CN101581249A - Large-size two-stroke diesel motor with a plurality of variable turbochargers - Google Patents
Large-size two-stroke diesel motor with a plurality of variable turbochargers Download PDFInfo
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- CN101581249A CN101581249A CNA200810125295XA CN200810125295A CN101581249A CN 101581249 A CN101581249 A CN 101581249A CN A200810125295X A CNA200810125295X A CN A200810125295XA CN 200810125295 A CN200810125295 A CN 200810125295A CN 101581249 A CN101581249 A CN 101581249A
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- speed
- variable turbochargers
- controller
- turbosupercharger
- turbochargers
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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
- F02B37/24—Control of the pumps by using pumps or turbines with adjustable guide vanes
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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
- 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
- F02B37/001—Engines characterised by provision of pumps driven at least for part of the time by exhaust using exhaust drives arranged in parallel
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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
- F02B37/007—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust-driven pumps arranged in parallel, e.g. at least one pump supplying alternatively
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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
- F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
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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
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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
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/16—Other safety measures for, or other control of, pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D23/00—Controlling engines characterised by their being supercharged
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/0002—Controlling intake air
- F02D41/0007—Controlling intake air for control of turbo-charged or super-charged engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/14—Introducing closed-loop corrections
- F02D41/1401—Introducing closed-loop corrections characterised by the control or regulation method
- F02D2041/1413—Controller structures or design
- F02D2041/1418—Several control loops, either as alternatives or simultaneous
- F02D2041/1419—Several control loops, either as alternatives or simultaneous the control loops being cascaded, i.e. being placed in series or nested
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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
- 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
A large-size two-stroke diesel motor with a plurality of variable turbochargers comprises the following components: a plurality of cylinders which are set in row; a plurality of turbochargers which have variable nozzle areas and are connected in parallel between an exhaust box and a scavenging box of the motor; and a controller which is coupled to the variable turbochargers and comprises an external pressure loop and an inner speed loop. The external pressure loop comprises a pressure controller, and the inner speed loop comprises a speed controller. The pressure controller is configured to determine a total nozzle area which is obtained by adding the areas of all turbochargers, and the speed controller is configured to control the speed of each turbocharger separately.
Description
Technical field
The present invention relates to a kind of large scale multi-cylinder two-stroke diesel engine that is provided with a plurality of variable turbochargers, and relate to the control of a plurality of variable turbochargers particularly.
Background technique
Because the two-stroke diesel engine enormous size is so large-scale two-stroke diesel engine has been provided with a plurality of turbosupercharger.Large-scale two-stroke diesel engine is the megamachine that has 5-14 single-row cylinder arrangement usually.Scavenging air box extends along the whole length of motor, and can be also longer than 30m.
Theoretically, these motors can be provided with single huge turbosupercharger.But therefore the turbosupercharger of a this size of structure is very difficult technically is very expensive.Thereby these large-scale two-stroke diesel engines are provided with two, three, four or more a plurality of turbosupercharger usually.These turbosupercharger distribute equably along the length of motor.
These known motors are provided with traditional turbosupercharger, and promptly these turbosupercharger are not variable types.The advantage of variable turbochargers is that they can provide high scavenging pressure when partial load, and can not provide high pressure when high capacity.The speed of turbosupercharger is reduced when high capacity relatively.This feature class is similar to exhaust gas bypass, but has higher efficient.The result is that compressor side will more be moved near surge line, thereby must very accurately control to avoid surge and stall.The suitable control system that is used for single variable turbochargers is known, but these known control system are not suitable for the variable turbochargers of a plurality of parallel connections, more are not suitable for when motor is large-scale two-stroke diesel engine.
Summary of the invention
The purpose of this invention is to provide a kind of large-scale two-stroke diesel engine with a plurality of variable turbochargers.
Variable turbochargers can be under the feasible operating conditions of motor high-efficiency operation.The optimal setting of variable turbochargers approaches surge limit (surge line) usually, and turbosupercharger must accurately be controlled to avoid stall when moving near surge limit.
