CN102619615A - Large turbocharged two-stroke diesel engine with exhaust gas recirculation - Google Patents
Large turbocharged two-stroke diesel engine with exhaust gas recirculation Download PDFInfo
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- CN102619615A CN102619615A CN2012100216312A CN201210021631A CN102619615A CN 102619615 A CN102619615 A CN 102619615A CN 2012100216312 A CN2012100216312 A CN 2012100216312A CN 201210021631 A CN201210021631 A CN 201210021631A CN 102619615 A CN102619615 A CN 102619615A
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- A—HUMAN NECESSITIES
- A42—HEADWEAR
- A42B—HATS; HEAD COVERINGS
- A42B3/00—Helmets; Helmet covers ; Other protective head coverings
- A42B3/04—Parts, details or accessories of helmets
- A42B3/06—Impact-absorbing shells, e.g. of crash helmets
- A42B3/066—Impact-absorbing shells, e.g. of crash helmets specially adapted for cycling helmets, e.g. for soft shelled helmets
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- A—HUMAN NECESSITIES
- A42—HEADWEAR
- A42B—HATS; HEAD COVERINGS
- A42B3/00—Helmets; Helmet covers ; Other protective head coverings
- A42B3/04—Parts, details or accessories of helmets
- A42B3/10—Linings
- A42B3/12—Cushioning devices
- A42B3/121—Cushioning devices with at least one layer or pad containing a fluid
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- A—HUMAN NECESSITIES
- A42—HEADWEAR
- A42B—HATS; HEAD COVERINGS
- A42B3/00—Helmets; Helmet covers ; Other protective head coverings
- A42B3/04—Parts, details or accessories of helmets
- A42B3/10—Linings
- A42B3/12—Cushioning devices
- A42B3/125—Cushioning devices with a padded structure, e.g. foam
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- A—HUMAN NECESSITIES
- A42—HEADWEAR
- A42B—HATS; HEAD COVERINGS
- A42B3/00—Helmets; Helmet covers ; Other protective head coverings
- A42B3/04—Parts, details or accessories of helmets
- A42B3/28—Ventilating arrangements
- A42B3/286—Ventilating arrangements with forced flow, e.g. by a fan
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
- F04F7/00—Pumps displacing fluids by using inertia thereof, e.g. by generating vibrations therein
- F04F7/02—Hydraulic rams
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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
The invention relates to a large turbocharged two stroke diesel engine (1) of the crosshead type that is provided with an exhaust gas recirculation system (30,32) that can be activated or deactivated or can be operated with variable exhaust gas recirculation rates. In order to ensure proper matching of the turbocharger (16) , and in particular the compressor (18) of the turbocharger (16) in all operating conditions, a cylinder bypass flow path (40) that includes a controllable valve (42) enables matching the turbocharger 16 to the engine (1) in operation modes with or without exhaust gas recirculation.
Description
Technical field
The present invention relates to large-sized turbo-charging two-stroke crosshead piston IC engine, preferably relate to the DENG that has emission control system, particularly have the cross hair style large-sized two-stroke diesel engine of exhaust gas recycling system.
Background technique
The large-sized two-stroke typical of engines ground of cross hair style uses in the propulsion system of large ship or as the motor in the power station.Emission request has been difficult to satisfy and will be difficult to day by day satisfy, particularly about the emission request of the horizontal aspect of nitrogen oxide (NOx).
Exhaust gas recirculatioon is to be known as the measure that helps in combustion engine, to reduce NOx.
For satisfying multiple emission request; For example International Maritime Organization (IMO) Tier II and Tier III emission standard; Advantageously configurable in cross hair style large two-stroke diesel engine have the exhaust gas recycling system operation, but said exhaust gas recycling system opening and closing or exhaust gas recirculatioon ratio wherein are variable.
