CN108223203A - Large-sized turbo-charging two-stroke compression ignition engine with exhaust gas recirculatioon - Google Patents
Large-sized turbo-charging two-stroke compression ignition engine with exhaust gas recirculatioon Download PDFInfo
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- CN108223203A CN108223203A CN201711374494.XA CN201711374494A CN108223203A CN 108223203 A CN108223203 A CN 108223203A CN 201711374494 A CN201711374494 A CN 201711374494A CN 108223203 A CN108223203 A CN 108223203A
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- scavenging
- boiler
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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
- F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
- F02B25/02—Engines characterised by using fresh charge for scavenging cylinders using unidirectional scavenging
- F02B25/04—Engines having ports both in cylinder head and in cylinder wall near bottom of piston stroke
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/02—EGR systems specially adapted for supercharged engines
- F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
- F02M26/05—High pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust system upstream of the turbine and reintroduced into the intake system downstream of the compressor
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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
- F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
- F02B25/02—Engines characterised by using fresh charge for scavenging cylinders using unidirectional scavenging
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/02—EGR systems specially adapted for supercharged engines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
- F02M26/23—Layout, e.g. schematics
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
- F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
- F02M26/30—Connections of coolers to other devices, e.g. to valves, heaters, compressors or filters; Coolers characterised by their location on the engine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/42—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders
-
- 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
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M2026/001—Arrangements; Control features; Details
-
- 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
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
- Exhaust-Gas Circulating Devices (AREA)
Abstract
One kind has the large-sized turbo-charging two-stroke compression ignition engine of crosshead (23), including：Multiple cylinders (1), each cylinder (1) is equipped with scavenging port (19) and air bleeding valve (4)；Exhaust receiver (3)；Turbocharger (5)；Discharge duct (18)；Turbocharger compressor (9)；Scavenging pipeline (11)；For a part of exhaust gas recirculatioon to be returned to the exhaust gas recirculatioon pipeline (30) of cylinder (1), exhaust gas recirculatioon pipeline (30) is including for forcing the exhaust of recycling to return to the air blower (32) of cylinder (1) or compressor and for by the way that scavenging pipeline (11) of a part of hot scavenging from scavenging cooler (22) upstream is transported to the turbine (6) of turbocharger (5) and around the cylinder by-pass line (40) of cylinder (1) and boiler (36).Engine is configured at least first part of exhaust being carried through boiler (36) from cylinder (1).
Description
Technical field
The present invention relates to a kind of crosshead type large turbocharging two-stroke compression ignition internal combustions with emission control system
Machine.
Background technology
Crosshead type large two-stroke compression ignition engine is commonly used in the propulsion system of large ship or as power plant
Engine.It already and will be increasingly more difficult to achieve emission request, especially with regard to nitrogen oxides (NOx) horizontal.
Exhaust gas recirculatioon is that known assistance internal combustion engine reduces NOxMeasure.
If without using exhaust gas recycling system, these emission requests such as International Maritime Organization (IMO) Section II grade, especially
Be Section III grade discharge standard it is implacable.Preferably, exhaust gas recirculation rate is variable.
DK 177388 discloses a kind of large-sized two-stroke compression ignition engine of preamble according to claim 1.
The energy resource system being made of engine cylinder and turbocharger must be balanced carefully under all operating conditions.
If uneven, become unacceptable and/or turbocharger compression for the boundary condition of the cyclic process in cylinder
Machine enters surge or chokes.Compressor characteristics determine whether turbocharger runs close under its maximal efficiency, but have
Enough surge margins are to ensure compressor stability.Surge margin is needed, because turbocharger operation point may be
Certain in a flash, for example, engine load quickly reduce during or in abnormal cases, the asthma close in compressor characteristics line chart
Shake line.
Has the operational mode that recycles with and without high pressure gas and with fixed whirlpool when engine must provide
When taking turns intensifier component, " balance " becomes significantly more complicated.Reason is the row from exhaust receiver to scavenging receiver
Gas recycling route includes a cooler, and larger numbers of energy is removed from energy system.This energy " loss " is in appearance
Device central cooler.When exhaust gas recirculatioon is run without in the case of, this energy removal is not present.Therefore, when from row
When gas recycling operation is switched to non-exhaust gas recirculatioon operation, the balance in energy system is significantly different, and vice versa.