The present inventor has recognized the existing control system that is used on the mini engine that has only a variable turbochargers because following former thereby can not work to a plurality of variable turbochargers on large-scale two-stroke diesel engine.One of them reason is that a plurality of variable turbochargers can influence each other, thereby the setting value that changes a variable turbochargers will have influence for the operation of other variable turbochargers.And the inventor recognizes that the operating conditions of each variable turbochargers depends on its position along motor.This position along motor can have considerable influence to the operation of single variable turbochargers, because have very big pressure surge in scavenging air box.In large-scale two-stroke diesel engine, this fluctuation has influence even as big as the operation for turbosupercharger: pressure surge causes the speed of related turbine pressurized machine to fluctuate.Usually, the low frequency pressure surge is the worst near scavenging air box extreme the time.The inventor recognizes that also the operation situation of each turbosupercharger in a plurality of turbosupercharger is all different each other, because only have one or two to be overhauled simultaneously in common a plurality of turbosupercharger.Thereby some in a plurality of turbosupercharger will overhauled in the recent period, and in a plurality of turbosupercharger some other will move under inferior good speed market shape, thereby produce the needs of the control system of considering these differences.
The inventor also recognizes for variable turbochargers to have bigger mechanical tolerance than traditional turbosupercharger.Thereby the turbosupercharger that the diversity ratio in the turbosupercharger of a plurality of variable types between each turbosupercharger is traditional is bigger.
This purpose realizes that by a kind of large-scale two-stroke diesel engine is provided it has: a plurality of cylinders that are provided with in upright arrangement; A plurality of nozzle area variable turbochargers, described variable turbochargers are parallel between the waste heat box and scavenging air box of motor; Be coupled to the controller of described variable turbochargers, described controller comprises external pressure loop and internal speed loop, the external pressure loop comprises pressure controller, the internal speed loop comprises speed controller, described pressure controller is configured to determine all turbosupercharger total nozzle area altogether of expectation, and described speed controller is configured to control separately the speed of each turbosupercharger.
By the external control loop of guaranteeing to have in the scavenging air box correct pressure is provided, thereby make that the internal speed control loop be used for each variable turbochargers is stable, and obtain to be parallel to the flexible control system of a plurality of variable turbochargers on the scavenging air box of large-scale two-stroke diesel engine.
Preferably, speed controller is arranged such that in each variable turbochargers each and all obtains about equally speed.
Speed controller can be configured to compensate the influence of the setting value change of one of them variable turbochargers to other variable turbochargers.
Speed controller can be configured to compensate the speed difference that the Different Effects by the low frequency pressure wave in the scavenging air box causes, and the Different Effects of described low frequency pressure wave is caused by the difference of each turbosupercharger position.
Speed controller can be configured to compensate the maintenance state of each turbosupercharger.
Speed controller can be configured to provide in order to the quick control of compensation dynamic differential and in order to compensate the control at a slow speed of permanent difference or static difference.
Controller can be configured to turbosupercharger is moved near setting value, and this moment, they had the peak efficiency near surge limit.
Controller can use represents for example signal of the engine operating state of inlet temperature and scavenging temperature, waste heat box pressure, waste heat box temperature, outlet temperature and/or outlet pressure and so on, as far as possible accurately to determine the distance of each turbosupercharger to surge limit.
Another object of the present invention provides a kind of method that is used to control a plurality of variable turbochargers, described turbosupercharger is parallel to the scavenging air box of the large-scale two-stroke diesel engine with a plurality of cylinders that are provided with in upright arrangement, this method comprises: the nozzle area of total expectation of all variable turbochargers of control in the scavenging pressure feedback loop, and under the restrictive condition of total nozzle area of the whole expectation of the variable turbochargers in a plurality of variable turbochargers speed feedback loops, control the nozzle area of each variable turbochargers.
Can control the nozzle area of each turbosupercharger, so that all turbosupercharger obtain consistent speed.
Linear quadratic type regulator can be used in the nozzle area of each turbosupercharger of control.
When operating conditions takes place to change fast, promptly under the situation of high seas (propeller cavitation raises and surpasses the sea level), change fast in speed under (promptly stop and handling) and other situation, can use dynamic anti-surge algorithm with equilibrium response.When if if the speed of turbosupercharger has remarkable difference or one of them turbosupercharger to break down, this is relevant especially.