The turbosupercharger of large cross-head formula two stroke engine needs and Engine Matching; Guaranteeing that turbosupercharger do not block (choke) or surge under any engine operating condition, and guarantee that turbosupercharger operates to and make it that desired scavenging pressure and efficient are provided.Whether compressor characteristics has confirmed turbosupercharger near its maximal efficiency operation, but has enough surging overmeasures to guarantee compressor stability.Surging overmeasure needs, because the turbosupercharger operating point maybe be during transient state, for example engine load reduces fast, or under abnormal situation near the surge line among the compressor MAP figure.
Yet, when the exhaust gas recirculatioon ratio in the large two-stroke diesel engine from for example 40% when changing into 0%, will increase about 30% to 40% in the mass flow of the exhaust of the ingress of leading to turbosupercharger.Therefore, if turbosupercharger and motor mate under 40% exhaust gas recirculatioon ratio, then not working when exhaust gas recirculatioon will exist not matching of scavenging pressure constantly.The blade-carrying compressor of the turbosupercharger of using at present is a singlet, and it does not have flux capacity and the required gamut of scavenging pressure variation that takes place when the operation that has exhaust gas recirculatioon switches to the operation that does not have exhaust gas recirculatioon when operation for reply.
Therefore, the demand that has the turbosupercharging two-stroke diesel engine of the coupling that does not jeopardize turbosupercharger and motor for moving with the exhaust gas recirculatioon ratio that changes.
Summary of the invention
Under this background, task of the present invention provides the large-sized turbo-charging two-stroke diesel engine, and said DENG can and/or have work or the operation of idle exhaust gas recycling system with the variable exhaust recirculation rates.
This task realizes that through cross hair style large-sized turbo-charging two-stroke combustion engine is provided said combustion engine comprises: a plurality of cylinders of provided in-line; The exhaust receiver that has big volume, said exhaust receiver are used for equilibrium provides constant with the outlet port at exhaust receiver from the pressure pulsation of the exhaust of independent cylinder pressure; The outlet of exhaust receiver is connected to the outlet pipe of the turbo machine of turbosupercharger; Turbosupercharger by turbine driven compressor, said compressor is transported to the scavenging receiver through the scavenging path that comprises the scavenging cooler with scavenging; The auxiliary wind blower relevant with the scavenging path, said auxiliary wind blower are used for auxiliary turbines under low engine load condition; Said scavenging receiver is connected to cylinder and has big volume to reduce because to the mobile pressure pulsation that causes of the inlet of independent cylinder; Exhaust gas recirculatioon stream, said stream comprise that a part that is used for exhaust supplies to wind blower or compressor in the scavenging; The part of the hot scavenging that is used for before the scavenging cooler, obtaining supplies to the cylinder bypass flow path of the turbo machine of turbosupercharger, and said cylinder bypass flow path comprises that controlled valve is with control flowing through the cylinder bypass flow path.
Thereby through providing the cylinder bypass flow path to allow to utilize the exhaust gas recirculatioon additional energy to make the turbo machine that directly flows to turbosupercharger from the hot scavenging of the compressor of turbosupercharger at run duration; Said additional energy otherwise will fall in the air-cooler internal loss; And mass flow is provided to the turbo machine of turbosupercharger and only is provided to turbo machine, and this causes the operating point (to higher scavenging pressure) of operating point when exhaust gas recirculatioon is not worked of turbosupercharger to move.This allows turbosupercharger in the operating mode that has exhaust gas recirculatioon with do not have in the operating mode of exhaust gas recirculatioon and all mate well with motor, and in two operating modes, acceptable scavenging pressure is provided all.
Be to obtain desirable effect, the specific energy of the gas flow in the cylinder bypass line that crucial is keeps constant before it reaches turbo machine or even increase.Any energy loss will reduce or even eliminate desirable effect fully.
In an embodiment, ECU is configured to increase and increase the aperture of said valve and vice versa along with the exhaust gas recirculatioon ratio, make turbosupercharger motor in order to all EGR of operation than under and Engine Matching.
In an embodiment, the exhaust gas recirculatioon stream can be worked or not work.
