CN108223203B - 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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- CN108223203B CN108223203B CN201711374494.XA CN201711374494A CN108223203B CN 108223203 B CN108223203 B CN 108223203B CN 201711374494 A CN201711374494 A CN 201711374494A CN 108223203 B CN108223203 B CN 108223203B
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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
-
- 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
-
- 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
Abstract
One kind having the large-sized turbo-charging two-stroke compression ignition engine of crosshead (23), comprising: multiple cylinders (1), each cylinder (1) are equipped with scavenging port (19) and exhaust valve (4)；Exhaust receiver (3)；Turbocharger (5)；Exhaust pipe (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) includes the air blower (32) or compressor for forcing the exhaust of recycling to return to cylinder (1), and cylinder by-pass line (40) and boiler (36) for bypassing cylinder (1) and a part of hot scavenging to be transported to turbine (6) of turbocharger (5) from the scavenging pipeline (11) of scavenging cooler (22) upstream.At least first part that engine is configured to be vented is 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 combustion with emission control system
Machine.
Background technique
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 not using exhaust gas recycling system, these emission requests such as International Maritime Organization (IMO) Section II grade, especially
It is Section III grade discharge standard 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, the boundary condition for the cyclic process in cylinder becomes unacceptable and/or turbocharger compression
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, during engine load quickly reduces, or in abnormal cases, the asthma close in compressor characteristics line chart
Shake line.
When engine must provide the operational mode having with and without high pressure gas recycling and have fixed whirlpool
When taking turns intensifier component, " balance " becomes significantly more complicated.Reason is the row from exhaust receiver to scavenging receiver
It includes a cooler that gas, which recycles route, and larger numbers of energy is removed from energy system.This energy " loss " Yu Rong
Device central cooler.Exhaust gas recirculatioon without in the case where run when, the removal of this energy is not present.Therefore, when from row
When gas recycling operation is switched to non-exhaust gas recirculatioon operation, the significant ground of balance in energy system is different, and vice versa.
Currently, by using from compressor outlet to turbine air inlet cylinder bypass and turbine bypass build
Vertical " balance ".The control strategy of these bypasses is designed to compensate for the removal of the energy under each operational mode.When not being vented
When running in the case where recycling, turbine bypass reduces the energy for being transported to turbine, when in the feelings with exhaust gas recirculatioon
When running 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 reducing 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 where recycling and all balances.
Summary of the invention
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 passes through 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
Include: multiple cylinders, each cylinder are equipped with scavenging port and exhaust valve；It is connect by the exhaust that the exhaust valve of each cylinder is connected to cylinder
Receive device；One turbocharger；The gas outlet of exhaust receiver is connected to the exhaust pipe 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 the air blower or compressor for forcing the exhaust of recycling to return to cylinder, and for by by a part of hot scavenging from sweeping
The scavenging pipeline of Gas Cooler upstream is transported to the turbine of turbocharger and bypasses the cylinder by-pass line and boiler of cylinder,
It is characterized in that at least first part that engine is configured to be vented is carried through boiler (36) from cylinder, and start
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 across exhaust gas recirculatioon pipeline from boiler (36) and sweeps a part of heat
Gas is transported to turbine from the scavenging pipeline of scavenging cooler upstream by bypass duct, and engine is configured in second
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 for crossing boiler, which is vented from boiler, is transported to turbine.
By removing the boiler of energy from exhaust in exhaust gas recirculatioon operation and non-exhaust gas recirculatioon operation including one,
Energy system is balanced in two kinds of operational modes, and runs without using turbine bypass for non-exhaust gas recirculatioon.On the contrary, it makes
With a boiler, the i.e. high-pressure boiler in parallel with exhaust receiver, to remove energy from system.One significant advantage is gas
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, second part that engine is configured to be vented is from cylinder
It is transported to turbine and without boiler.
In the second possible embodiment of first aspect, engine includes the auxiliary air blast 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 second part of the first part of exhaust and exhaust structure together
At 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 exhaust pipe 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
Exhaust pipe is connected at position.
In the 7th possible embodiment of first aspect, engine includes first in exhaust gas recirculatioon pipeline
Control valve.