When the nozzle area of each variable turbochargers of control, can consider the static difference between each variable turbochargers.
Another object of the present invention provides a kind of large-scale two-stroke diesel engine, and it has: a plurality of cylinders that are provided with in upright arrangement; A plurality of nozzle area variable turbochargers, described variable turbochargers are parallel between the waste heat box and scavenging air box of motor; Be coupled to the controller of described variable turbochargers, described controller is provided with the speed of each variable turbochargers, described variable turbochargers is provided with the actuator of the nozzle area that is used to change them, and described controller is configured to determine to have based on the position of the speed of all variable turbochargers and the turbosupercharger that do not break down the actual nozzle area of the variable turbochargers of the actuator that has broken down.
By detailed explanation, according to other purpose, feature, advantage and the characteristic of large-scale two-stroke diesel engine of the present invention and the method that is used to control large-scale two-stroke diesel engine will become obvious.
Description of drawings
In the detailed part below this specification, the present invention is introduced in more detail with reference to illustrative embodiments illustrated in the accompanying drawings, wherein:
Fig. 1 is the front elevation according to the large-scale two-stroke diesel engine of embodiment of the present invention;
Fig. 2 is the side view of the two-stroke diesel engine of Fig. 1;
Fig. 3 is the block diagram of the gas handling system and the vent systems of the motor among Fig. 1; And
Fig. 4 is the Block Diagram that is used for the controller of Fig. 1 engine turbine pressurized machine.
Embodiment
In the detailed description below, will the present invention be described by preferred implementation.Fig. 1-3 shows the crosshead type large turbocharging type two-stroke diesel engine 1 that has its gas handling system and vent systems.Motor 1 has scavenging air box 2 and waste heat box 3.In these casees each all extended along the whole length of motor.The cylinder of setting in upright arrangement that motor has a plurality of (usually between 5 to 14).The exhaust valve that is connected to the firing chamber is by 4 expressions.Motor 1 can be for example as the master motor in the ocean going vessel or as the stationary engine that makes generator operation in the power station.The overall output of this motor for example can be between 5,000 to 110, the scope of 000kW.Motor 1 utilizes the heavy fuel oil operation usually, thereby is provided with the heavy fuel oil system, and this heavy fuel oil system comprises the heavy fuel oil pipeline (not shown) of the restrike fuel tank and the heating of heating.The element of these heating of fuel injection system also is heated at the motor stopping period, because heavy fuel oil viscosity when room temperature is extremely big.And heavy fuel oil system (not shown) is provided with recirculating system, and this recirculating system keeps flow through each parts of heavy fuel oil system of heavy fuel oil at the motor stopping period.This recirculation has guaranteed that each parts that do not have its special heating equipment of heavy fuel oil system keep warm heat at the motor stopping period, and the degasification of heavy fuel oil system is convenient in this recirculation.
Scavenging flows to the scavenging port (not shown) of each cylinder from scavenging air box 2.When exhaust valve 4 is opened, waste gas flows in the waste heat box 3 through first exhaust piping and arrives the variable area formula turbine 7 (nozzle area variable turbochargers) of one of them variable turbochargers of a plurality of variable turbochargers 6 forward through first exhaust piping 5, and waste gas flows out through second exhaust piping 20 from this variable area formula turbine 7.Each variable area formula turbine 7 drives via air inlet 10 compressed and supplied machines 9 by axle 8.Compressor 9 scavenging of will pressurizeing is sent to scavenge line 11 towards scavenging air box 2.As shown in Figure 2, variable turbochargers 6 distributes on the whole length of motor 1 substantially equably.In the present embodiment, have three variable turbochargers 6, but this number only is an example, can has still less individual or more a plurality of variable turbochargers.
Each variable turbochargers 6 is provided with actuator, and described actuator is controlled the nozzle area of described variable turbochargers 6.Each actuator of a plurality of variable turbochargers 6 all is connected to controller 50.