Preferably, when work in the exhaust gas recirculatioon path, the valve in the cylinder bypass flow path is opened or is partially opened.
In an embodiment, when work in the exhaust gas recirculatioon path, the valve in the cylinder bypass flow path is opened or is partially opened.
In another embodiment; Cross hair style large-sized turbo-charging two-stroke combustion engine comprises ECU; Said ECU is configured to control the exhaust gas recirculatioon ratio through the wind blower in the control exhaust gas recirculatioon stream; Make to change the exhaust gas recirculatioon ratio, and wherein said ECU be configured to exhaust gas recirculatioon ratio, engine load and combustion chamber components on the acceptable heat load aperture of control valve relatively.The aperture of acceptable cylinder bypass valve will be trading off between three factors.
Preferably; ECU is configured to increase the aperture of valve along with the increase of exhaust gas recirculatioon ratio and vice versa; And along with engine load reduces the aperture that increases valve, the allowance of heat load increases and the driving pressure difference at cylinder bypass valve two ends reduces because under lower engine load, can accept.Above combination means aperture needs of cylinder bypass and turned to for different running mode by preparatory program considers this situation.
In an embodiment; Cross hair style large-sized turbo-charging two-stroke combustion engine further comprises the ECU that is configured to control the exhaust gas recirculatioon ratio, and wherein ECU (50) is configured to relevant with the exhaust gas recirculatioon ratio and controls flowing through cylinder bypass path (40) relatively with engine load.
In an embodiment, exhaust gas recirculatioon path and cylinder bypass flow path are through the heat exchanger heat exchange.In this way, maximum available energy is recovered and is sent to turbo machine.
Above purpose also realizes through the method that is provided for making the cross hair style large-sized two-stroke turbo-charging diesel motor operation that has cylinder bypass tube and exhaust gas recycling system; Said operation method comprises: when exhaust is recycled, allow scavenging bypass cylinder, and when exhaust is not recycled, do not allow the air by-pass cylinder.
Above purpose also realizes that through the method that is provided for making the cross hair style large-sized two-stroke turbo-charging diesel motor operation that has cylinder bypass tube and exhaust gas recycling system said operation method comprises: control flowing with the bypass cylinder of scavenging relatively with exhaust gas recirculatioon ratio and engine load.
To become obvious with other task, characteristic, advantage and the characteristic method that is used to make the operation of large-sized two-stroke turbo-charging diesel motor according to describing in detail according to large-sized two-stroke diesel internal-combustion engine of the present invention.
Description of drawings
In the following part in detail of this specification, will explain the present invention in more detail with reference to the exemplary embodiments shown in the accompanying drawing, each figure is:
Fig. 1 is the schematic representation of exemplary embodiments of the present invention,
Fig. 2 be according to another schematic representation of the embodiment's of Fig. 1 motor and
Fig. 3 is another exemplary embodiments according to motor of the present invention.
Embodiment
Hereinafter, will describe operation method in detail through exemplary embodiments according to cross hair style large-sized turbo-charging two-stroke diesel engine of the present invention and cross hair style large-sized turbo-charging two-stroke diesel engine.
Fig. 1 and Fig. 2 show first exemplary embodiments of large-sized two-stroke diesel engine 1.Motor 1 for example can be used as oceanic trip boats and ships master motor or with the static motor that acts on the generator of operation in the power station.Total output of motor for example can change in the scope of 2000kW to 110000kW.
The cylinder 2 that motor 1 is provided with a plurality of (typically between 5 and 14) becomes delegation to be arranged side by side.Each cylinder 2 is provided with reciprocating piston 3.Piston 3 is connected to bent axle 4 through piston rod 5, crosshead 6 and connecting rod 7.Crosshead 6 is included in the cross head bearing that is directed between the guide plane.
