CN104487661A - Internal combustion engine system, ship provided with same, and method for operating internal combustion engine system - Google Patents
Internal combustion engine system, ship provided with same, and method for operating internal combustion engine system Download PDFInfo
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- CN104487661A CN104487661A CN201380037384.8A CN201380037384A CN104487661A CN 104487661 A CN104487661 A CN 104487661A CN 201380037384 A CN201380037384 A CN 201380037384A CN 104487661 A CN104487661 A CN 104487661A
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- steam
- combustion engine
- water
- internal
- pressurized machine
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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
- 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
- F01D21/00—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for
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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
- F01K23/065—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
- 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
- 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
- F01N5/04—Exhaust or silencing apparatus combined or associated with devices profiting from exhaust energy the devices using kinetic energy
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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
- F02B37/12—Control of the pumps
- F02B37/22—Control of the pumps by varying cross-section of exhaust passages or air passages, e.g. by throttling turbine inlets or outlets or by varying effective number of guide conduits
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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
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B1/00—Methods of steam generation characterised by form of heating method
- F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
- F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
- F22B1/1807—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines
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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
- Y02E20/30—Technologies for a more efficient combustion or heat usage
-
- 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
Abstract
Provided is an internal combustion engine system that, when performing the actions of stopping and starting power generation in a supercharger for generating power, can avoid sudden fluctuations in the amount of steam produced by an exhaust gas boiler to stably operate a steam turbine and a steam turbine power generator. A water supply control valve (27) is controlled in an opening direction when the water level in a brackish water separator (12) falls below an allowable water level range and is controlled in a closing direction when the water level exceeds the allowable water level range. A steam inlet control valve (22) is controlled so as to supplement the amount of power generated by a steam turbine power generator (40) in accordance with variation in the amount of power generated by a power generator (3c) of a supercharger (3). The allowable water level range of the brackish water separator (12) is expanded when a supercharger power generation stop action is performed for stopping power generation by the power generator (3c) of the supercharger (3), and/or when a supercharger power generation start action is performed for starting the power generation by power generator (3c) of the supercharger (3).
Description
Technical field
The present invention relates to and a kind ofly such as possess the internal-combustion engine system of the internal-combustion engines such as marine diesel engine and possess the boats and ships of this internal-combustion engine system and the operation method of internal-combustion engine system.
Background technique
Such as be provided with for carrying high performance pressurized machine in the low speed 2 being used as marine engine circulates diesel engine (internal-combustion engine).As this pressurized machine, there will be a known the hybrid pressurized machine (with reference to following patent documentation 1) possessing generator and VTI (VariableTurbine Inlet) pressurized machine (with reference to following patent documentation 2) of turbine nozzle by area changing waste gas.
Conventional art document
Patent documentation
Patent documentation 1: Japan Patent No. 4648347 publication
Patent documentation 2: Japanese Patent Publication 2010-216468 publication
Summary of the invention
The technical task that invention will solve
Hybrid pressurized machine as Patent Document 1 can generate electricity when the load of the diesel engine as main frame becomes more than about 50% load.This is because when engine load becomes the low load of about less than 50%, do not improve the efficiency of pressurized machine, there is no the enough and to spare generated electricity.Therefore, hybrid pressurized machine for benchmark, stops generating when load declines with the engine load (such as 50% load) of regulation, starts generating when load is risen.
And, when reclaiming the exhaust gas economiser of heat to the diesel engine combination possessing hybrid pressurized machine and generated electricity by steam turbin generator by the steam driven steamturbine obtained in exhaust boiler from the waste gas of diesel engine, likely produce following problem.
That is, if the generating carrying out hybrid pressurized machine when the load of diesel engine declines stops action, then not only generated energy reduces, and also can decline from the temperature of the waste gas of diesel engine discharge.If generated energy reduces, then in order to make up the amount of minimizing, controlling the steam inlet control valve of steamturbine to opening direction, increasing to make the generated energy of steam turbin generator.Further, if exhaust gas temperature declines, being then arranged at the pressure drop in the steam-water separator of exhaust boiler, therefore controlling steam inlet control valve in order to obtain steam further to opening direction.If steam inlet control valve is opened, then the steam in steam-water separator be forced produce and make the water level decreasing in steam-water separator, in order to maintain allow in water level range to opening direction control water supply control valve, increase to make water supply.But, due to the new water that supplying temperature is lower, therefore cause the temperature in steam-water separator to decline and pressure in steam-water separator declines further.
So, if the generating carrying out hybrid pressurized machine stops action, then not only can produce the minimizing of generated energy, also can produce the decline of exhaust gas temperature, therefore the opening action of steam inlet control valve and the opening action of water supply control valve repeat, pressure in steam-water separator sharply declines, and the steam flow produced in exhaust boiler significantly reduces, thus is sometimes difficult to carry out stable steamturbine and the operation of steam turbin generator.Further, if the steam flow produced in exhaust boiler significantly reduces, then required steam cannot be provided, in the worst case, full-bodied astatki and lubricant oil cannot be made to warm, control viscosity cannot be carried out and control, thus likely also impact be brought on the stable operation of main frame.
Further, if the generating carrying out hybrid pressurized machine when the load of diesel engine is risen starts action, then not only generated energy increases, and also can rise from the temperature of the waste gas of diesel engine discharge.If generated energy increases, then in order to make up the amount of increase, controlling (reducing) steam inlet control valve to closing direction, reducing to make the generated energy of steam turbin generator.Further, if the temperature of waste gas rises, be then arranged at the pressure increase in the steam-water separator of exhaust boiler, therefore control steam inlet control valve to closing direction further.If control steam inlet control valve to closing direction, then the water level in steam-water separator rises, and allow in water level range and controls (reducing) water supply control valve to closing direction, water supply is reduced in order to maintain.But, fail the lower new water of suitably supplying temperature, therefore cause the temperature in steam-water separator to rise and pressure in steam-water separator rises further.