The inlet stream of pipeline 11 is through cooling unit 12, and the about 200 ℃ pressurized air/scavenging that is used for leaving compressor is cooled between 36 ℃ to 80 ℃.Cooling unit 12 can be an air scrubber in one embodiment, and a large amount of water injection and evaporation are so that pressurized air/scavenging humidity in air scrubber.
The auxiliary blower 16 chilled and scavenging humidity is flowed through and driven by electric motor 17, this auxiliary blower make under the situation of low load or partial load in pressurization of scavenging stream and the arrival scavenging air box 2.When high capacity, the compressor 9 of turbosupercharger transmits sufficient compressed scavenging, and then auxiliary blower 16 is via safety check 15 bypasses.
The variable area formula turbine 7 of each turbosupercharger 6 is coupled to controller 50 by actuator.The nozzle area of controller 50 control area changable type turbines 7, and controller 50 receives the information relevant with the motor operation conditions.
Fig. 4 illustrates in greater detail controller 50.Controller 50 comprises two control loops.First control loop is a pressure control circuit, and it is configured to scavenging pressure is remained on predetermined normal value level, is called " pressure set points " in the accompanying drawings.Pressure control circuit is the external circuit of two control loops.And controller 50 comprises the variable turbochargers speed control loop, and this speed control loop is controlled the relative velocity of each variable turbochargers 6 separately.The speed control loop of variable turbochargers is a home loop, and promptly it can only move in the lit range that pressure control circuit is set.
Pressure control circuit comprises pressure controller, the corresponding signal of difference between this pressure controller reception and pressure set points and the pressure that records in scavenging air box 2.This pressure controller produces the signal that a total nozzle area with the variable turbochargers of expecting adapts, and this signal is sent to the speed controller of the variable turbochargers in speed loop.
The speed controller of variable turbochargers is controlled the speed of each variable turbochargers 6 separately in feedback control circuit.Thereby, each variable turbochargers 6 is parts of speed control loop, wherein relevant variable turbochargers 6 receives the individual signals of nozzle area that is used to set single relevant variable turbochargers 6 of the speed controller that comes from variable turbochargers, and speed controller receives the signal of the speed of each single variable turbochargers 6 of expression.
The speed controller of variable turbochargers receives multiple engine operating parameter, for example inlet temperature, scavenging temperature, waste heat box pressure, waste heat box temperature, outlet temperature and outlet pressure, and correspondingly regulate the control signal that is delivered to each variable turbochargers 6.
Each speed control loop can not comprise linear quadratic type regulator in one embodiment and comprise PID (ratio/integration/difference) function, to obtain required variable turbochargers speed.
The speed controller of variable turbochargers guarantees that variable turbochargers 6 nozzle area altogether equals the output signal of pressure controller, to keep required scavenging pressure.Yet the nozzle area of each independent variable turbochargers 6 can change in such restrictive condition, that is, variable turbochargers 6 gross area altogether equals the value of the output signal of pressure controller.
The variation of the setting value of a variable turbochargers 6 therein will exert an influence to other turbosupercharger 6.For example, if the area of all variable turbochargers 6 reduces, then the variable turbochargers speed of all turbosupercharger 6 will increase.Yet if only there is one of them variable turbochargers 6 to reduce its nozzle area, the speed of this specific variable turbochargers 6 will reduce, and the speed of other variable turbochargers 6 will increase.If there is not suitable control algorithm, these influences will cause a kind of unsettled situation.Thereby speed controller is configured to consider the influence that the variation of the setting value of one of them turbosupercharger 6 produces other turbosupercharger, and the influence of the nozzle area of considering turbosupercharger when changing simultaneously.Arrive this, the speed controller of variable turbochargers comprises linear quadratic type regulator (LQR) in one embodiment, so that a kind of controller that overcomes above-mentioned influence and stablize this system to be provided.
Soon and slowly control simultaneously and implement, to realize different purposes.The compensation of carrying out for permanent difference that will be further described below is applied to control slowly.The compensation of carrying out for for example dynamic differential of violent load change and so on is applied to fast control.