Each cylinder 2 is provided with the exhaust valve relevant with its cylinder head 10.The exhaust passage can open and close through exhaust valve 10.Exhaust elbow 11 is connected to exhaust receiver 12.Exhaust receiver 12 is near the big microscler hydrostatic columns the top of the row that is arranged in parallel and be arranged in cylinder 2.Exhaust receiver 12 has big volume, thus make exhaust receiver can be balanced because the pressure pulsation that becomes a mandarin and cause in the periodicity from the exhaust of Indivudual cylinder 2 of the opening of exhaust valve 12.The portfolio effect of exhaust receiver 12 makes the outlet port at exhaust receiver 12 have the pressure of constant.Requirement has constant compression force in the outlet port of exhaust receiver 12, because the turbosupercharger of the exhaust gas drive of in large-sized two-stroke diesel engine, using or a plurality of turbosupercharger 16 are benefited from constant supply pressure.
Exhaust is directed the turbo machine 17 (can have a plurality of turbosupercharger 16) to turbosupercharger 16 from exhaust receiver 12 through outlet pipe 14.Exhaust is arrived atmosphere in the downstream drain of turbo machine 17.Turbosupercharger 16 is constant voltage turbosupercharger, and promptly turbosupercharger 16 is not configured to the pressure pulsation work in the exhaust.Turbosupercharger 16 have axial flow turbine to or radial-flow turbine, and be configured to until 500 ℃ to 550 ℃ delivery temperature roughly.
Turbosupercharger 16 also comprises through turbo machine 17 compressor driven 18.Compressor 18 is connected to air inlet.Compressor 18 is transported to scavenging receiver 20 through scavenging air pipe 21 with the high pressure scavenging, and said scavenging air pipe 21 comprises scavenging cooler 22 and the auxiliary wind blower 23 relevant with safety check 24.Auxiliary wind blower 23 is typically by electrical motor driven (also can by fluid motor-driven), and under low load condition, (typically is being lower than 40% o'clock of maximum continuous constant engine value) and starts and keep enough scavengings with auxiliary compressor 18.When auxiliary wind blower 23 does not use (typically be higher than maximum continuous constant engine value 40% o'clock) through safety check 24 by bypass.
Scavenging receiver 20 is to be arranged in parallel and to be arranged near the big microscler hydrostatic column the bottom of row of cylinder 2.Scavenging receiver 20 has big volume, thereby makes scavenging receiver 20 to compensate owing to descend at the periodicity of the scavenging of leading to Indivudual cylinder 2 of the opening of scavenging port 26 pressure that causes that effluents.The compensation effect of scavenging receiver 20 has allowed the pressure of the constant in the scavenging receiver, makes each cylinder 2 can obtain roughly the same scavenging pressure.Constant compression force in the scavenging receiver 20 is requirement; Because promptly there are not the pressure pulsation that can use for the scavenging of Indivudual cylinder 2 in the turbosupercharger of in large-sized two-stroke diesel engine, using or a plurality of turbosupercharger 16 with the constant supply pressure operation and the supply pressure of delivered constant.
The scavenging port 26 of Indivudual cylinder 2 is led in scavenging from scavenging receiver 20.
In the exemplary embodiments kind of Fig. 1 and Fig. 2, exhaust gas recirculatioon pipe 32 is connected to scavenging air pipe 21 with outlet pipe 14.
In the embodiment shown in Fig. 1 and Fig. 2, exhaust gas recirculatioon pipe 32 comes out from outlet pipe 14 branches in the exhaust receiver location downstream, and is connected to scavenging air pipe 21 in the position at the upper reaches of scavenging cooler 22.
Exhaust gas recirculatioon pipe 32 comprises the multiple parts of vent systems.These parts can comprise cleaning equipment for example washing machine or filter, suction wind blower 33 (through electric motor or fluid motor-driven), cooler and one or more valve.
One end of cylinder bypass tube 40 in the downstream that are positioned at compressor 18 and the position that is positioned at exhaust gas recirculatioon pipe 32 and the upper reaches of the link position of scavenging air pipe 21 be connected to scavenging air pipe 21.Alternatively, an end of cylinder bypass tube 40 is connected to scavenging receiver 20, as indicating through the dotted line among Fig. 2.Other link positions along scavenging air pipe 21 also are fine.
