10 increases.
- the exhaust heat recovery side circuit breaker When the frequency of the exhaust heat recovery generator 10 reaches the frequency of the grid 40, the exhaust heat recovery side circuit breaker is turned on (electrically connected) from the interrupted state. Thereby, the output power of the exhaust heat recovery generator 10 is supplied to the output electric wire 23 and guided to the system 40 through the main circuit breaker 25. Thereafter, the control unit opens the steam flow rate adjustment valve 20 fully, and basically does not adjust the opening degree (that is, the opening degree is fixed when fully opened). Thereby, the steam turbine 7 is operated depending on the frequency of the system 40.
- the following effects can be obtained.
- the opening of the steam flow rate adjusting valve 20 is increased from the closed state to increase the frequency of the exhaust heat recovery generator 10, and the frequency of the exhaust heat recovery generator reaches the frequency of the system 40.
- the exhaust heat recovery side circuit breaker 26 is connected to supply power to the system, and the opening of the steam flow rate adjusting valve 20 is fully opened, and the steam turbine 7 is operated depending on the frequency of the system 40. That is, control is performed so that the rotation speed of the steam turbine 7 is governed by the frequency of the system 40. Thereby, it is not necessary to install a governing governor that adjusts the rotation speed of the steam turbine 7, and the cost can be reduced.
- the output capacity of the steam turbine 7 is smaller than that of the diesel engine 5 (for example, 20% or less, typically about 10%). Therefore, the main generator 11 driven by the diesel engine 5 is hardly affected even if the rotational speed of the steam turbine 7 is not controlled by the governor governor.
- the output capacity ratio of the steam turbine 7 to the diesel engine 5 is, for example, 20% or less, typically about 10%.
- the present invention is not limited to this, and the steam turbine is more than the diesel engine 5. If the output capacity of 7 is small, the present invention can be applied. Preferably, the output capacity ratio should be less than 50%.
Abstract
Description