The speed controller of variable turbochargers is configured to obtain roughly the same speed for each variable turbochargers 6 usually, because when all variable turbochargers 6 have roughly the same speed, motor 1 will move most effectively.
Yet, some exceptions are arranged for the principle that all variable turbochargers 6 are moved at the same rate.
One of them exception relates to the pressure surge in the scavenging air box 2.In large-scale scavenging air box 2, there is big low frequency standing wave at the motor run duration.Locate if turbosupercharger 6 accurately is positioned at " eye ", it will can not stand any big pressure surge by the low frequency wave generation.Yet in fact variable turbochargers 6 must and only have some of them can accurately be positioned at " eye " along the distribution of lengths of motor to locate.All the other variable turbochargers 6 will stand big low frequency pressure surge, and will be all the more so when particularly they are set to vertical end near microscler scavenging air box 2.Because such setting, big low frequency pressure surge will have influence for the operation conditions of relevant variable turbochargers 6.Therefore, the speed of related turbine pressurized machine 6 may fluctuate, and the related turbine pressurized machine that is exposed to very near these low frequency pressure surges of surge line may not move, because surpass surge line and make the risk of related turbine pressurized machine 6 stalls too high.
Thereby controller 50 is provided with setting value, and it makes any turbosupercharger 6 be exposed to big pressure surge also have at the distance surge line under the situation of big nargin and moves.Usually, this means the speed operation with other turbosupercharger of being slightly less than motor 1 of the variable turbochargers 6 that is exposed to big low frequency pressure surge in practice.
Another factor is the difference of the inlet temperature of each variable turbochargers 6.Inlet temperature is directly measured on each turbosupercharger 6 sometimes, but also can estimate according to the knowledge of temperature distribution in the temperature transducer binding engine chamber in the engine compartment.And this difference in the inlet temperature may relate to the position of relevant variable turbochargers 6 along the length of motor, and this controller is configured to be increased to by the speed that increases turbosupercharger the distance of surge line.
The also very fast generation of another part thing, because the speed fluctuation of turbosupercharger will bring extra wearing and tearing, and therefore the speed of the variable turbochargers of fluctuation will reduce.These two aspects force to be controlled on the opposite direction carries out.Yet, for surge be higher than load 75%, no problem under the serious situation of wearing and tearing, so controller is configured to gather way, when high loading, reduce speed when partial load, thereby realize optimum process.
Some other exception for the principle that all turbosupercharger are moved at the same rate relates to the state of safeguarding each variable turbochargers 6.In the reality, common all turbosupercharger that can during a maintenance phase, not overhaul motor 1.This means in a plurality of variable turbochargers 6 and only overhaul one or two turbosupercharger, and other variable turbochargers 6 must be waited for next maintenance phase.Safeguard that less variable turbochargers 6 can not move near surge line as the full wheel pressurized machine 6 that newly overhauled.Thereby controller 50 is provided with the maintenance state of each turbosupercharger 6, and new turbosupercharger of overhauling is more being moved under the state near surge line than the turbosupercharger 6 of not maintenance.Usually, this means that the variable turbochargers 6 that had overhauled recently in the reality is moving than the speed that turbosupercharger 6 of maintenance is slightly not high recently.
And the instrument error of variable turbochargers is quite high, even therefore variable turbochargers is same type, but one of their feature is all different with another.These differences of controller compensation.The result of the machine error in variable turbochargers 6 is the deviation of turbocharger speed normally, and because controller is configured to the speed of balance variable turbochargers, so the error effect is offset.
When obviously different separately or one of them variable turbochargers 6 has broken down when the speed of each variable turbochargers 6, use dynamic anti-surge algorithm with equilibrium response.
When the actuator of a variable turbochargers 6 broke down therein, its nozzle location was according to the speed of all other variable turbochargers and the location estimation of other variable turbochargers 6.Thereby controller 50 is known the summation of all variable turbochargers 6 nozzle area altogether and the tram of the variable turbochargers 6 that can determine not break down.
In a mode of execution (not shown), wherein one or more turbosupercharger 6 are immutable types, and all the other turbosupercharger of motor are variable types.In this system, controller is known nozzle area that can not the variant turbosupercharger and is correspondingly regulated the variable area of all the other variable turbochargers.