At present, it is built by using the cylinder bypass from compressor outlet to turbine air inlet and turbine bypass
Vertical " balance ".The control strategy of these bypasses is designed to compensate for the energy removal under each operational mode.When not being vented
When being run in the case of recycling, turbine bypass reduces the energy for being transported to turbine, when in the feelings with exhaust gas recirculatioon
When being run under condition, cylinder bypass increases the energy for being transported to turbine.In short, these measures compensate for exhaust gas recirculation line road
It works or inoperative effect, while reduces the scavenging for flowing through cylinder.
Therefore, there is a kind of demand for turbo charged two-stroke compression ignition engine, wherein using bypass
In the case that demand is minimized with Minimal energy loss in exhaust gas recirculation cooler, turbocharger is with and without exhaust
It runs in the case of recycling and all balances.
Invention content
In view of the foregoing, the purpose of the present invention is to provide it is a kind of overcome or at least reduce the above problem have cross
The large-sized two-stroke compression ignition engine of head.
Foregoing and other purpose is realized by the feature of independent claims.Further form of implementation is from appurtenance
It is it is required that apparent in the description and the appended drawings.
According in a first aspect, provide a kind of large-sized turbo-charging two-stroke compression ignition engine with crosshead, wrap
It includes：Multiple cylinders, each cylinder are equipped with scavenging port and air bleeding valve；The exhaust that cylinder is connected to by the air bleeding valve of each cylinder connects
Receive device；One turbocharger；The gas outlet of exhaust receiver is connected to the discharge duct of the turbine of turbocharger；By whirlpool
The turbocharger compressor of the turbocharger of turbine driving；The gas outlet of turbocharger compressor is connected to scavenging to connect
Receive device air inlet scavenging pipeline, scavenging pipeline include a scavenging cooler, scavenging receiver via each cylinder scavenging
Mouth is connected to cylinder；For a part of exhaust gas recirculatioon to be returned to the exhaust gas recirculatioon pipeline of cylinder, exhaust gas recirculatioon pipeline packet
Include for force the exhaust of recycling return to cylinder air blower or compressor and for by by a part of hot scavenging from sweeping
The scavenging pipeline of Gas Cooler upstream be transported to the turbine of turbocharger and around the cylinder by-pass line and boiler of cylinder,
Its feature is that engine is configured at least first part of exhaust being carried through boiler (36), and start from cylinder
Machine has at least two operational modes, and engine is configured in the first operational mode, will be carried through boiler from cylinder
(36) first part of exhaust returns to cylinder from boiler (36) across exhaust gas recirculatioon pipeline and sweeps a part of heat
Gas is transported to turbine, and engine is configured in second by bypass duct from the scavenging pipeline of scavenging cooler upstream
Operational mode, to prevent the flowing across exhaust gas recirculatioon pipeline, to prevent to wear across the flowing of bypass duct and by conveying
The first part's exhaust for crossing boiler is transported to turbine from boiler.
By include one exhaust gas recirculatioon operation and non-exhaust gas recirculatioon operation in from exhaust remove energy boiler,
Energy system is balanced in two kinds of operational modes, and is run without using turbine bypass for non-exhaust gas recirculatioon.On the contrary, it makes
With a boiler, i.e., high-pressure boiler in parallel with exhaust receiver, to remove energy from system.One is gas the advantages of notable
Temperature and density are high, lead to extremely efficient heat exchanger or high-pressure boiler, compared to conventional boiler, in turbine gas outlet
Afterwards, useful steam is provided with significantly lower size and cost.When the engine be used to always need on the ship of steam,
This is particularly useful.
In the first possible embodiment of first aspect, engine is configured to the second part of exhaust from cylinder
It is transported to turbine and without boiler.
In the second possible embodiment of first aspect, engine includes the auxiliary air blast being located in scavenging pipeline
Machine, and engine is configured as operation auxiliary blower to maximize the steam production of boiler.
In the possible embodiment of third of first aspect, the first part of exhaust and the second part of exhaust together structure
Into total exhaust from cylinder.
In the 4th possible embodiment of first aspect, engine includes the boiler tubing with boiler, boiler tube
The air inlet in road is connected to exhaust receiver or discharge duct in first position.
In the 5th possible embodiment of first aspect, the gas outlet of boiler tubing is connected to exhaust in the third place
Recirculation conduit, the third place are preferably located in the upstream of air blower or compressor.
In the 6th possible embodiment of first aspect, the gas outlet of boiler tubing is the second of first position downstream
Discharge duct is connected at position.
In the 7th possible embodiment of first aspect, engine includes be located in exhaust gas recirculatioon pipeline first
Control valve.