So, if the generating carrying out hybrid pressurized machine starts action, then not only produce the increase of generated energy, also can produce the rising of exhaust gas temperature, therefore the closing motion of steam inlet control valve and the closing motion of water supply control valve repeat, pressure in steam-water separator sharply rises, and the steam flow produced in exhaust boiler significantly increases, thus is likely difficult to carry out stable steamturbine and the operation of steam turbin generator.
As more than, when reclaiming the exhaust boiler of heat to the diesel engine combination possessing hybrid pressurized machine and generated electricity by steam turbin generator by the steam driven steamturbine obtained in exhaust boiler from the waste gas of diesel engine, when the generating of hybrid pressurized machine stops action or when generating starts action, the steam flow produced in exhaust boiler significantly changes, exist and be difficult to carry out stable steamturbine and the operation of steam turbin generator, and when generating electricity stopping action along with the minimizing producing steam flow, likely also be difficult to the problem of the stable operation of the diesel engine carried out as main frame.
On the other hand, the VTI pressurized machine as shown in patent documentation 2 just can only can carry out the operation that turbine nozzle is reduced by area when load on host computers is about less than 65%.This is because when load on host computers is about more than 65%, scavenging pressure becomes too high, exceed the permissible range of the cylinder roasting pressure of diesel engine.Therefore, even if only there is VTI pressurized machine, also can do nothing to help the fuel consumption cutting down diesel engine at whole load area.
Therefore, consider that this high load area of more than about 50% load by being combined in diesel engine is carried out the hybrid pressurized machine of generating action and VTI pressurized machine and in the whole load area of main frame, suppresses the fuel consumption in propulsion apparatus entirety.
At this, fuel consumption in propulsion apparatus entirety is cut down and is referred to that the exhaust energy effectively applied from diesel engine generates electricity, reduce the fuel consumption in generating engine thus, cut down the fuel consumption comprised in the propulsion apparatus entirety of main frame and generating engine.
But, the turbine nozzle area making turbine nozzle be reduced by area if carry out reduces action, then delivery temperature declines, the phenomenon stopping action identical with the generating of hybrid pressurized machine can be there is, namely the opening action of steam inlet control valve and the opening action of water supply control valve repeat, pressure in steam-water separator sharply declines, the phenomenon that the steam flow produced in exhaust boiler significantly reduces.And, the turbine nozzle area making turbine nozzle be increased by area if carry out increases action, then delivery temperature rises, can occur to start the identical phenomenon of action with the generating of hybrid pressurized machine, namely the closing motion of steam inlet control valve and the closing motion of water supply control valve repeat, pressure in steam-water separator sharply rises, the phenomenon that the steam flow produced in exhaust boiler significantly increases.So, when for also possessing pressurized machine by area changing mechanism of power facility and turbine nozzle, the stopping of Power Generation Section with pressurized machine and the unfavorable condition of beginning can be encouraged further.When to carry out turbocharger electrical generation and stop action and turbine nozzle area to reduce action simultaneously, or start when action and turbine nozzle area increase action especially remarkable when to carry out turbocharger electrical generation simultaneously.
Therefore, even if when to hybrid pressurized machine combination VTI pressurized machine, the steam flow produced in exhaust boiler also can be there is and significantly changes, be difficult to the problem of the operation carrying out stable steamturbine and steam turbin generator.
The present invention completes in light of this situation, when its object is to provide a kind of generating when implementing to carry out the pressurized machine generated electricity to stop action or generating to start action, sharply the changing of steam flow that produce in exhaust boiler can be avoided and internal-combustion engine system that steamturbine and steam turbin generator are stably run and possess the boats and ships of this internal-combustion engine system and the operation method of internal-combustion engine system.
And, the object of the present invention is to provide a kind of when carry out generating electricity and changes turbine nozzle by the pressurized machine of area carry out generating stop action or generate electricity beginning action, and carry out turbine nozzle area and reduce action or turbine nozzle area when increasing action, sharply the changing of steam flow that produce in exhaust boiler can be avoided and internal-combustion engine system that steamturbine and steam turbin generator are stably run and possess the boats and ships of this internal-combustion engine system and the operation method of internal-combustion engine system.
For the means of technical solution problem
In order to solve above-mentioned problem, the operation method of internal-combustion engine system of the present invention and the boats and ships and internal-combustion engine system that possess this internal-combustion engine system adopts following means.
That is, internal-combustion engine system of the present invention possesses: internal-combustion engine, pressurized machine, is had by the exhaust-driven turbine portion from this internal-combustion engine, to be driven and carry out the Power Generation Section that generates electricity to the press part of described internal-combustion engine pressurized delivered air and the rotating force that obtains described turbine portion by this turbine portion, exhaust boiler, reclaims heat, and possesses steam-water separator from the waste gas from described internal-combustion engine, water supply control valve, controls the water yield being supplied to described exhaust boiler, steamturbine, by the steam driven obtained in described exhaust boiler, steam inlet control valve, controls the steam flow guiding to steamturbine, and steam turbin generator, generated electricity by this steamturbine, when the water level in described steam-water separator is lower than when allowing water level range, described water supply control valve is controlled to opening direction, and, control to closing direction when allowing water level range higher than this, the mode making up the generated energy that described steam turbin generator produces with the increase and decrease of the generated energy produced according to the described Power Generation Section of described pressurized machine controls described steam inlet control valve, wherein, the turbocharger electrical generation of generating is stopped to stop action when carrying out making the described Power Generation Section of described pressurized machine, and/or, when the turbocharger electrical generation making the described Power Generation Section of described pressurized machine start to generate electricity starts action, expand described in described steam-water separator and allow water level range.