The other end of cylinder bypass tube 40 is connected to the downstream, position of outlet pipe 14 and is connected to outlet pipe 40 in the position at the inlet upper reaches of turbo machine 17 at exhaust gas recirculatioon pipe 32.Also be fine along outlet pipe 14 or other link positions at exhaust receiver 12 places.
In an embodiment, valve 42 is open and close type valves, and said valve is through ECU 50 controls.In this embodiment, ECU 50 is configured to when exhaust gas recycling system is worked, open valve 42, and is configured to when exhaust gas recycling system is not worked or cut-off valve 42 when exhaust gas recycling system is worked under low exhaust gas recirculatioon ratio.
Be to obtain desirable effect, the specific energy of the gas flow in the cylinder bypass line that crucial is is kept constant before it reaches turbo machine or even is increased.Any energy loss will reduce or even eliminate desirable effect fully.
In another embodiment, electrically-controlled valve 42 is Proportional valves.In this embodiment, ECU is configured to control relatively with exhaust gas recirculatioon ratio and engine load the aperture of electrically-controlled valve 42.
In an embodiment, the level of the aperture of electrically-controlled valve 42 and exhaust gas recirculatioon ratio is inversely proportional to.
Exhaust gas recycling system can be owing to multiple former thereby do not work.A defective or the fault that reason can be an exhaust gas recycling system.The idle Another reason of exhaust gas recycling system is the chance of carrying out fuel optimization with respect to Tier II NOx emission level and for motor.The exhaust gas recirculatioon ratio can be for example 0% to roughly changing between 45%.
When exhaust gas recycling system when working state changes to off working state, the operating mode of turbosupercharger obviously changes.That is, turbosupercharger 16 is matched with motor 1 with at operation under the state of exhaust gas recycling system work (that is, for example roughly exhaust gas recirculatioon ratio between 20% to 45% and the state that has with the matched well of turbosupercharger 16 move down).When exhaust gas recycling system is not worked; If do not take counter-measure then turbosupercharger 16 will mate not good; Because scavenging pressure will increase roughly 25% with flowing, this is unacceptable under high engine load, and possibly cause the obstruction and the hypervelocity of turbosupercharger and cause poor efficiency.
For the exhaust gas recirculatioon motor that satisfies IMO Tier III Abgasgesetz or do not have the Tier II motor of exhaust gas recirculatioon (or in a small amount EGR), the coupling of turbosupercharger 16 is trading off between compressor stability (surging overmeasure) and the compressor/turbocharger efficiency/fuel consumption of motor 1.If the compressor of turbosupercharger is through best layout coupling when not having the exhaust gas recirculatioon operation, then unnecessary big surging overmeasure is because exhaust gas recirculatioon has reduced the flow velocity (engine operation point is shifted to surge line) through compressor 18.Conventional turbosupercharger or variable turbine area turbosupercharger do not have when between these two patterns, switching flow variation and do not jeopardize the flow range of scavenging pressure (boost pressure) and engine efficiency of desired reply.
In an embodiment, the compressor 18 of turbosupercharger 16 is mated for the exhaust gas recirculatioon operation, and opens cylinder bypass flow path 40.When switching to non-exhaust gas recirculatioon pattern, cylinder bypass flow path 40 is closed, thereby guaranteeing to flow increases and compressor 18 that scavenging pressure reduces to avoid turbosupercharger 16 blocks, and has obtained the optimum condition in the compressor characteristics (MAP figure).Another effect is for realizing that contemplated NOx reduces, requiring lower absolute exhaust gas recirculatioon mass flow, because the air flow through cylinder 2 reduces when cylinder bypass flow path 40 is opened.Another effect is that the capacity of exhaust gas recycling system self can reduce again, because need the amount of the exhaust of lower suction wind blower power and recirculation.Therefore, controller 50 is configured to increase the aperture of valve 42 and vice versa with the exhaust gas recirculatioon ratio, make turbosupercharger 16 and motor at all EGR that are being used for the motor operation than mating down.