In the 8th possible embodiment of first aspect, engine includes the be located in bypass duct second control
Valve.
In the 9th possible embodiment of first aspect, engine includes third control valve, the third control valve position
Between the third place and exhaust gas recirculatioon pipeline are connected to the position of discharge duct.
In the tenth possible embodiment of first aspect, exhaust gas recirculatioon pipeline includes exhaust gas recirculation cooler.
In the 11st possible embodiment of first aspect, balanced to control boiler according to desired turbocharger
The distribution of exhaust stream between discharge duct.
In the 12nd possible embodiment of first aspect, boiler is integrated into exhaust receiver.
In the 13rd possible embodiment of first aspect, exhaust receiver has comes from each cylinder for balanced
Exhaust pressure pulse large volume, to provide substantially invariable pressure at the gas outlet of exhaust receiver.
In the 14th possible embodiment of first aspect, engine further includes auxiliary associated with scavenging pipeline
Air blower, for the assisted turbocharger under the conditions of related load.
In the 15th possible embodiment of first aspect, scavenging receiver has to reduce by flowing into each vapour
The large volume of pressure oscillation caused by the air-flow of cylinder.
In the 16th possible embodiment of first aspect, engine is configured in all engine loadings level
Lower operation auxiliary blower, so as to maximize the steam production of boiler.Therefore, it is possible to reduce or avoid increasing using oil burner etc.
Add the steam production in the low-load region of sustainer.
In the 17th possible embodiment of first aspect, engine is not provided with steam copper in the low-pressure side of turbine
Stove.
These and other aspects of the invention will become apparent from the embodiments described below.
Description of the drawings
In the part in detailed below of the disclosure, the exemplary embodiment shown in refer to the attached drawing is explained in greater detail
The present invention, wherein：
Fig. 1 be show the compression-ignited turbocharged engine of large-sized two-stroke accoding to exemplary embodiment front end and one
The stereogram of side；
Fig. 2 is the rear end of the engine of Fig. 1 and the stereogram of another cross side；
Fig. 3 is the schematic diagram of the engine according to Fig. 1 with intake and exhaust system；
Fig. 4 is the III level engine of the prior art, the schematic diagram of the intake and exhaust system of the prior art；
Fig. 5 is in the case that the III level engine of the prior art in Fig. 4 has exhaust gas recirculatioon under III level pattern
The schematic diagram of operation；
Fig. 6 is the II stage motors of the prior art in Fig. 4 under II grades of patterns in the case of i.e. no exhaust gas recirculatioon
The schematic diagram of operation；
Fig. 7 is the signal of the exemplary embodiment of the III level engine according to the present invention with intake and exhaust system
Figure；
Fig. 8 is that the III level engine of Fig. 7 has the schematic diagram run in the case of exhaust gas recirculatioon under III level pattern；
Fig. 9 is the signal that the III level engine of Fig. 7 is run under II grades of patterns in the case of i.e. no exhaust gas recirculatioon
Figure；With
Figure 10 to 12 is another exemplary reality of the III level engine according to the present invention with intake and exhaust system
Apply example.
Specific embodiment
In the following detailed description, will large-sized two-stroke compression ignition engine be described by exemplary embodiment.Fig. 1
The bent axle 22 having and the large-sized low-speed turbocharging two-stroke compression ignition internal combustion of crosshead 23 are shown in stereogram with Fig. 2
Machine.Fig. 3 shows the schematic diagram of the engine with intake and exhaust system.In this exemplary embodiment, engine has
The cylinder 1 of six alinements.There are five large-sized turbo-charging two-stroke diesel engine usually tools to 16 alinements
Cylinder, these cylinders support by cylinder stent 25, and cylinder stent 25 is supported by entablature 24.Engine can be used, for example, as
The sustainer of foreign-going ship or the stationary engine as operation generator in power station.The gross output of engine is for example
It can be in the range of 5000-110000kW.
Engine is diesel oil (compression-ignited) engine of two-stroke single stream type, is had at the lower area of cylinder 1
Piston control port ring form scavenging port 19 and the air bleeding valve 4 at the top of cylinder 1.Therefore, combustion chamber
Interior flowing is from bottom to top always, therefore engine is so-called single current.Scavenging is transferred to respectively from scavenging receiver 2
The scavenging port 19 of cylinder 1.Reciprocating-piston 21 in cylinder 1 compresses scavenging, fuel via 2 be arranged in cylinder cover 26 or
3 fuel valves 27 spray.With after-combustion and generate exhaust.When air bleeding valve 4 is opened, it is vented by associated with corresponding cylinder 1
Exhaust pipe 20 flow into exhaust receiver 3, and be advanced through the turbine 6 that discharge duct 18 flow to turbocharger 5, be vented
It is flowed away by exhaust pipe 7 from the turbine 6 of turbocharger 5.By axis 8, turbine 6 drives the pressure supplied via air inlet 10
Contracting machine 9.