When carry out turbocharger electrical generation stop action time, expand steam-water separator allow water level range, even if the water level decreasing in steam-water separator also expand allow in water level range time, forbid opening water supply control valve and water output being increased.Thus, even if water level decreasing also can not make water output increase, therefore, it is possible to suppress the pressure in steam-water separator sharply to reduce, die-offing of the steam flow produced in exhaust boiler can be avoided to guarantee stable steamturbine and the operation of steam turbin generator.
Further, when carrying out turbocharger electrical generation and starting action, what expand steam-water separator allows water level range, though water level in steam-water separator rise also expand allow in water level range time, forbid reducing water supply control valve and water output being reduced.Thus, also water output can not be made to reduce even if water level rises, therefore, it is possible to the pressure in suppression steam-water separator sharply rises, sharply rising of the steam flow produced in exhaust boiler can be avoided to guarantee stable steamturbine and the operation of steam turbin generator.
In addition, steam-water separator allow water level range such as from time usual ± 50mm is extended to hundred tens of mm (such as ± 150mm).
Further, typically, the Power Generation Section of pressurized machine and the electric power management system (PMS of steamturbine by managing the generating action of other generators (such as diesel engine generator) or secondary cell; Power Management System) control generating action, to meet required electric power (in such as ship required electric power).
In addition, in internal-combustion engine system of the present invention, described pressurized machine possesses turbine nozzle by area changing mechanism, and described turbine nozzle changes by area changing mechanism the turbine nozzle being supplied to the described waste gas of described turbine portion and passes through area.
The turbine nozzle area making turbine nozzle be reduced by area if carry out reduces action, then delivery temperature declines and produces the phenomenon stopping action identical with turbocharger electrical generation.Further, the turbine nozzle area making turbine nozzle be increased by area if carry out increases action, then delivery temperature rises and produces and start the identical phenomenon of action with turbocharger electrical generation.So, when for possessing the pressurized machine of turbine nozzle by area changing mechanism, encourage the stopping of Power Generation Section with pressurized machine and the unfavorable condition of beginning further.When to carry out turbocharger electrical generation and stop action and turbine nozzle area to reduce action simultaneously, or carry out turbocharger electrical generation simultaneously and start when action and turbine nozzle area increase action especially remarkable.In the present invention, owing to using above-mentioned internal-combustion engine system, even therefore possess the pressurized machine of turbine nozzle by area changing mechanism, stable steamturbine and the operation of steam turbin generator also can be guaranteed.
Further, boats and ships of the present invention possess above-mentioned according to any one of internal-combustion engine system.
By possess above-mentioned any one of internal-combustion engine system, can provide a kind of and possess the boats and ships that can carry out the internal-combustion engine system of the stable operation of steamturbine and steam turbin generator.
Further, in the operation method of internal-combustion engine system of the present invention, described internal-combustion engine system possesses: internal-combustion engine; Pressurized machine, is had by the exhaust-driven turbine portion from this internal-combustion engine, to be driven and carry out the Power Generation Section that generates electricity to the press part of described internal-combustion engine pressurized delivered air and the rotating force that obtains described turbine portion by this turbine portion; Exhaust boiler, reclaims heat, and possesses steam-water separator from the waste gas from described internal-combustion engine; Water supply control valve, controls the water yield being supplied to described exhaust boiler; Steamturbine, by the steam driven obtained in described exhaust boiler; Steam inlet control valve, controls the steam flow guiding to steamturbine; And steam turbin generator, generated electricity by this steamturbine, described operation method has following operation: when the water level in described steam-water separator is lower than when allowing water level range, described water supply control valve is controlled to opening direction, further, control to closing direction when allowing water level range higher than this; The mode making up the generated energy that described steam turbin generator produces with the increase and decrease of the generated energy produced according to the described Power Generation Section of described pressurized machine controls described steam inlet control valve; And when carrying out making the described Power Generation Section of described pressurized machine to stop the turbocharger electrical generation of generating to stop action, and/or, when the turbocharger electrical generation making the described Power Generation Section of described pressurized machine start to generate electricity starts action, expand described in described steam-water separator and allow water level range.
Invention effect
Action or turbocharger electrical generation is stopped to start action when carrying out turbocharger electrical generation, and/or, when turbine nozzle reduces action by area increase action or turbine nozzle by area, what expand steam-water separator allows water level range, therefore by suppressing the sharply variation of the pressure in steam-water separator, the sharply variation of the steam flow produced in exhaust boiler can be avoided, stable steamturbine and the operation of steam turbin generator can be guaranteed.Further, when carrying out generating and stopping action, due to the sharply minimizing of the steam flow produced in exhaust boiler can be avoided, therefore, it is possible to guarantee the operation of stable internal-combustion engine.
Accompanying drawing explanation
Fig. 1 is the integrally-built summary construction diagram of the internal-combustion engine system represented involved by one embodiment of the present invention.
Fig. 2 is the longitudinal section of the pressurized machine representing Fig. 1.
The plotted curve of state when Fig. 3 is the switching representing the electricity generate function of pressurized machine and VTI function.
Fig. 4 is the chart of the action of each equipment of the internal-combustion engine system of summing up involved by the 1st mode of execution of the present invention.
Fig. 5 is the chart of the action of each equipment of the internal-combustion engine system of summing up involved by reference implementation mode of the present invention.
Embodiment
Below, with reference to accompanying drawing, mode of execution involved in the present invention is described.
[the 1st mode of execution]
Below, Fig. 1 to Fig. 3 is utilized to be described the 1st mode of execution of the present invention.
For the marine diesel engine system (internal-combustion engine system) 1 of boats and ships shown in Fig. 1.As shown in the drawing, marine diesel engine system 1 possess as such as low speed 2 circulate diesel engine main frame (internal-combustion engine) 2, to supply compressed-air actuated pressurized machine 3 and waste gas from always from host 2 to main frame 2 in reclaim the exhaust gas economiser (exhaust boiler) 4 of heat.