すなわち、本発明の第一の態様にかかる発電プラント設備は、ディーゼル機関と、該ディーゼル機関から得た駆動力によって発電するとともに系統へと電力供給する主発電機と、前記ディーゼル機関から排出された排ガスから排熱を回収して蒸気を生成する蒸気発生装置と、該蒸気発生装置によって生成された蒸気によって駆動される蒸気タービンと、該蒸気タービンから得た駆動力によって発電するとともに系統へと電力供給する誘導式とされた排熱回収発電機と、該排熱回収発電機と前記系統との間の電力線に配置された排熱回収側遮断器と、前記蒸気タービンの上流側の蒸気流路に設けられた蒸気流量調整弁と、前記排熱回収側遮断器および前記蒸気流量調整弁を制御する制御部とを備えた発電プラント設備において、前記制御部は、前記蒸気タービンの起動時に、前記蒸気流量調整弁を閉止状態から開度を増大させて前記蒸気タービンおよび前記排熱回収発電機の周波数を上昇させ、該排熱回収発電機の周波数が前記系統の周波数に達した後に、前記排熱回収側遮断器を接続して前記系統に給電するとともに前記蒸気流量調整弁の開度を略全開とし、前記系統の周波数に依存させて前記蒸気タービンを動作させるものである。
本発明の第一の態様では、蒸気タービンの起動時に、蒸気流量調整弁を閉止状態から開度を増大させて蒸気タービンおよび排熱回収発電機(誘導発電機)の周波数を上昇させ、排熱回収発電機の周波数が系統の周波数に達した後に、排熱回収側遮断器を接続して系統に給電するとともに蒸気流量調整弁の開度を略全開とし、系統の周波数に依存させて蒸気タービンを動作させることとした。すなわち、蒸気タービンの回転数が系統の周波数に支配されるように制御する。これにより、蒸気タービンの回転数を調整する調速ガバナを設置する必要がなくなり、コストを低減することができる。
特に、本発明の第一の態様では、ディーゼル機関の排熱によって駆動する蒸気タービンとされているので、ディーゼル機関よりも蒸気タービンの出力容量が小さい(例えば20%以下、典型的には10%程度)。したがって、調速ガバナによって蒸気タービンの回転数を制御しなくてもディーゼル機関によって駆動される主発電機に影響を及ぼすことが殆どない。
本発明の第二の態様では、蒸気タービンの起動時に、蒸気流量調整弁を閉止状態から開度を増大させて蒸気タービンおよび排熱回収発電機(誘導発電機)の周波数を上昇させ、排熱回収発電機の周波数が系統の周波数に達した後に、排熱回収側遮断器を接続して系統に給電するとともに蒸気流量調整弁の開度を略全開とし、系統の周波数に依存させて蒸気タービンを動作させることとした。すなわち、蒸気タービンの回転数が系統の周波数に支配されるように制御する。これにより、蒸気タービンの回転数を調整する調速ガバナを設置する必要がなくなり、コストを低減することができる。
特に、本発明の第二の態様では、ディーゼル機関の排熱によって駆動する蒸気タービンとされているので、ディーゼル機関よりも蒸気タービンの出力容量が小さい(例えば20%以下、典型的には10%程度)。したがって、調速ガバナによって蒸気タービンの回転数を制御しなくてもディーゼル機関によって駆動される主発電機に影響を及ぼすことが殆どない。
図1に示されているように、例えば陸上に設置された発電プラント設備1は、ディーゼル機関5と、ディーゼル機関出力軸3に接続された主発電機11と、ディーゼル機関5が排出する高温の排ガスによって蒸気を生成する蒸気発生装置6と、蒸気発生装置6にて発生した蒸気によって駆動される蒸気タービン7と、蒸気タービン7によって駆動されて発電する排熱回収発電機10とを有している。
ディーゼル機関5に設けられた過給機14は、同軸上に設けられたタービン14Aと圧縮機14Bとを有している。タービン14Aは、ディーゼル機関5から排出された排ガスが導かれ回転駆動される。タービン14Aが駆動されると、同軸上に設けられた圧縮機14Bが回転し空気を圧縮する。圧縮された空気は、ディーゼル機関5に燃焼用空気として供給される。
タービン14Aの下流側には排ガス管8が接続され、タービン14Aにて仕事を終えた排ガスは、排ガス管8を介して排ガスエコノマイザ15に導かれる。
ディーゼル機関5は、出力回転数を調整する調速ガバナ(図示せず)を備えている。調速ガバナによって投入燃料量が調整され出力回転数が調整される。調速ガバナは、図示しない制御部によって制御される。
排ガスエコノマイザ15は、その煙道内に過熱器15Aと蒸発器15Bとを有している。過熱器15Aと蒸発器15Bとは、排ガスエコノマイザ15内を下から上(排ガス流れの上流側から下流側)に向かって順番に平行に据え付けられている。排ガスエコノマイザ15の煙道内には、高温の排ガスが流れ、その下流側に接続された煙突(図示せず)を経て大気に放出される。過熱器15Aには、汽水分離器16の上部から蒸気が導かれる。蒸発器15Bには、汽水分離器16の下部から水が導かれる。
汽水分離器16内は、水と蒸気が上下にそれぞれ分離して収容されている。汽水分離器16には、復水配管33から水が供給される。汽水分離器16内の水は、ボイラ水循環ポンプ17によって排ガスエコノマイザ15内の蒸発器15Bに導かれる。汽水分離器16には、排ガスエコノマイザ15の蒸発器15Bからの水分を含んだ湿り蒸気が導かれ水と蒸気とに分離される。分離された蒸気は、排ガスエコノマイザ15内の過熱器15Aに導かれ過熱蒸気とされる。
蒸気流量調整弁20は、蒸気止め弁としての役割と、蒸気発生量に応じて蒸気タービン7の回転数を昇速するための昇速弁としての役割とを有している。しかし、蒸気タービン7の回転数を所定値に維持するためのガバナとしての役割は有していない。したがって、蒸気流量調整弁20の開度調整は、系統の回転数まで昇速する起動時に主として行われる。
ディーゼル機関5が運転を開始すると、ディーゼル機関5に直接接続されているディーゼル機関出力軸3と、主発電機11の発電機入力軸4とが回転する。ディーゼル機関5は、系統40が要求する電力仕様に適合して発電機11が動作するように、定格回転数(例えば約514rpm)で運転される。例えば発電機11の回転数を得てフィードバック制御を行う制御部によって調速ガバナが制御され、これにより、ディーゼル機関5の回転数が制御される。