The scavenging of pressurization is transported to the scavenging pipeline 11 for leading to scavenging receiver 2 by compressor 9.Scavenging warp in pipeline 11
Cross the intercooler 12 for cooling down scavenging.Cooled scavenging is transferred to via the auxiliary blower 16 that motor 17 drives
Charging air receiver 2, the auxiliary blower 16 pressurize under low-load or part-load condition to pressurized air.Higher negative
Under load, turbocharger compressor 9 conveys the scavenging of enough compressions, and then auxiliary blower 16 can be other via check-valves 15
Road.
Exhaust receiver 3 is large-scale elongated column shape container, parallel and extremely set close to the top of the exhaust casing 1.
Exhaust receiver 3 has big volume so that exhaust receiver can come from each cylinder 1 in the opening equilibrium of air bleeding valve 4
Exhaust it is periodical flow into caused by pressure pulse.The proportionality action of exhaust receiver 3 provides the gas outlet of exhaust receiver 3
The substantially invariable pressure at place.Constant pressure at the gas outlet of exhaust receiver 3 is advantageous, and is rushed because being used for large size two
One or more of journey diesel engine exhaust-gas-driven turbo charger 5 benefits from constant supply pressure.
Exhaust (can have multiple from exhaust receiver 3 by the turbine 6 that discharge duct 18 is directed to turbocharger 5
Turbocharger 5 and can have multiple exhaust receivers 3).Exhaust is configured into the air in 6 downstream of turbine.Turbine
Booster 5 is constant pressure turbocharger, that is, turbocharger 5 is not configured for running with the pressure pulse in exhaust.Whirlpool
Taking turns booster 5 has axial-flow type or radial-flow turbine, and be configured for being up to about 500 to 550 DEG C of delivery temperature.
Turbocharger 5 further includes the compressor 9 driven by turbine 6 via axis 8.Compressor 9 is connected to air inlet 10.
High pressure scavenging is transported to scavenging receiver 2 by compressor 9 by the scavenging pipeline 11 comprising scavenging cooler 12.
Scavenging receiver 2 is a big elongated column shape container, it is parallel to and extremely close to the bottom of the exhaust casing 1
Position.Scavenging receiver 2 has big volume, make scavenging receiver 2 can compensate for opening in scavenging port 19 from scavenging to
The pressure that the periodical outflow of each cylinder 1 is caused declines.The compensating effect of scavenging receiver 2 carries in scavenging receiver 2
For substantially invariable pressure so that each cylinder 1 has essentially identical scavenging pressure.What is needed in scavenging receiver 2 is constant
Pressure, because being used for one or more of large-sized two-stroke diesel engine turbocharger 5 with constant supply pressure
It runs and transmits constant supply pressure, that is, can be used for without pressure pulse to each 1 scavenging of cylinder.
The engine of the prior art is equipped with the exhaust gas recycling system shown in Fig. 4.Exhaust gas recycling system is configured
Scavenging is delivered by a part for the exhaust from cylinder 1, for example, for reducing ignition temperature and thereby reducing NOxRow
It puts.Exhaust gas recycling system can be activity or what inactive either a kind of exhaust gas recirculation rate with variation was run is
System.Exhaust gas recycling system includes extending to scavenging pipeline 11 or scavenging receiver 2 from exhaust receiver 3 or discharge duct 18
Pipeline 30.Alternatively, exhaust can be directly acquired via valve or port (not shown) from cylinder 1.
It is shown in Fig. 4 in the prior art, discharge duct 18 is connected to scavenging pipeline 11 by exhaust gas recirculatioon pipeline 30.Row
Gas recirculation conduit 30 is branched off at the position in 3 downstream of exhaust receiver from discharge duct 18, and in vent gas cooler
12 downstream or upstream position are connected to scavenging pipeline 11.
Exhaust gas recirculatioon pipeline 30 includes various parts.The cleaning that these components include such as washer or filter is set
It is standby, 32 and first control valve 34 of (being driven by electro-motor or hydraulic motor) suction blower.