The crankshaft (not shown) forming main frame 2 is provided with propeller cavitation (not shown) directly or indirectly via screw shaft (not shown).Further, in main frame 2, be provided with the cylinder part 6 comprising cylinder sleeve (not shown), cylinder cowl (not shown) etc., in each cylinder part 6, be configured with the piston (not shown) linked with crankshaft.
The exhaust port (not shown) of each cylinder part 6 is connected with gas exhaust manifold 7.Gas exhaust manifold 7 is connected with the inlet side of the turbine portion 3a of pressurized machine 3 via outlet pipe L1.
Gas exhaust manifold 7 being provided with exhaust by-pass valve (exhaust bypass component) 11, by opening this exhaust by-pass valve 11, making the part from the waste gas of gas exhaust manifold 7 not be supplied to pressurized machine 3 and to exhaust gas economiser 4 side bypass.Exhaust by-pass valve 11 is controlled by not shown control device.
The air feed port (not shown) of each cylinder part 6 is connected with gas manifold (air trapping portion) 8, and gas manifold 8 is connected with the press part 3b of pressurized machine 3 via air supply pipe L2.Air supply pipe L2 is provided with main frame feed-water heater 17 and air-cooler 13, thus carries out heat exchange with the air compressed by press part 3b.Main frame feed-water heater 17 is arranged at the pressurized air stream upstream side of air-cooler 13, and the water supply guided from raw water service pump 18 described later is heated by pressurized air.The water supply of being heated by main frame feed-water heater 17 is delivered to the steam-water separator 12 of donkey boiler 14 and is arranged at the low pressure vapor separator 21 of steam vapour system 19.Air-cooler 13 utilizes not shown cooling water to cool the pressurized air declined by main frame feed-water heater 17 temperature further.
Gas manifold 8 being provided with scavenging bypass valve (scavenging bleed component) 9, by opening this scavenging bypass valve 9, the air in gas manifold 8 can being discharged.Scavenging bypass valve 9 is controlled by not shown control device.
As shown in Figures 1 and 2, pressurized machine 3 is formed primarily of following important document: turbine portion 3a, is driven by the waste gas (combustion gas) guided from main frame 2 via outlet pipe L1; And press part 3b, by this turbine portion 3a driving and to main frame 2 pressurized delivered extraneous gas (air).
Pressurized machine 3 possesses the generator 3c that the rotating force obtaining turbine portion 3a carries out generating electricity.By controlling generator 3c from the control signal of the PMS (power-supply management system) 28 being arranged at MSB (main distribution board) 26.That is, between PMS28 and the inverter 30 of generator 3c, carry out the exchange of control signal.Between inverter 30 and generator 3c, be provided with transducer 32, thus carry out the exchange of control signal between inverter 30.The alternating electromotive force generated electricity by generator 3c is converted to desired frequency by inverter 30 is orthogonal, is delivered to lash ship 33 in ship via contactor 35 after being undertaken handing over straight conversion by transducer 32.
PMS28 controls generation power according to required electric power in ship, also carries out the control being such as set to the generating diesel motor 37 of 4 strokes driving diesel engine generator DG.The generation electric power of diesel engine generator DG exports lash ship 33 in ship to.In addition, 3 groups of generatings diesel motor 37 and diesel engine generator DG shown in Fig. 1, but also can be 1 group or 2 groups, or more than 4 groups.In addition, PMS28 also can carry out the control of the secondary cells such as lithium secondary battery.
Pressurized machine 3 is provided with and changes the turbine nozzle that is supplied to the waste gas of turbine portion 3a from the outlet pipe L1 turbine nozzle by area by area changing mechanism 3g.Specifically, turbine nozzle is possessed by area changing mechanism 3g and turbine nozzle is divided into the dividing plate 3f of inner circumferential side and outer circumferential side (with reference to figure 2), by the branch pipe arrangement 3d of a part of branch of the waste gas guided from outlet pipe L1 and the open and close valve 3e of opening and closing carrying out this branch pipe arrangement 3d.As shown in Figure 2, the waste gas flowing through branch pipe arrangement 3d flows through the inner circumferential side of the dividing plate 3f of turbine nozzle.In addition, open and close valve 3e is controlled by not shown control device.
If close open and close valve 3e, then waste gas does not flow through branch pipe arrangement 3d and flows only through the outer circumferential side of the dividing plate 3f of turbine nozzle, by area, VTI function is set to ON by reducing turbine nozzle.On the other hand, if open open and close valve 3e, then the undue Zhi Peiguan 3d of waste gas streams, also flows through the inner circumferential side of the dividing plate 3f of turbine nozzle, and turbine nozzle is by enlarged areas, thus VTI function becomes OFF.
As shown in Figure 1, exhaust gas economiser 4 has high pressure heat exchanger 10a, middle pressure heat exchanger 10b and low pressure heat exchanger 10c successively from the upstream side of waste gas streams in its flue.Each heat exchanger 10a, 10b, 10c possess multiple heat conductive tube, heat by the high-temp waste gas flow through in the flue of exhaust gas economiser 4 water flow through in heat conductive tube.
The steam be separated by the steam-water separator 12 of donkey boiler 14 is guided in high pressure heat exchanger 10a.Heated by high pressure heat exchanger 10a and the superheated vapor of degree of superheat rising guides to steamturbine 23 via steam inlet control valve 22.In addition, a part for the steam be separated by steam-water separator 12 guides to supplementary equipment 20 in ship.The predominant use of the steam in ship in supplementary equipment 20 is the heating of astatki and the lubricant oil used for the fuel as main frame 2.