In one embodiment, this system has two turbosupercharger.One of them is variable and another is traditional.Variable turbochargers is normally bigger one in the two.When hanging down load, variable turbochargers is closed (minimizing nozzle area) as far as possible to increase waste heat box pressure.This is sent to the size (mainly be sent to littler can not variant turbosupercharger) of the energy of turbosupercharger with increase, thereby scavenging pressure is increased.Variable turbochargers should remain on the right side of surge limit value certainly.When high capacity, purpose is to avoid the turbosupercharger of less (tradition) to reach at a high speed, is not only for fear of hypervelocity and for fear of wearing and tearing.
Above-mentioned situation is to compare with existing variable turbochargers solution by increasing the nozzle scope to be improved.
Same principle can be used in the system with two above turbosupercharger.
They are on the other hand, when a motor uses the turbosupercharger of a plurality of traditional types, need oversize, because must be same.This oversize problem can be by mix using large-scale and the small sized turbine pressurized machine be avoided, and this only can just be achieved when one of them of the turbosupercharger of these mixed size is variable type on the other hand.
Above-mentioned various aspect can be used separately or with various combining forms.The application's instruction preferably realizes by the combination of hardware and software, but also can realize with hardware mode.The application's instruction can also be embodied as the computer-readable code on the computer-readable medium.
The application's instruction has multiple advantage.Different mode of executions or realization can obtain wherein one or more of following advantage.Should be noted that this is not enumerating of limit and may has other advantage of not describing here.An advantage of the application's instruction provides the reliable control of a plurality of turbosupercharger in large-scale two-stroke diesel engine.Another advantage of the application's instruction provides the reliable control of a plurality of turbosupercharger in a kind of large-scale two-stroke diesel engine that can consider the static difference between the single turbosupercharger.Another advantage of the application's instruction provides the urgent and/or complicated operation situation control of a plurality of variable turbochargers of large-scale two-stroke diesel engine.Another advantage of the present invention provides the even velocity substantially of variable turbochargers, and this provides optimum engine performance and the discharging that reduces again, and has reduced wearing and tearing.Another advantage of the present invention provides a kind of control system, and this control system has reduced the risk of stall.Another advantage of the present invention is to make fault treatment be able to optimization.Another advantage of the present invention is the local difference that can offset in the turbosupercharger operation situation.An also advantage of the present invention is to allow optimization to utilize the variable turbochargers of different sizes.An advantage more of the present invention provides the control of variable turbochargers with mixing and large-scale two-stroke diesel engine that can not the variant turbosupercharger, and this cost that allows to be used for the variable turbochargers of big-block engine again reduces.
Although described the application's instruction for illustrative purposes in detail, it should be understood that these details only are for explanatory purposes, and those skilled in the art can make distortion under the situation of the scope of the instruction that does not depart from the application.
The term that uses in the claim " comprises " does not get rid of other element or step.The term that uses in the claim " one " or " one " do not get rid of a plurality of.Single processor or other unit can satisfy the function of the multiple arrangement of putting down in writing in the claim.
Claims (14)
1. large-scale two-stroke diesel engine, it has:
A plurality of cylinders that are provided with in upright arrangement;
A plurality of nozzle area variable turbochargers, described variable turbochargers are parallel between the waste heat box and scavenging air box of described motor;
Be coupled to the controller of described variable turbochargers, described controller comprises external pressure loop and internal speed loop, described external pressure loop comprises pressure controller, described internal speed loop comprises speed controller, described pressure controller is configured to determine described turbosupercharger total nozzle area altogether of expectation, and described speed controller is configured to control separately the speed of each described turbosupercharger.
2. large-scale two-stroke diesel engine as claimed in claim 1, wherein, described speed controller is arranged such that in each described variable turbochargers each all obtains speed about equally.
3. large-scale two-stroke diesel engine as claimed in claim 1, wherein, described speed controller is configured to compensate the change of setting value of one of them described variable turbochargers to the influence of other described variable turbochargers.