32 and first control valve 34 of air blower, that is, the component of exhaust gas recirculatioon pipeline 30 is connected to an electronic control unit
(not shown).Electronic control unit controls the work of exhaust gas recycling system based on the input of operating condition and/or operating personnel
It is dynamic.Electronic control unit is configured to start and deactivate exhaust gas recycling system, and changeably control if necessary
Ratio between exhaust gas recirculation rate processed, i.e. air and exhaust.
The engine of the prior art is equipped with cylinder bypass duct 40, and scavenging pipeline 11 is connected to discharge duct 18.Vapour
One end of cylinder bypass duct 40 is connected to scavenging pipeline at the position of the downstream of compressor 9 and the upstream of scavenging cooler 12
11.The other end of cylinder bypass duct 40 is connected to the downstream position of the position of discharge duct 18 in exhaust gas recirculatioon pipeline 30
It is connect with the upstream position of the air inlet of turbine 6 with discharge duct 18.It is also along other link positions of discharge duct 18
Feasible.
Cylinder bypass duct 40 includes the second control valve 41, which is adjusted from scavenging flow path 11 to exhaust
The flowing of the scavenging of pipeline 18, for example, under the instruction of electronic control unit or operating personnel.Second control valve 41 is to passing through valve
Flow have variable and controllable limited degree.
Optionally, the second control valve 4 is by electronic control unit or the ON/OFF type controlled by operating personnel.In the reality
It applies in example, electronic control unit is configured to open the second control valve 41 when exhaust gas recycling system activity, and be configured
Into closing the second control valve 41 when exhaust gas recycling system is inactive.
Exhaust gas recycling system may be inactive due to various reasons.One of reason may be exhaust gas recirculatioon
The defects of system or failure.Another reason for exhaust gas recycling system is inactive may be to be in opposite in order to optimize engine
In two level NOxThe opportunity of the fuel consumption of emission level.Exhaust gas recirculation rate can be with for example, become between 0% and about 45%
Change.
When turbocharger 5 is not matched preferably due to surge or chokes with engine, operation is bad or completely not
Operation.In typical compressor characteristics, pressure ratio is plotted as the function of mass flowrate and rotary speed, and efficiency curve
It is applied.When turbocharger 5 is matched to engine, the purpose is to the operating point of engine is disposed proximate to or most
In efficient curve ranges, but there is safety margin relative to surge line.
When exhaust gas recycling system becomes inactive state from active state, the service condition of turbocharger is substantially
Change.In the case of exhaust gas recycling system activity, turbocharger 5 is to be matched with engine operation (that is, in exhaust again
Cycling rate is for example about between 20% and 45% and with being run in the case of 5 matched well of turbocharger).When exhaust again
The circulatory system fail when, in the case of no countermeasure, turbocharger 5 will not matched well, because of scavenging pressure and stream
Amount will increase about 25%, this is unacceptable under high engine load and may lead to gripping for turbocharger
Stream, hypervelocity and inefficiency.
Match the exhaust gas recirculation engines for meeting IMO III level emission regulations or for being followed again in no exhaust
The turbocharger 5 of II stage motors run in the case of ring (or a small amount of exhaust gas recirculatioon) is in (the asthma of compressor stability
Shake nargin) a kind of compromise between compressor/turbocharger efficiency/fuel consumption of engine 1.If turbocharger
Compressor matched when being run in the case of no exhaust gas recirculatioon with preferred plan, then need not be reduced in exhaust gas recirculatioon
There are big surge margins during by the flow of compressor 9 (engine operation point being moved towards surge line).It is swept when uncompromising
When switching between these two modes in the case of atmospheric pressure (boost pressure) and engine efficiency, traditional turbocharger or
The turbocharger in variable turbine region does not have the range of flow needed for processing flowing variation.
In embodiment, the compressor 9 of turbocharger 5 is matched for exhaust gas recirculatioon operation and opens cylinder bypass
Flow path 40.When being switched to non-exhaust gas recirculation mode, cylinder bypass flow path 40 closes to ensure flow and sweep
The growth of atmospheric pressure is reduced to avoid 9 chokes of compressor of turbocharger 5, and obtains best in compressor characteristics (figure)
Service condition.Another effect is that relatively low absolute exhaust gas recirculation mass flow is needed to realize expected NOxDecline, because
When cylinder bypass flow path 40 is opened, reduced by the air mass flow of cylinder 1.Another effect is less due to needing
Suction blower power and circulating exhaust amount, so the capacity of exhaust gas recycling system in itself can be reduced.Therefore, electronics
Control unit can be configured as the aperture for increasing the second control valve 41 with the increase of exhaust gas recirculation rate, and vice versa,
Under all exhaust gas recirculation rates run therewith in engine so as to turbocharger 5 with engine best match.