A part for the superheated vapor heated by high pressure heat exchanger 10a guides to supplementary equipment 20 in each ship via high pressure steam bypass valve 29.Be dispensing by control each flow rate regulating valve 31a, 31b of being supplied to the steam of supplementary equipment 20 in each ship carry out.Do not guide to the remaining steam of supplementary equipment 20 in each ship and guide to capacitor 34.
The water be separated by the steam-water separator 12 of donkey boiler 14 guides to middle pressure heat exchanger 10b via conveying pump 25a.Heated by middle pressure heat exchanger 10b and the steam of evaporation guides to steam-water separator 12.
Water and steam is accommodated respectively in the mode be separated up and down in steam-water separator 12.As mentioned above, the water heated by main frame feed-water heater 17 is supplied in steam-water separator 12.The water output being supplied to steam-water separator 12 is controlled by water supply control valve 27.Water supply control valve 27 controls its aperture by not shown control device, allows in water level range to make the water level in steam-water separator 12 maintain.Water level in steam-water separator 12 is measured by not shown water-level gauge, and its measured value is sent to not shown control device.
Be provided with safety valve 24 on the top of steam-water separator 12, if the pressure in steam-water separator 12 becomes more than specified value, then safety valve is opened, and makes inner discharge of steam to outside.
Low pressure heat exchanger 10c is arranged in steam vapour system 19, makes it evaporate to heating from the water that low pressure vapor separator 21 guides via conveying pump 25b.The steam Transportation evaporated by low pressure heat exchanger 10c is to low pressure vapor separator 21.The steam be separated by low pressure vapor separator 21 guides to the intermediate section of steamturbine 23, and remainder guides to supplementary equipment 20 in ship.
Steam after using in supplementary equipment 20 in each ship guides to condensing cooler 15, is accumulated in condensing storage unit 16 by the condensing water of condensing cooler (drain cooler) 15 condensations.Condensed water from ground capacitor 36 described later also guides in condensing storage unit 16.The condensing water accumulated in condensing storage unit 16 guides to above-mentioned main frame feed-water heater 17 by raw water service pump 18.
Steamturbine 23 is connected with steam turbin generator 40 via speed reducer 38.The generating of steam turbin generator 40 exports and guides to lash ship 33 in ship via not shown line of electric force.
The high pressure steam flow of steamturbine 23 is supplied to by steam inlet control valve 22 adjustment.According to the aperture of the SC sigmal control steam inlet control valve 22 of the speed regulator 44 of the instruction from reception turbine control panel 43.Turbine control panel 43 is controlled by PMS28.Therefore, the aperture of steam inlet control valve 22 is controlled to steam turbin generator 40 and exports the generated energy determined by PMS28.
The steam of being finished the work by steamturbine 23 guides to the rear condensation of capacitor 34, and this condensed water (water of condensation) guides to ground capacitor 36 by condensate pump 42.
The internal-combustion engine system of said structure carries out action as follows.Below, be divided into " when usually running ", " load on host computers rise time switching time ", " load on host computers reduce time switching time " be described.At this, refer to the state beyond the moment that Electricity Functional and VTI function are changed in the state incision being undertaken generating electricity by pressurized machine 3 during usual operation, refer to and the pressure in steam-water separator 12 can not be made sharply to change and the state of the continuous service of steamturbine 23 can be carried out.
[when usually running]
Heat after the condensing water accumulated in condensing storage unit 16 guides to main frame feed-water heater 17 by raw water service pump 18, and guide to the steam-water separator 12 of donkey boiler 14 and the low pressure vapor separator 21 of steam vapour system 19.
Become steam after the water guiding to steam-water separator 12 guides to middle pressure heat exchanger 10b by conveying pump 25a, be back to steam-water separator 12.The steam be separated by steam-water separator 12 becomes the superheated vapor of high temperature after guiding to high pressure heat exchanger 10a.The superheated vapor generated by high pressure heat exchanger 10a guides to steamturbine 23 after adjusting flow by steam inlet control valve 22.
On the other hand, become steam after the water guiding to low pressure vapor separator 21 guides to low pressure heat exchanger 10c by conveying pump 25b, be back to low pressure vapor separator 21.The low pressure steam be separated by low pressure vapor separator 21 guides to the intermediate section of steamturbine 23.
Exported by the rotation of directed steam-powered steamturbine 23 and be passed to steam turbin generator 40 via speed reducer 38, generate electricity.The generated energy that this steam turbin generator 40 produces is managed by PMS28.PMS28 obtains generated energy, the generated energy of other generators (diesel engine generator DG), the charging and discharging state of secondary cell BT of the generator 3c of pressurized machine 3 online, send power generation command to each equipment, meet required electric power in ship to make the total of the electric power supplied from these generators and secondary cell.About the generated energy of steam turbin generator 40, send instruction to turbine control panel 43, control the aperture of steam inlet control valve 22 via speed regulator 44.Specifically, the mode making up with the increase and decrease of the generated energy produced according to the generator 3c of pressurized machine 3 generated energy that steam turbin generator 40 produces controls steam inlet control valve 22.Namely, when the generated energy of the generator 3c of pressurized machine 3 reduces, the aperture of steam inlet control valve 22 is controlled to opening direction, the generated energy produced to make steam turbin generator 40 increases, when the generated energy of the generator 3c of pressurized machine 3 increases, control the aperture of steam inlet control valve 22 to closing direction, the generated energy produced to make steam turbin generator 40 reduces.
The generated energy of the generator 3c of pressurized machine 3 increases and decreases according to the load of main frame 2, as shown in the plotted curve of " the hybrid turbocharger electrical generation electric power " of Fig. 3, when load on host computers is more than 65%, load on host computers rise then generated energy increase, load on host computers reduce then generated energy reduce.