The counter productive of cylinder bypass flow is that the heat load of motor increases, and this is because due to the swept volume through cylinder 2 reduces.
According to embodiment, turbosupercharger 16 is following with the coupling of motor operation:
When engine operation mode was changed into IMO Tier II, cylinder bypass flow path 40 was closed under the instruction of ECU 50 through valve 42, and roughly 90% time of continuous maximum rating, do not work for all engine loads in the exhaust gas recirculatioon path.
In the IMO Tier II pattern, scavenging pressure will be roughly increases with the IMO Tier III pattern of the exhaust gas recirculatioon that has work relatively, but scavenging pressure will be no more than matching pressure.Itself will cause lower discharging the scavenging pressure that under the sub load condition, increases, and allow to optimize the big scope than fuel consume (SFOC).
Under 90% engine load roughly, scavenging pressure will be near matching pressure.At this some place, turbosupercharger 16 has reached the coupling scavenging pressure, and along with the further increase of engine load, the exhaust gas recirculatioon ratio increases gradually, therefore scavenging pressure is maintained constant at 100% place of matching pressure.Therefore, in Tier II pattern, motor 1 under its sub load with the operation of high scavenging pressure, and scavenging pressure turnover (bend) under 90% engine load roughly.Under 100% engine load, roughly 30% the exhaust gas recirculatioon ratio that requires to be used to mate is to maintain scavenging pressure the coupling level.Therefore, under 90% engine load, with there being exhaust gas recirculatioon in a small amount, this will allow further and enough NOx dischargings to reduce.
Therefore, in impossible situation that exhaust gas recirculatioon stream 32 can not move, 90% of the maximum continuous power rating value of motor 1 will be capable of using, and the problem of compressor-free stability.Usually, turbosupercharger 16 can be tackled the increased pressure in the urgent Ministry of worker, and therefore in addition the maximum continuous power rating value of motor 1 100% will typically be possible.
Alternatively, in IMO Tier II operating mode, high pressure evaporator can be installed in the outlet pipe.In this situation, the coupling scavenging pressure obtains under 100% engine load, and does not use exhaust gas recirculatioon.Alternatively, the turbo machine bypass can be installed around turbo machine.Bypass is opened under 100% engine load, to obtain the coupling scavenging pressure.
Basically with identical with the embodiment that Fig. 2 describes with reference to figure 1, difference is to have added heat exchanger 44 in the embodiment shown in Fig. 3.Heat exchange between the exhaust of heat exchanger 44 permission recirculation and the scavenging of bypass.Therefore, the exhaust of recirculation is cooled and the bypass scavenging obtains even than the energy more energy of the turbo machine that is provided to turbosupercharger 16 17.
Through when in the EGR pattern, moving, using the cylinder bypass; Compensated to a great extent because the flow velocity and the reduction of scavenging pressure that the quality of the turbo machine loss of turbosupercharger and energy fluence cause, promptly the operating point of the compressor of turbosupercharger removing from surge line on the compressor MAP figure safety on the compressor MAP figure and regional efficiently mobile.
Other advantages of the present invention are the propelling reliabilities that in the situation of exhaust gas recycling system and component failure thereof, obviously increase, and in the operating identical compressor stability of IMO Tier II and III.High relatively scavenging pressure will guarantee low ratio fuel consume under sub load in IMO Tier 2 patterns, although there is not exhaust gas recirculatioon.
Describe in detail though the teaching of this application has been illustrated purpose, be understood that such details only is used for this purpose, and persons skilled in the art can change and do not depart from the scope of the teaching of this application it.
Above-described embodiment can make up to improve the function of motor with each possible mode.
Also it should be noted many alternative of the equipment that has the teaching of implementing this invention.