発電機11の発電出力は、出力電線23を通り主遮断器25を介して系統40へと送られる。
過熱蒸気は、過熱蒸気管30に導かれる。過熱蒸気管30に導かれた過熱蒸気は、蒸気流量調整弁20を経て蒸気タービン7の入口側に供給される。蒸気タービン7は、導かれた蒸気によって回転駆動される。蒸気タービン7が回転することによってタービン出力軸7Bが回転する。このタービン出力軸7Bの回転力を得て排熱回収発電機10が発電を行う。排熱回収発電機10の発電出力は、排熱回収側遮断器26を介して出力電線23へと送られ、最終的に系統40へと供給される。
先ず、起動前において、蒸気流量調整弁20および圧力制御弁22は全閉とされ、ダンプ弁24は全開とされる。
蒸気発生装置6にて蒸気が生成され、過熱蒸気管30から供給された過熱蒸気が所定量以上となると、蒸気流量調整弁20は全閉状態から微開状態とされる。このとき、圧力制御弁22は開とされ、ダンプ弁24は閉とされる。そして、蒸気流量調整弁20の開度を徐々に大きくしていき、蒸気タービン7の回転数を昇速させる。これによりタービン出力軸7Bの回転数が上昇して排熱回収発電機10の周波数が上昇する。排熱回収発電機10の周波数が系統40の周波数に達すると、排熱回収側遮断器を遮断状態からオン状態にする(電気的に接続する)。これにより、排熱回収発電機10の出力電力は出力電線23へと供給され、主遮断器25を介して系統40へと導かれる。その後、制御部は、蒸気流量調整弁20を全開とし、基本的にその開度の調整は行わない(すなわち全開で開度を固定する)。これにより、系統40の周波数に依存させて蒸気タービン7を動作させる。
蒸気タービン7の起動時に、蒸気流量調整弁20を閉止状態から開度を増大させて排熱回収発電機10の周波数を上昇させ、排熱回収発電機の周波数が系統40の周波数に達した後に、排熱回収側遮断器26を接続して系統に給電するとともに蒸気流量調整弁20の開度を全開とし、系統40の周波数に依存させて蒸気タービン7を動作させることとした。すなわち、蒸気タービン7の回転数が系統40の周波数に支配されるように制御する。これにより、蒸気タービン7の回転数を調整する調速ガバナを設置する必要がなくなり、コストを低減することができる。
特に、ディーゼル機関5の排熱によって駆動する蒸気タービン7とされているので、ディーゼル機関5よりも蒸気タービン7の出力容量が小さい(例えば20%以下、典型的には10%程度)。したがって、調速ガバナによって蒸気タービン7の回転数を制御しなくてもディーゼル機関5によって駆動される主発電機11に影響を及ぼすことが殆どない。
また、ディーゼル機関5に対する蒸気タービン7の出力容量比について、例えば20%以下、典型的には10%程度としたが、本発明はこれに限定されるものではなく、ディーゼル機関5よりも蒸気タービン7の出力容量が小さければ本発明を適用することができ、好ましくは出力容量比50%未満であればよい。
5 ディーゼル機関
6 蒸気発生装置
7 蒸気タービン
10 排熱回収発電機
11 主発電機
20 蒸気流量調整弁
22 圧力制御弁
24 ダンプ弁
40 系統
Claims (4)
- ディーゼル機関と、
該ディーゼル機関から得た駆動力によって発電するとともに系統へと電力供給する主発電機と、
前記ディーゼル機関から排出された排ガスから排熱を回収して蒸気を生成する蒸気発生装置と、
該蒸気発生装置によって生成された蒸気によって駆動される蒸気タービンと、
該蒸気タービンから得た駆動力によって発電するとともに系統へと電力供給する誘導式とされた排熱回収発電機と、
該排熱回収発電機と前記系統との間の電力線に配置された排熱回収側遮断器と、
前記蒸気タービンの上流側の蒸気流路に設けられた蒸気流量調整弁と、
前記排熱回収側遮断器および前記蒸気流量調整弁を制御する制御部と、
を備えた発電プラント設備において、
前記制御部は、前記蒸気タービンの起動時に、前記蒸気流量調整弁を閉止状態から開度を増大させて前記蒸気タービンおよび前記排熱回収発電機の周波数を上昇させ、該排熱回収発電機の周波数が前記系統の周波数に達した後に、前記排熱回収側遮断器を接続して前記系統に給電するとともに前記蒸気流量調整弁の開度を略全開とし、前記系統の周波数に依存させて前記蒸気タービンを動作させる発電プラント設備。 - 前記蒸気流量調整弁の上流側には、圧力制御弁が設けられ、
前記制御部は、前記蒸気流路の圧力が所定値以下になった場合に前記圧力制御弁を閉とする請求項1に記載の発電プラント設備。 - 前記制御部は、前記蒸気流路の圧力が所定値以上になった場合に、前記蒸気タービンをバイパスして該蒸気タービンの下流側に設けられた復水器へと蒸気流れを切り替える請求項1又は2に記載の発電プラント設備。
- ディーゼル機関と、
該ディーゼル機関から得た駆動力によって発電するとともに系統へと電力供給する主発電機と、
前記ディーゼル機関から排出された排ガスから排熱を回収して蒸気を生成する蒸気発生装置と、
該蒸気発生装置によって生成された蒸気によって駆動される蒸気タービンと、
該蒸気タービンから得た駆動力によって発電するとともに系統へと電力供給する誘導式とされた排熱回収発電機と、
該排熱回収発電機と前記系統との間の電力線に配置された排熱回収側遮断器と、
前記蒸気タービンの上流側の蒸気流路に設けられた蒸気流量調整弁と、
前記排熱回収側遮断器および前記蒸気流量調整弁を制御する制御部と、
を備えた発電プラント設備の運転方法において、