The water level in the steam-water separator 12 of donkey boiler 14 is adjusted by water supply control valve 27.During usual operation, if the water level in steam-water separator 12 declines from desired value, then control to opening direction, if higher than desired value, then control to closing direction.That is, when usually running, will allow water level range (tolerance) be set to ± 50mm to be to carry out water lev el control.This allows that water level range sets according to equipment, and when usually running, target carries out the stable operation of steamturbine and steam turbin generator, therefore preferably reduces as far as possible and allows water level range.
[load on host computers rise time switching time]
Then, when rising to load on host computers, the switching electricity generate function of pressurized machine and the situation of VTI function are described.
As shown in Figure 3, when load on host computers rises (during speedup), about electricity generate function, under the load (being 65% in Fig. 3) of regulation, switch to generating action from non-power generating action.This can learn from following situation: the solid line of the plotted curve of " the hybrid turbocharger electrical generation electric power " of Fig. 3 rises in load 65%.On the other hand, about VTI function, under the load (being 65% in Fig. 3) of regulation, switch to OFF from ON.This can learn from following situation: decline from pressure higher than single dotted broken line of the fine line of the plotted curve of " the main frame scavenging pressure " of Fig. 3 in load 65%.And the plotted curve as " main frame exhaust gas temperature " from this figure can be learnt, exhaust gas temperature sharply rises.
So, if switch to generating action when load on host computers rises from non-power generating action and VTI function is switched to OFF from ON, then not only the generated energy of the generator 3c of pressurized machine 3 increases, and also rises from the temperature of the waste gas of main frame 2 discharge.If the generated energy of the generator 3c of pressurized machine 3 increases, then control (reducing) steam inlet control valve 22 to closing direction, with the increasing amount making the generated energy of steam turbin generator 40 reduce the generated energy of the generator 3c of pressurized machine 3.Further, if the temperature of waste gas rises, then by the pressure increase in steam-water separator 12, the vapor pressure being supplied to steamturbine rises further, therefore controls steam inlet control valve 22 to closing direction further.If control steam inlet control valve 22 to closing direction, then the water level in steam-water separator 12 rises, and in order to allowing in water level range of using when maintaining and usually run controls (reducing) water supply control valve 27 to closing direction, water supply is reduced.But, due to can not new water that suitably supplying temperature is lower, therefore cause the temperature in steam-water separator 12 to rise and pressure in steam-water separator 12 rises further.
So, if the generating carrying out pressurized machine 3 starts action, then not only produce the increase of the generated energy of the generator 3c of pressurized machine 3, also can produce the rising of exhaust gas temperature, therefore the closing motion of steam inlet control valve 22 and the closing motion of water supply control valve 27 repeat, pressure in steam-water separator 12 sharply rises, and the steam flow produced in exhaust gas economiser 4 significantly increases, thus is likely difficult to carry out stable steamturbine and the operation of steam turbin generator.
Therefore, in present embodiment, when the generating carrying out pressurized machine 3 starts action, allowing steam-water separator 12 that water level range is set to and expand tolerance (being below+150mm in present embodiment) than (in present embodiment for ± 50mm) when usually running, even if water level in steam-water separator 12 rise also than expand when usually running allow in water level range time, forbid reducing water supply control valve 27 and water output being reduced.Thus, when even if water table ratio is run usually allow water level range rise water output also can not be made to reduce, therefore, it is possible to suppress the pressure in steam-water separator 12 sharply to rise, sharply increasing of the steam flow produced in exhaust gas economiser 4 can be avoided to guarantee stable steamturbine and the operation of steam turbin generator.
[load on host computers reduce time switching time]
When load on host computers reduces (during deceleration), when rising with above-mentioned load on host computers on the contrary, about electricity generate function, under the load (being 65% in Fig. 3) of regulation, switch to non-power generating action from generating action.On the other hand, about VTI function, under the load (being 65% in Fig. 3) of regulation, switch to ON from OFF.Now, as learnt from the plotted curve of " the main frame scavenging pressure " of Fig. 3, scavenging pressure sharply rises.And as learnt from " the main frame exhaust gas temperature " of Fig. 3, exhaust gas temperature sharply declines.
So, if switch to non-power generating action when load on host computers reduces from generating action and VTI function is switched to ON from OFF, then not only the generator 3c of pressurized machine 3 stops generating, also can decline from the temperature of the waste gas of diesel engine discharge.If the generator 3c of pressurized machine 3 stops generating, then in order to make up this generating, controlling the steam inlet control valve 22 of steamturbine 23 to opening direction, increasing to make the generated energy of steam turbin generator 40.Further, if exhaust gas temperature declines, then by the pressure drop in steam-water separator 12, the vapor pressure being supplied to steamturbine declines further, therefore controls steam inlet control valve 22 in order to obtain steam further to opening direction.If open steam inlet control valve 22, then force to produce the steam in steam-water separator 12 and the water level decreasing in steam-water separator 12, allow in water level range and control water supply control valve 27 in order to maintain to opening direction, thus water supply is increased.But, due to the new water that supplying temperature is lower, therefore cause the temperature in steam-water separator 12 to decline and pressure in steam-water separator 12 declines further.
So, if the generating carrying out pressurized machine 3 stops action, then not only produce generating to stop, also can produce the decline of exhaust gas temperature, therefore the opening action of steam inlet control valve 22 and the opening action of water supply control valve 27 repeat, pressure in steam-water separator 12 sharply declines, and the steam flow produced in exhaust gas economiser 4 significantly reduces, thus is likely difficult to carry out stable steamturbine and the operation of steam turbin generator.Further, if the steam flow produced in exhaust gas economiser 4 reduces, then required steam cannot be provided, in the worst case, full-bodied astatki and lubricant oil cannot be made to warm, cannot viscosity control be carried out, thus likely also be difficult to the stable operation carrying out main frame 2.