Like what in claim, use, term " comprises " does not get rid of other elements or step.Like what in claim, use, term " " or " one " do not get rid of a plurality of.Independent processor or other unit can satisfy the function of several devices of in claim, stating.
Claims (10)
1. a cross hair style large-sized turbo-charging two-stroke combustion engine (1) comprising:
A plurality of cylinders (2) of provided in-line,
Exhaust receiver (12), said exhaust receiver (12) has big volume, is used for the pressure pulsation of balanced exhaust from independent cylinder (2), with the outlet port at said exhaust receiver (12) pressure of constant is provided,
Outlet pipe (14), said outlet pipe (14) is connected to the turbo machine (17) of turbosupercharger (16) with the outlet of said exhaust receiver (12),
Said turbosupercharger (16) by said turbo machine (17) compressor driven (18), said compressor (18) is transported to scavenging receiver (20) with scavenging via the scavenging path (21) that comprises scavenging cooler (22),
Auxiliary wind blower (23), said auxiliary wind blower (23) is associated with said scavenging path (21), is used for auxiliary said turbo machine (17) under low engine load condition,
Said scavenging receiver (20), said scavenging receiver (20) is connected to said cylinder (2) and has big volume, is used to reduce the pressure pulsation of being flowed and being caused by the inlet that flows to independent cylinder,
Exhaust gas recirculatioon stream (32), said exhaust gas recirculatioon stream (32) comprise wind blower or compressor (33), be used for the part of said exhaust is supplied to said scavenging,
Cylinder bypass flow path (40), said cylinder bypass flow path (40) be used for the part in the hot scavenging of the preceding suction of said scavenging cooler (22) supply to said turbosupercharger (16) turbo machine (17) and
Controlled valve (42), said controlled valve (42) are used for control flowing through said cylinder bypass flow path (40).
2. cross hair style large-sized turbo-charging two-stroke combustion engine according to claim 1 (1), wherein said exhaust gas recirculatioon stream (32) can start and stop.
3. cross hair style large-sized turbo-charging two-stroke combustion engine according to claim 2 (1), wherein when said exhaust gas recirculatioon path (32) started, the said valve (42) in the said cylinder bypass flow path (40) was opened or is partially opened.
4. cross hair style large-sized turbo-charging two-stroke combustion engine according to claim 3 (1), the said valve (42) in the wherein said cylinder bypass flow path (40) is for have variable and controllable throttle degree through said valve mobile.
5. cross hair style large-sized turbo-charging two-stroke combustion engine according to claim 2; Further comprise ECU (50); Said ECU (50) is configured to control the exhaust gas recirculatioon ratio and make it possible to change said exhaust gas recirculatioon ratio through controlling wind blower in the said exhaust gas recirculatioon stream, and wherein said ECU is configured to consider the aperture that the heat load accepted on engine load and the combustion chamber components controls relatively with said exhaust gas recirculatioon ratio said valve (42).
6. cross hair style large-sized turbo-charging two-stroke combustion engine according to claim 5, wherein said ECU (50) are configured to increase the aperture of said valve (42) along with increasing the exhaust gas recirculatioon ratio, and vice versa.
7. cross hair style large-sized turbo-charging two-stroke combustion engine according to claim 5; Wherein said ECU (50) is configured to increase the aperture of said valve (42) along with increasing the exhaust gas recirculatioon ratio and vice versa, make said turbosupercharger (16) under whole EGR ratios of said motor operation all with said Engine Matching.
8. cross hair style large-sized turbo-charging two-stroke combustion engine according to claim 2; Further comprise ECU; Said ECU is configured to control the exhaust gas recirculatioon ratio, and wherein said ECU is configured to control flowing through said cylinder bypass flow path relatively relatively and with said engine load with the exhaust cycle ratio.
9. method that is used to move the cross hair style large-sized two-stroke turbo-charging diesel motor that has cylinder bypass tube and exhaust gas recycling system; It is characterized in that; When exhaust is recycled, allow scavenging to walk around cylinder, and when exhaust is not recycled, do not allow scavenging to walk around said cylinder.