The negative effect for flowing through the cylinder bypass of bypass duct 40 is that the thermic load on engine increases, which increases
It is caused by being reduced by the amount of the scavenging of cylinder 1.
Turbine bypass pipeline 50 is provided for during the operation of no exhaust gas recirculatioon, blowing from discharge duct 18
Except excessive exhaust.It is controlled by the flow of turbine bypass pipeline 50 by the 5th control valve 51.Steam copper in discharge duct 7
Heat in gas outlet from turbine and the exhaust from turbine bypass 50 is converted into steam by stove 52.
Fig. 5 shows the operational mode of the engine in Fig. 4 during the operation for having exhaust gas recirculatioon, the first control valve 34
It is all opened with the second control valve 41.For illustrative purposes, control valve is not shown in Fig. 5.
During the operation of no exhaust gas recirculatioon, the first control valve 34 and the second control valve 41 are all closed.The operation mould
Formula is shown in FIG. 6.For illustrative purposes, control valve is not shown in figure 6.In the operational mode of no exhaust gas recirculatioon
In, some exhausts from cylinder 1 need to bypass turbine 6 to balance turbocharger 5.For this purpose, 51 quilt of the 5th control valve
It opens so that a part for the exhaust from cylinder 1 bypasses turbine 6 via turbine bypass pipeline 50.
Fig. 7 shows the first exemplary embodiment of engine.In addition to turbine bypass pipeline 50,51 He of the 5th control valve
Other than EGR gas cooler 31, engine includes all features of prior art engine according to this embodiment.In reality
It applies in example, engine does not have or do not need at least the low-pressure side in turbine 6 with steam boiler 52, remains able to simultaneously
Enough steam is generated, and at the same time remaining able to fully extract ceiling capacity from the fuel of burning.
Engine is alternatively provided with high-pressure boiler 36 according to this embodiment.High-pressure boiler 36 generates steam, the steaming
Vapour can be used by the various consumer joined with engine or its environmental correclation, for example, installing the ship of the engine.High-pressure boiler
36 receive the first part of the total flow of exhaust by boiler tubing 35 from cylinder 1.Boiler tubing 35 includes the 4th control valve 38.
In this embodiment, the air inlet of boiler tubing 35 is connected to exhaust receiver 3, and the outlet of boiler tubing 35
Mouth is connected to exhaust gas recirculatioon pipeline 30.Exhaust cycle pipeline 30 is provided with third control valve 37.
The control valve can be manually operated or be connected to electronic control unit (not shown).
Engine is run in the case where there is exhaust gas recirculatioon in the first mode of operation.In this mode, third control
Valve 37 processed is closed, and the first control valve 34 is opened, and the second control valve 41 is opened.First mode is shown in Fig. 8, illustrates only activity
Pipeline, and control valve is not shown so that diagram be more readily understood.In the first mode, exhaust from cylinder 1
First part is preferably cooled down by boiler tubing 35, high-pressure boiler 36, exhaust gas recirculatioon pipeline 30 and air blower 32 in scavenging
The upstream position (optionally, the exhaust of recycling can be delivered directly to scavenging receiver 2) of device 12 is transported to scavenging
Pipeline 11.
Hot scavenging from scavenging pipeline 11 via bypass duct 40 by being transmitted to discharge duct 18 and around cylinder 1.
Engine is run in the case of no exhaust gas recirculatioon in the second mode of operation.In this mode, third
Control valve 37 is opened, and the first control valve 34 is closed, and the second control valve 41 is closed.The second way is as shown in figure 9, only shown activity
Control valve is not shown so that diagram should be readily appreciated that in pipeline.In a second mode, the first part of the exhaust from cylinder 1 leads to
Cross boiler tubing 35, high-pressure boiler 36, open third control valve 37, be transported to discharge duct 18 with from cylinder 1
Second (residue) of exhaust stream is partly combined.Therefore, whole exhausts from cylinder 1 are transported to turbine 6.However, with
The prior art is compared, and the part in energy is eliminated due to high-pressure boiler 36, and the removal of energy is partially converted into steam,
Therefore it is relatively low towards the energy value of compressor 6 in the total flow of the exhaust of conveying.Therefore, turbocharger 5 and engine are perfect
Ground balances, although turbine 6 receives whole exhaust streams from cylinder 1.