Therefore, in present embodiment, when the generating carrying out pressurized machine 3 stops action, allowing steam-water separator 12 that water level range is set to and expand tolerance (being more than-150mm in present embodiment) than (in present embodiment for ± 50mm) when usually running, even if the water level decreasing in steam-water separator 12 also than expand when usually running allow in water level range time, forbid opening water supply control valve 27 and water output being increased.Thus, when even if water table ratio is run usually allow water level range decline water output also can not be made to increase, therefore, it is possible to suppress the pressure in steam-water separator 12 sharply to reduce, the die-offing of steam flow produced in exhaust gas economiser 4 can be avoided to guarantee stable steamturbine and steam turbin generator, and then guarantee the operation of main frame 2.
The action of each equipment when summing up above-mentioned usual operation in the diagram and when switching.
As shown in the drawing, steam-water separator 12 allow that water level range is set to ± 50mm when usually running, but change into ± 150mm when switching.
In addition, steam-water separator 12 allow that the switching instant of water level range carries out when switching the electricity generate function of pressurized machine 3 and VTI function, it can be obtained by various method.Such as, in the inlet temperature of the time rate of change of the pressure in steam-water separator 12, the time rate of change of water level and exhaust gas economiser 4 or the time rate of change of outlet temperature or mean temperature, the combination of wherein any one or they can be utilized, predict that the increase and decrease of steam generating amount judges by control device.And, the switching of the electricity generate function of pressurized machine 3 can be exported by the control obtaining inverter 30 and judge, the switching of VTI function can be judged by the action of the open and close valve 3e (with reference to figure 2) detecting pressurized machine 3, therefore can judge based on these switching instant.Further, when being fixed on the load on host computers of regulation in advance, can by grasping by control device the switching instant that load on host computers increment rate predicts electricity generate function and VTI function like a cork.
As when expand allow water level range after return to when usually running allow water level range when, as mentioned above, in the inlet temperature of the time rate of change of the pressure such as in steam-water separator 12, the time rate of change of water level and exhaust gas economiser 4 or the time rate of change of outlet temperature or mean temperature, the combination of wherein any one or they can be utilized, predict that the increase and decrease of steam generating amount judges by control device.
Further, established amount can be changed according to load on host computers from the load on host computers (65%) when switching and be set to the recovery moment.Or, also can recover the moment by from being set to after the stipulated time during switching, below specified value can also be become be set to according to the time variation amount of the water level measured by water-level gauge and recover the moment.
Further, in above-mentioned each mode of execution, possess premised on electricity generate function and VTI function by pressurized machine 3 and be illustrated, but when for do not possess VTI function only possess the so-called hybrid pressurized machine of electricity generate function time, also can be suitable for the present invention.This is because, even if exhaust gas temperature sharply changes and does not possess VTI function to the phenomenon that the power generation command value of steam turbin generator 40 sharply changes and also can occur when switching electricity generate function.
[reference implementation mode]
Then, reference implementation mode is described.Basic structure is identical with the 1st mode of execution using Fig. 1 to Fig. 3 to illustrate, therefore the description thereof will be omitted.In 1st mode of execution, allow that water level range avoids the pressure oscillation sharply in steam-water separator 12 when switching the electricity generate function of pressurized machine 3 and VTI function by what change steam-water separator 12, but in the present embodiment, do not change and allow water level range but use secondary cell BT, this point is different.
Therefore, when PMS28 manages secondary cell, present embodiment can be suitable for.
Identical with the 1st mode of execution during usual operation, therefore the description thereof will be omitted.
When the generating carrying out pressurized machine 3 when load on host computers rises starts action, never illustrated control device sends the charging requirement instruction of secondary cell to PMS28.PMS28 sends charging instruction when receiving charging requirement instruction to secondary cell.Secondary cell charges to absorb the increase of the generated energy of the generator 3c of pressurized machine 3.Thus, PMS28 can make the total electric power from each generator consistent with required electric power in ship.
Thus, the increase of the generated energy of the generator 3c in order to absorb pressurized machine 3 can be avoided and reduce steam inlet control valve 22, therefore, it is possible to suppress the pressure in steam-water separator 12 sharply to rise, sharply rising of the steam flow produced in exhaust gas economiser 4 can be avoided to guarantee stable steamturbine and the operation of steam turbin generator.
Further, when the generating carrying out pressurized machine 3 when load on host computers reduces stops action, the electric discharge that never illustrated control device sends secondary cell to PMS28 requires instruction.PMS28 sends electric discharge instruction when receiving when electric discharge requires instruction to secondary cell.The slippage of the generated energy that secondary cell produces in order to the generator 3c making up pressurized machine 3 and discharging.Thus, PMS28 can make the total electric power from each generator consistent with required electric power in ship.
Thus, the slippage of generated energy in the ship in order to make up with the generating stopping of the generator 3c of pressurized machine 3 can be avoided and open steam inlet control valve 22, therefore, it is possible to suppress the pressure in steam-water separator 12 sharply to reduce, the die-offing of steam flow produced in exhaust gas economiser 4 can be avoided to guarantee stable steamturbine and the operation of steam turbin generator.
The action of each equipment when summing up above-mentioned usual operation in Figure 5 and when switching.
As shown in the drawing, when usually running, do not require that PMS28 carries out the action to secondary cell, and require charge or discharge when switching.
Further, in above-mentioned each mode of execution, possess premised on electricity generate function and VTI function by pressurized machine 3 and be illustrated, but when being also suitable for the present invention for not possessing when VTI function only possesses the so-called hybrid pressurized machine of electricity generate function.This is because, even if exhaust gas temperature sharply changes and does not possess VTI function to the phenomenon that the power generation command value of steam turbin generator 40 sharply changes and also can occur when switching electricity generate function.