In the 8th possible embodiment of first aspect, engine includes the second control in bypass duct
Valve.
In the 9th possible embodiment of first aspect, engine includes third control valve, the third control valve position
Between the position that the third place and exhaust gas recirculatioon pipeline are connected to exhaust pipe.
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 according to desired turbocharger to control boiler
The distribution of exhaust stream between exhaust pipe.
In the 12nd possible embodiment of first aspect, boiler is integrated into exhaust receiver.
In the 13rd possible embodiment of first aspect, exhaust receiver, which 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 assisted turbocharger under the conditions of related load.
In the 15th possible embodiment of first aspect, scavenging receiver has for reducing 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 to horizontal in all engine loadings
Lower operation auxiliary blower, 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
Furnace.
These and other aspects of the invention will become apparent from the embodiments described below.
Detailed description of the invention
In the part in detailed below of the disclosure, exemplary embodiment shown in the drawings will be referred to, will be explained in greater detail
The present invention, in which:
Fig. 1 be show the compression-ignited turbocharged engine of large-sized two-stroke accoding to exemplary embodiment front end and one
The perspective view of side；
Fig. 2 is the rear end of the engine of Fig. 1 and the perspective view of another cross side；
Fig. 3 is the schematic diagram with the engine according to Fig. 1 of 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；
In the case that Fig. 5 is that the III level engine of the prior art in Fig. 4 has exhaust gas recirculatioon under III level mode
The schematic diagram of operation；
Fig. 6 is the II stage motor of the prior art in Fig. 4 under II grades of modes in the case where 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 the schematic diagram run in the case that the III level engine of Fig. 7 has exhaust gas recirculatioon under III level mode；
Fig. 9 is the signal that the III level engine of Fig. 7 is run in the case where i.e. no exhaust gas recirculatioon under II grades of modes
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, large-sized two-stroke compression ignition engine will be described by exemplary embodiment.Fig. 1
The large-sized low-speed turbocharging two-stroke compression ignition internal combustion of the crankshaft 22 and crosshead 23 that have is shown in perspective view 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.Large-sized turbo-charging two-stroke diesel engine usually has that there are five to 16 alinements
Cylinder, these cylinders support by cylinder bracket 25, and cylinder bracket 25 is supported by entablature 24.Engine can be used, for example, as
The sustainer of foreign-going ship or as in power station run generator stationary engine.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 exhaust valve 4 at the top of cylinder 1.Therefore, combustion chamber
Always from bottom to top, therefore engine is so-called single current for interior flowing.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 exhaust valve 4 is opened, exhaust passes through associated with corresponding cylinder 1
Exhaust pipe 20 flow into exhaust receiver 3, and be advanced through the turbine 6 that exhaust pipe 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, is arranged in parallel and extremely close to the top of the exhaust casing 1.
Exhaust receiver 3 has big volume, enables exhaust receiver in the opening equilibrium of exhaust valve 4 from each cylinder 1
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 exhaust-gas-driven turbo chargers 5 in journey diesel engine benefit from constant supply pressure.
Being vented from exhaust receiver 3 by the turbine 6 that exhaust pipe 18 is directed to turbocharger 5 (can have multiple
Turbocharger 5 and can have multiple exhaust receivers 3).Exhaust is configured into the atmosphere 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 is 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 the inclusion of the scavenging pipeline 11 of scavenging cooler 12 by compressor 9.
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 caused pressure decline of the periodical outflow of each cylinder 1.The compensating effect of scavenging receiver 2 mentions 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 the one or more turbocharger 5 being used in large-sized two-stroke diesel engine are with constant supply pressure
It runs and transmits constant supply pressure, that is, no pressure pulse can be used for each 1 scavenging of cylinder.
The engine of the prior art is equipped with exhaust gas recycling system shown in Fig. 4.Exhaust gas recycling system is configured
Scavenging is delivered at by a part of the exhaust from cylinder 1, for example, for reducing ignition temperature and thereby reducing NOxRow
It puts.What exhaust gas recycling system can be that movable or inactive either a kind of exhaust gas recirculation rate with variation runs is
System.Exhaust gas recycling system includes extending to scavenging pipeline 11 or scavenging receiver 2 from exhaust receiver 3 or exhaust pipe 18
Pipeline 30.Alternatively, exhaust can be directly acquired from cylinder 1 via valve or port (not shown).