10. a method that is used to move the cross hair style large-sized two-stroke turbo-charging diesel motor that has cylinder bypass tube and exhaust gas recycling system is characterized in that, controls flowing to walk around cylinder of scavenging relatively with the exhaust gas recirculatioon ratio.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DKPA201100060 | 2011-01-31 | ||
| DKPA201100060A DK177388B1 (en) | 2011-01-31 | 2011-01-31 | Large turbocharged two-stroke diesel engine with exhaust gas recirculation |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102619615A true CN102619615A (en) | 2012-08-01 |
| CN102619615B CN102619615B (en) | 2015-04-08 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210021631.2A Active CN102619615B (en) | 2011-01-31 | 2012-01-31 | Large turbocharged two-stroke diesel engine with exhaust gas recirculation |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP5661658B2 (en) |
| KR (1) | KR101274016B1 (en) |
| CN (1) | CN102619615B (en) |
| DK (1) | DK177388B1 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103967594A (en) * | 2013-05-21 | 2014-08-06 | 曼柴油机欧洲股份公司曼柴油机德国分公司 | Large two-stroke diesel engine and method for obtaining characteristics of a butterfly valve in the large two-stroke diesel engine |
| CN104564435A (en) * | 2013-10-29 | 2015-04-29 | 曼柴油机欧洲股份公司曼柴油机德国分公司 | A large slow running turbocharged two-stroke internal combustion engine |
| CN104854338A (en) * | 2012-12-28 | 2015-08-19 | 三菱重工业株式会社 | Internal combustion engine, ship, and method for operating internal combustion engine |
| CN106050373A (en) * | 2015-06-19 | 2016-10-26 | 曼柴油机欧洲股份公司曼柴油机德国分公司 | Large-size two-stroke turbocharging compression ignition explosive motor with waste gas cleaning system |
| CN108223203A (en) * | 2016-12-21 | 2018-06-29 | 曼狄赛尔公司德国曼柴油机欧洲股份公司的联营公司 | Large-sized turbo-charging two-stroke compression ignition engine with exhaust gas recirculatioon |
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| CN104854338A (en) * | 2012-12-28 | 2015-08-19 | 三菱重工业株式会社 | Internal combustion engine, ship, and method for operating internal combustion engine |
| CN104854338B (en) * | 2012-12-28 | 2018-08-03 | 三菱重工业株式会社 | The operation method of internal combustion engine, ship and internal combustion engine |
| CN103967594A (en) * | 2013-05-21 | 2014-08-06 | 曼柴油机欧洲股份公司曼柴油机德国分公司 | Large two-stroke diesel engine and method for obtaining characteristics of a butterfly valve in the large two-stroke diesel engine |
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| CN104564435B (en) * | 2013-10-29 | 2018-10-09 | 曼柴油机欧洲股份公司曼柴油机德国分公司 | The turbocharged two-stroke internal combustion engine of large-sized low-speed operation |
| CN106050373A (en) * | 2015-06-19 | 2016-10-26 | 曼柴油机欧洲股份公司曼柴油机德国分公司 | Large-size two-stroke turbocharging compression ignition explosive motor with waste gas cleaning system |
| CN108223203A (en) * | 2016-12-21 | 2018-06-29 | 曼狄赛尔公司德国曼柴油机欧洲股份公司的联营公司 | Large-sized turbo-charging two-stroke compression ignition engine with exhaust gas recirculatioon |
Also Published As
| Publication number | Publication date |
|---|---|
| DK177388B1 (en) | 2013-03-04 |
| KR101274016B1 (en) | 2013-06-12 |
| DK201100060A (en) | 2012-08-01 |
| CN102619615B (en) | 2015-04-08 |
| JP2012159079A (en) | 2012-08-23 |
| JP5661658B2 (en) | 2015-01-28 |
| KR20120088590A (en) | 2012-08-08 |
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