4. as each described large-scale two-stroke diesel engine among the claim 1-3, wherein, described speed controller is configured to compensate the speed difference that the Different Effects by the low frequency pressure wave in the described scavenging air box causes, and the Different Effects of described low frequency pressure wave is caused by the difference of each described turbosupercharger position.
5. as each described large-scale two-stroke diesel engine among the claim 1-4, wherein, described speed controller is configured to compensate the maintenance state of each described turbosupercharger.
6. each described large-scale two-stroke diesel engine in the claim as described above, wherein, described speed controller provides in order to the quick control of compensation dynamic differential and in order to compensate the control at a slow speed of permanent difference or static difference.
7. each described large-scale two-stroke diesel engine in the claim as described above, wherein, described controller is configured to make described turbosupercharger near described setting value operation, and this moment, they had the peak efficiency near surge limit.
8. large-scale two-stroke diesel engine as claimed in claim 7, wherein, described controller uses represents for example signal of the engine operating state of inlet temperature and scavenging temperature, waste heat box pressure, waste heat box temperature, outlet temperature and/or outlet pressure and so on, as far as possible accurately to determine the distance of each described turbosupercharger to described surge limit.
9. method that is used to control a plurality of variable turbochargers, described turbosupercharger are parallel to the scavenging air box of the large-scale two-stroke diesel engine with a plurality of cylinders that are provided with in upright arrangement, and this method comprises:
The nozzle area of total expectation of all variable turbochargers of control in the scavenging pressure feedback loop, and
Under the restrictive condition of total nozzle area of the whole expectation of the described variable turbochargers in the speed feedback loop of a plurality of variable turbochargers, control the nozzle area of each described variable turbochargers.
10. method as claimed in claim 9, wherein, the nozzle area of each described turbosupercharger is controlled as the speed that obtains unanimity for all described turbosupercharger that makes.
11. method as claimed in claim 10, wherein, linear quadratic type regulator is used to control the nozzle area of each described turbosupercharger.
12. method as claimed in claim 11 wherein, when obviously different or one of them described turbosupercharger breaks down when the speed of each described turbosupercharger, is used the dynamic anti-surge algorithm with equilibrium response.
13. method as claimed in claim 12 wherein, is considered the static difference between each described variable turbochargers when the nozzle area of each described variable geometry turbocharger of control.
14. a large-scale two-stroke diesel engine, it has:
A plurality of cylinders that are provided with in upright arrangement;
A plurality of nozzle area variable turbochargers, described variable turbochargers are parallel between the waste heat box and scavenging air box of described motor;
Be coupled to the controller of described variable turbochargers, the speed of each described variable turbochargers is provided to described controller, described variable turbochargers is provided with the actuator of the nozzle area that is used to change them, and described controller is configured to determine to have based on the position of the speed of all described variable turbochargers and the described turbosupercharger that do not break down the actual nozzle area of the described variable turbochargers of the actuator that has broken down.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2008129066A JP4528339B2 (en) | 2008-05-16 | 2008-05-16 | Large two-cycle diesel engine with multiple variable turbochargers |
| JP2008129066 | 2008-05-16 | ||
| JP2008-129066 | 2008-05-16 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101581249A true CN101581249A (en) | 2009-11-18 |