前記制御部は、前記蒸気タービンの起動時に、前記蒸気流量調整弁を閉止状態から開度を増大させて前記蒸気タービンおよび前記排熱回収発電機の周波数を上昇させ、該排熱回収発電機の周波数が前記系統の周波数に達した後に、前記排熱回収側遮断器を接続して前記系統に給電するとともに前記蒸気流量調整弁の開度を略全開とし、前記系統の周波数に依存させて前記蒸気タービンを動作させる発電プラント設備の運転方法。
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2011
- 2011-08-02 CN CN201180016043.3A patent/CN102822451B/zh not_active Expired - Fee Related
- 2011-08-02 US US13/636,768 patent/US20130118168A1/en not_active Abandoned
- 2011-08-02 KR KR1020127024843A patent/KR101503129B1/ko active IP Right Grant
- 2011-08-02 EP EP11814629.9A patent/EP2602438A4/en not_active Withdrawn
- 2011-08-02 WO PCT/JP2011/067659 patent/WO2012018004A1/ja active Application Filing
Patent Citations (4)
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JPS57143110A (en) * | 1981-02-26 | 1982-09-04 | Mitsubishi Heavy Ind Ltd | Exhaust gas turbo-generation device |
JPS5838304A (ja) * | 1981-08-28 | 1983-03-05 | Hitachi Ltd | タ−ビン起動制御装置 |
JPS58200010A (ja) * | 1982-05-17 | 1983-11-21 | Toshiba Corp | 蒸気タ−ビンの制御装置 |
JP2004190558A (ja) | 2002-12-11 | 2004-07-08 | Babcock Hitachi Kk | 熱電併給プラント |
Non-Patent Citations (1)
Title |
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See also references of EP2602438A4 |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ITPR20120006A1 (it) * | 2012-02-17 | 2013-08-18 | Giovanni Sicurello | Dispositivo di generazione di potenza motrice |
CN102787870A (zh) * | 2012-08-25 | 2012-11-21 | 华北电力大学(保定) | 一种提高供热机组一次调频能力的方法 |
WO2014060760A3 (en) * | 2012-10-17 | 2015-06-11 | Norgren Limited | A waste heat recovery system comprising a bypass valve |
WO2014060761A3 (en) * | 2012-10-17 | 2015-06-18 | Norgren Limited | Vehicle waste heat recovery system |
EP2993316A1 (en) | 2012-10-17 | 2016-03-09 | Norgren Limited | Waste heat recovery system |
EP2993317A1 (en) * | 2012-10-17 | 2016-03-09 | Norgren Limited | Bypass valve |
US9964229B2 (en) | 2012-10-17 | 2018-05-08 | Norgren Limited | Bypass valve |
WO2015029724A1 (ja) * | 2013-08-29 | 2015-03-05 | ヤンマー株式会社 | 発電装置 |
JP2015048711A (ja) * | 2013-08-29 | 2015-03-16 | ヤンマー株式会社 | 発電装置 |
JP2015048712A (ja) * | 2013-08-29 | 2015-03-16 | ヤンマー株式会社 | 発電装置 |
Also Published As
Publication number | Publication date |
---|---|
KR101503129B1 (ko) | 2015-03-24 |
US20130118168A1 (en) | 2013-05-16 |
EP2602438A4 (en) | 2018-07-04 |
EP2602438A1 (en) | 2013-06-12 |
CN102822451B (zh) | 2015-08-05 |
CN102822451A (zh) | 2012-12-12 |
KR20120125383A (ko) | 2012-11-14 |
JP2012031822A (ja) | 2012-02-16 |
JP5496006B2 (ja) | 2014-05-21 |
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