A part for the total flow of exhaust from cylinder is transported to the air inlet of turbine 6, it is preferable that either exists
Operation is still run in the case of no exhaust gas recirculatioon in the case of having exhaust gas recirculatioon.
Figure 10 shows the second embodiment essentially identical with first embodiment, in addition to exhaust gas recirculatioon pipeline 30 is provided with
Except EGR gas cooler (washer) 39.
Figure 11 shows the 3rd embodiment essentially identical with first embodiment, in addition to the air inlet of boiler tubing 35 is direct
The gas outlet for being connected to cylinder and boiler tubing is connected to except discharge duct 18.
Figure 12 shows the fourth embodiment essentially identical with first embodiment, in addition to the air inlet of boiler tubing 35 connects
To except discharge duct 18.
In embodiment, engine is configured under all engine load levels (low, medium and high engine is horizontal)
Run auxiliary blower 16, it is therefore an objective to maximize the steam production of boiler 36.Therefore, it is possible to reduce or avoid using fuel oil
Burner etc. increases the steam production in the low-load region of sustainer.
In embodiment (not shown), high-pressure boiler 36 is arranged in exhaust receiver 3.This substantially reduces pass through exhaust
Pressure and be applied to the power on boiler component.By the way that high-pressure boiler 36 is integrated into exhaust receiver so that less sky
Between used and engine will be compacter.
It has been combined various embodiments herein and describes the present invention.However, those skilled in the art protect in practice requirement
During the invention of shield, by studying attached drawing, disclosure and appended claims, it is possible to understand that and realize to the disclosed embodiments
Other modifications.In the claims, word " comprising " is not excluded for other elements or step, and indefinite article " one (a) " or
" a kind of (an) " is not excluded for multiple.The fact that describe certain measures in mutually different dependent claims is not offered as
The combination of these measures cannot be advantageously used.
The reference numeral used in claim is not necessarily to be construed as limitation range.
Claims (14)
1. one kind has the large-sized turbo-charging two-stroke compression ignition engine of crosshead (23), including：
Multiple cylinders (1), each cylinder (1) is equipped with scavenging port (19) and air bleeding valve (4)；
Exhaust receiver (3), the exhaust receiver (3) are connected to the cylinder via the air bleeding valve (4) of each cylinder
(1)；
Turbocharger (5)；
The gas outlet of the exhaust receiver (12) is connected to the turbine and increased by discharge duct (18), the discharge duct (18)
The turbine (6) of depressor (5)；
The turbocharger compressor (9) of the turbocharger (5), the turbocharger compressor (9) is by the turbine
Machine (17) drives；
The gas outlet of the turbocharger compressor (9) is connected to scavenging by scavenging pipeline (11), the scavenging pipeline (11)
The air inlet of receiver (2), the scavenging pipeline (11) include a scavenging cooler (12), the scavenging receiver (2) via
The scavenging port (19) of each cylinder (1) is connected to the cylinder (1)；
Exhaust gas recirculatioon pipeline (30), the exhaust gas recirculatioon pipeline (30) by a part of exhaust gas recirculatioon for returning to the vapour
Cylinder (1), the exhaust gas recirculatioon pipeline (30) include：Exhaust for forcing recycling returns to the air blower of the cylinder (1)
(32) or compressor and for passing through the scavenging pipeline by a part of hot scavenging from the scavenging cooler (22) upstream
(11) be transported to the turbine (6) of the turbocharger (5) and around the cylinder bypass duct (40) and pot of cylinder (1)
Stove (36)；
It is characterized in that, the engine is configured to wear at least first part of the exhaust from the cylinder (1) conveying
The boiler is crossed, and the engine has at least two operational modes, the engine is configured in the first operation mould
Formula will be carried through the first part of the exhaust of the boiler (36) from the cylinder (1), from the boiler
(36) it is delivered back into the cylinder (1) across the exhaust gas recirculatioon pipeline (30) and a part of hot scavenging is passed through into the side
Road pipeline (40) is transported to the turbine (6) from the scavenging pipeline (11) of the scavenging cooler (12) upstream, and
The engine is configured in the second operational mode, to prevent the flowing across the exhaust gas recirculatioon pipeline (30), with resistance
Only across the flowing of the bypass duct (40) and the first part exhaust of the boiler (36) will be carried through from institute
It states boiler (36) and is transported to the turbine (6).