| CN101581249B CN101581249B (en) | 2012-02-22 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200810125295XA Active CN101581249B (en) | 2008-05-16 | 2008-06-30 | Large-size two-stroke diesel motor with a plurality of variable turbochargers |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP4528339B2 (en) |
| KR (1) | KR101026741B1 (en) |
| CN (1) | CN101581249B (en) |
| CH (1) | CH698244B1 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102937528A (en) * | 2012-10-31 | 2013-02-20 | 沈阳黎明航空发动机(集团)有限责任公司 | Method for adjusting supercharging conversion rotation speed of aero engine |
| CN103452685A (en) * | 2012-06-04 | 2013-12-18 | 罗伯特·博世有限公司 | Method and device for diagnosing an actuator for an exhaust-gas-driven supercharger |
| CN105545533A (en) * | 2014-10-07 | 2016-05-04 | 温特图尔汽柴油公司 | Piston type internal combustion engine and exhaust gas master pipe, in particular combined exhaust gas master pipe |
| CN105673219A (en) * | 2014-12-08 | 2016-06-15 | 通用汽车环球科技运作有限责任公司 | Energy balance based boost control using feedback linearization |
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| IT1395038B1 (en) * | 2009-08-12 | 2012-09-05 | Magneti Marelli Spa | METHOD OF CONTROL OF A COMMON-RAIL TYPE DIRECT INJECTION SYSTEM |
| JP6071583B2 (en) * | 2013-01-24 | 2017-02-01 | 三菱重工業株式会社 | Control device, supercharging system, control method and program |
| EP3112631A1 (en) * | 2015-06-29 | 2017-01-04 | Winterthur Gas & Diesel Ltd. | Air supply arrangement, internal combustion engine, method for additional air supply of an internal combustion engine and method of refitting an internal combustion engine |
| KR102237209B1 (en) * | 2017-10-24 | 2021-04-07 | 현대중공업 주식회사 | Ship Engine and Method for Ship Engine |
| US11319906B2 (en) * | 2020-10-06 | 2022-05-03 | Ford Global Technologies, Llc | Methods and systems for an exhaust gas recirculation system |
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| KR100290398B1 (en) * | 1997-12-31 | 2001-07-12 | 이계안 | Turbo charger control apparatus |
| JP3953636B2 (en) * | 1998-04-30 | 2007-08-08 | 富士重工業株式会社 | Multistage turbocharging system for reciprocating engine |
| JP2000356136A (en) | 1999-06-14 | 2000-12-26 | Yanmar Diesel Engine Co Ltd | Two-stage supercharging device for internal combustion engine |
| US6550247B1 (en) | 2001-08-30 | 2003-04-22 | Caterpillar Inc | Multiple parallel turbocharger control with discrete step nozzles |
| JP2006083717A (en) * | 2004-09-14 | 2006-03-30 | Nissan Motor Co Ltd | Supercharging pressure regulator of variable supercharging system |
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- 2008-05-16 JP JP2008129066A patent/JP4528339B2/en active Active
- 2008-06-09 KR KR1020080053836A patent/KR101026741B1/en active IP Right Grant
- 2008-06-30 CN CN200810125295XA patent/CN101581249B/en active Active
- 2008-09-03 CH CH01407/08A patent/CH698244B1/en unknown
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103452685A (en) * | 2012-06-04 | 2013-12-18 | 罗伯特·博世有限公司 | Method and device for diagnosing an actuator for an exhaust-gas-driven supercharger |
| CN102937528A (en) * | 2012-10-31 | 2013-02-20 | 沈阳黎明航空发动机(集团)有限责任公司 | Method for adjusting supercharging conversion rotation speed of aero engine |
| CN102937528B (en) * | 2012-10-31 | 2014-12-24 | 沈阳黎明航空发动机(集团)有限责任公司 | Method for adjusting supercharging conversion rotation speed of aero engine |
| CN105545533A (en) * | 2014-10-07 | 2016-05-04 | 温特图尔汽柴油公司 | Piston type internal combustion engine and exhaust gas master pipe, in particular combined exhaust gas master pipe |
| CN105587432A (en) * | 2014-10-07 | 2016-05-18 | 温特图尔汽柴油公司 | Piston type internal combustion engine, exhaust distributing pipe and particularly combined exhaust distributing device |
| CN105673219A (en) * | 2014-12-08 | 2016-06-15 | 通用汽车环球科技运作有限责任公司 | Energy balance based boost control using feedback linearization |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101581249B (en) | 2012-02-22 |
| JP4528339B2 (en) | 2010-08-18 |
| CH698244B1 (en) | 2009-06-30 |
| KR101026741B1 (en) | 2011-04-08 |
| KR20090119655A (en) | 2009-11-19 |
| JP2009275644A (en) | 2009-11-26 |
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Address after: Copenhagen, Denmark Patentee after: Mannone solutions (mannone solutions Germany) branch Address before: Copenhagen, Denmark Patentee before: Mann Diesel & Turbine, an associate company of Mann Diesel & Turbine Europe AG |