Symbol description
1-marine diesel engine system (internal-combustion engine system), 2-main frame (internal-combustion engine), 3-pressurized machine, 3a-turbine portion, 3b-press part, 3c-generator, 3d-branched pipe (turbine nozzle is by area changing mechanism), 3e-open and close valve (turbine nozzle is by area changing mechanism), 3f-dividing plate (turbine nozzle is by area changing mechanism), 4-exhaust gas economiser (exhaust boiler), 12-steam-water separator, 22-steam inlet control valve, 23-steamturbine, 28-PMS (electric power management system), 40-steam turbin generator.
Claims (4)
1. an internal-combustion engine system, it possesses:
Internal-combustion engine;
Pressurized machine, is had by the exhaust-driven turbine portion from this internal-combustion engine, to be driven and carry out the Power Generation Section that generates electricity to the press part of described internal-combustion engine pressurized delivered air and the rotating force that obtains described turbine portion by this turbine portion;
Exhaust boiler, reclaims heat, and possesses steam-water separator from the waste gas from described internal-combustion engine;
Water supply control valve, with the water level in described steam-water separator lower than the mode controlled to closing direction when controlling to opening direction when allowing water level range and allow water level range higher than this, controls the water yield being supplied to described exhaust boiler;
Steamturbine, by the steam driven obtained in described exhaust boiler;
Steam inlet control valve, makes up the mode of the generated energy that described steam turbin generator produces with the increase and decrease of the generated energy produced according to the described Power Generation Section of described pressurized machine, control the steam flow guiding to steamturbine; And
Steam turbin generator, is generated electricity by this steamturbine,
Wherein, the turbocharger electrical generation of generating is stopped to stop action when carrying out making the described Power Generation Section of described pressurized machine, and/or, when the turbocharger electrical generation making the described Power Generation Section of described pressurized machine start to generate electricity starts action, expand described in described steam-water separator and allow water level range.
2. internal-combustion engine system according to claim 1, wherein,
Described pressurized machine possesses turbine nozzle by area changing mechanism, and described turbine nozzle changes by area changing mechanism the turbine nozzle being supplied to the described waste gas of described turbine portion and passes through area.
3. boats and ships, it possesses the internal-combustion engine system described in claim 1 or 2.
4. an operation method for internal-combustion engine system, it possesses following operation:
Drive internal-combustion engine;
By the exhaust gas-driven turbine portion from internal-combustion engine, and drive press part by the driving of this turbine portion, thus to described internal-combustion engine pressurized delivered air;
Obtain the rotating force of described turbine portion and generated electricity by pressurized machine;
Supply water to the exhaust boiler possessing steam-water separator, and carry out heat exchange with the waste gas from described internal-combustion engine, produce steam thus;
The steam driven steamturbine produced by described heat exchange is generated electricity,
The operation method of described internal-combustion engine system possesses following operation:
When the water level in described steam-water separator is lower than water supply start when allowing water level range, and, stop supplying water when allowing water level range higher than this;
According to the increase and decrease of the generated energy that described pressurized machine produces, control the generated energy that described steamturbine produces; And
When carrying out making described pressurized machine stop the turbocharger electrical generation of generating to stop action, and/or, when the turbocharger electrical generation making described pressurized machine start to generate electricity starts action, expand described in described steam-water separator and allow water level range.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012237053A JP5976498B2 (en) | 2012-10-26 | 2012-10-26 | INTERNAL COMBUSTION ENGINE SYSTEM, SHIP HAVING THE SAME, AND METHOD FOR OPERATING INTERNAL COMBUSTION ENGINE SYSTEM |
| JP2012-237053 | 2012-10-26 | ||
| PCT/JP2013/078944 WO2014065397A1 (en) | 2012-10-26 | 2013-10-25 | Internal combustion engine system, ship provided with same, and method for operating internal combustion engine system |
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| CN104487661A true CN104487661A (en) | 2015-04-01 |
| CN104487661B CN104487661B (en) | 2016-06-08 |
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| CN201380037384.8A Active CN104487661B (en) | 2012-10-26 | 2013-10-25 | Internal-combustion engine system and possess the boats and ships of this internal-combustion engine system and the operation method of internal-combustion engine system |
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| Country | Link |
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| JP (1) | JP5976498B2 (en) |
| KR (1) | KR101660655B1 (en) |
| CN (1) | CN104487661B (en) |
| WO (1) | WO2014065397A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN108699976A (en) * | 2016-02-29 | 2018-10-23 | 三菱重工业株式会社 | The control device and internal combustion engine of internal combustion engine |
| CN108779687A (en) * | 2016-03-31 | 2018-11-09 | 三菱重工业株式会社 | The control method of waste heat recovery plant, internal-combustion engine system and ship and waste heat recovery plant |
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| JP6498433B2 (en) * | 2014-12-19 | 2019-04-10 | 三菱重工業株式会社 | Exhaust heat recovery system, ship equipped with the same, and exhaust heat recovery method |
| JP6389794B2 (en) * | 2015-04-09 | 2018-09-12 | 株式会社神戸製鋼所 | Thermal energy recovery device |
| RU2635425C1 (en) * | 2017-02-09 | 2017-11-13 | Никишин ГмбХ | Device to control turbocharged internal combustion engine |
| EP3594569A1 (en) * | 2018-07-12 | 2020-01-15 | Repsol, S.A. | Heat recovery device |
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- 2013-10-25 KR KR1020157000777A patent/KR101660655B1/en active IP Right Grant
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Also Published As
| Publication number | Publication date |
|---|---|
| JP5976498B2 (en) | 2016-08-23 |
| WO2014065397A1 (en) | 2014-05-01 |
| JP2014084853A (en) | 2014-05-12 |
| KR101660655B1 (en) | 2016-09-27 |
| KR20150027796A (en) | 2015-03-12 |
| CN104487661B (en) | 2016-06-08 |
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