2. engine according to claim 1, wherein, the engine be configured to by the second part of the exhaust from
The cylinder (1) is transported to the turbine (6) and without the boiler (36).
3. engine according to claim 1 or 2 further includes the auxiliary blower in the scavenging pipeline (11)
(16), and wherein described engine is configured as running the auxiliary blower (16) to maximize the boiler (36)
Steam production.
4. engine according to any one of claim 1 to 3, wherein, the first part of the exhaust and described
The second part of exhaust forms total exhaust from the cylinder (1) together.
5. engine according to any one of claim 1 to 4, the engine includes the pot with the boiler (36)
Boiler tube road (35), the air inlet of the boiler tubing (35) are connected to the exhaust receiver (3) or the row in first position
Feed channel (18).
6. engine according to any one of claim 1 to 5, wherein, the gas outlet of the boiler tubing (35) is
Three positions are connected to the exhaust gas recirculatioon pipeline (30), and the third place is preferably located in the air blower (32) or compression
The upstream of machine.
7. engine according to claim 5 or 6, wherein, the gas outlet of the boiler tubing (35) is at described first
The second place for putting downstream is connected to the discharge duct (18).
8. engine according to any one of claim 1 to 7, the engine includes being located at the exhaust gas recirculatioon pipe
The first control valve (34) in road (30).
9. engine according to any one of claim 1 to 8, the engine includes being located at the bypass duct (40)
In the second control valve (41).
10. according to the engine described in any one of claim 6,8 and 9, the engine includes third control valve (37), institute
It states third control valve (37) and is connected to the discharge duct positioned at the third place and the exhaust gas recirculatioon pipeline (30)
(18) between position.
11. engine according to any one of claim 1 to 10, wherein, the exhaust gas recirculatioon pipeline (30) includes
Exhaust gas recirculation cooler (39).
12. engine according to any one of claim 1 to 11, wherein, when running in the second mode, root
The distribution to control the exhaust stream between the boiler (36) and the discharge duct (18) is balanced according to desired turbocharger.
13. engine according to any one of claim 1 to 12, wherein, the boiler (36) is integrated into the row
In gas receiver (3).
14. the engine according to any one of claim 3 to 13, the engine is configured to bear in all engines
The horizontal lower operation auxiliary blower (16) is carried, so as to maximize the steam production of the boiler (36).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DKPA201671013A DK179313B1 (en) | 2016-12-21 | 2016-12-21 | Large turbocharged two-stroke compression-igniting engine with exhaust gas recirculation |
| DKPA201671013 | 2016-12-21 |
Publications (2)
| Publication Number | Publication Date |
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| CN108223203A true CN108223203A (en) | 2018-06-29 |
| CN108223203B CN108223203B (en) | 2019-12-03 |
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| CN201711374494.XA Active CN108223203B (en) | 2016-12-21 | 2017-12-19 | Large-sized turbo-charging two-stroke compression ignition engine with exhaust gas recirculatioon |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP6595571B2 (en) |
| KR (1) | KR102019931B1 (en) |
| CN (1) | CN108223203B (en) |
| DK (1) | DK179313B1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113482805A (en) * | 2021-07-30 | 2021-10-08 | 东风商用车有限公司 | Hierarchical type double-circulation cooling system of two-stage supercharged engine |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DK201670345A1 (en) * | 2016-05-24 | 2017-12-11 | Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland | Method for operating a two-stroke engine system |
| KR102587329B1 (en) | 2018-12-10 | 2023-10-10 | 한화에어로스페이스 주식회사 | An auxiliary power unit for reducing the flow loss of the gas |
| JP7244382B2 (en) * | 2019-07-25 | 2023-03-22 | 川崎重工業株式会社 | hydrogen gas fuel engine |
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| CN113482805B (en) * | 2021-07-30 | 2022-05-03 | 东风商用车有限公司 | Hierarchical type double-circulation cooling system of two-stage supercharged engine |
Also Published As
| Publication number | Publication date |
|---|---|
| DK201671013A1 (en) | 2018-04-30 |
| JP2018100669A (en) | 2018-06-28 |
| KR20180072552A (en) | 2018-06-29 |
| KR102019931B1 (en) | 2019-11-04 |
| JP6595571B2 (en) | 2019-10-23 |
| CN108223203B (en) | 2019-12-03 |
| DK179313B1 (en) | 2018-04-30 |
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