It is shown in Fig. 4 in the prior art, exhaust pipe 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 exhaust pipe 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.These components include that the cleaning of such as washer or filter is set
It is standby, (being driven by electric motor or hydraulic motor) suction blower 32 and the first control valve 34.
Air blower 32 and the first control valve 34, 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 operator
It is dynamic.Electronic control unit is configured to starting and deactivated exhaust gas recycling system, and changeably controls 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 exhaust pipe 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 exhaust pipe 18 in exhaust gas recirculatioon pipeline 30
It is connect with the upstream position of the air inlet of turbine 6 with exhaust pipe 18.Other link positions along exhaust pipe 18 are also
It is 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 operator.Second control valve 41 is to passing through valve
Flow there is variable and controllable limited degree.
Optionally, the second control valve 4 is by electronic control unit or the ON/OFF type controlled by operator.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 is configured
At 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 defect or failure of system.The inactive reason of exhaust gas recycling system may be in opposite in order to optimize engine
In second 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, run bad or completely not
Operation.In typical compressor characteristics, pressure ratio is plotted as the function of mass flowrate and rotation speed, and efficiency curve
It is applied.When turbocharger 5 is matched to engine, the purpose is to which 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 movable situation of exhaust gas recycling system, turbocharger 5 is to be matched with engine operation (that is, being vented again
Cycling rate be for example about between 20% and 45% and with 5 matched well of turbocharger in the case where run).When exhaust again
The circulatory system fail when, in the case where 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 cause gripping for turbocharger
Stream, hypervelocity and inefficiency.
Match the exhaust gas recirculation engines for meeting IMO III level emission regulation or for following again in no exhaust
The turbocharger 5 of the II stage motor run in the case where ring (or a small amount of exhaust gas recirculatioon) is in (the asthma of compressor stability
Shake nargin) and compressor/turbocharger efficiency/fuel consumption of engine 1 between a kind of compromise.If turbocharger
Compressor matched with preferred plan when being run in the case where no exhaust gas recirculatioon, then need not be reduced in exhaust gas recirculatioon
There are big surge margins when by the flow of compressor 9 (engine operation point is mobile towards surge line).It is swept when uncompromising
When switching between these two modes in the case where atmospheric pressure (boost pressure) and engine efficiency, traditional turbocharger or
Range of flow needed for the turbocharger in variable turbine region does not have 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 is closed 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 lower 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 itself can be reduced.Therefore, electronics
Control unit can be configured as the increase with exhaust gas recirculation rate and increase the aperture of the second control valve 41, and vice versa,
To turbocharger 5 under all exhaust gas recirculation rates that engine is run therewith with engine best match.
The negative effect for flowing through the cylinder bypass of bypass duct 40 is that thermic load on engine increases, which increases
It is caused by being reduced due to the amount of the scavenging by cylinder 1.
Turbine bypass pipeline 50 is provided for blowing from exhaust pipe 18 during the operation of not exhaust gas recirculatioon
Except excessive exhaust.It is controlled by the flow of turbine bypass pipeline 50 by the 5th control valve 51.Steam copper in exhaust pipe 7
Heat in gas outlet from turbine and the exhaust from turbine bypass 50 is converted into steam by furnace 52.
Fig. 5 shows the operational mode of the engine during the operation for having exhaust gas recirculatioon in Fig. 4, 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 not 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 Fig. 6.In the operational mode of not 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 of 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, still is able to simultaneously
Enough steam is generated, and at the same time still being able to sufficiently 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).
In the first mode of operation, engine is run in the case where there is exhaust gas recirculatioon.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 cooling in scavenging by boiler tubing 35, high-pressure boiler 36, exhaust gas recirculatioon pipeline 30 and air blower 32
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 bypasses cylinder 1 and being transmitted to exhaust pipe 18 via bypass duct 40 from scavenging pipeline 11.
In the second mode of operation, engine is run in the case where no exhaust gas recirculatioon.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 is logical
Cross boiler tubing 35, high-pressure boiler 36, open third control valve 37, be transported to exhaust pipe 18 with from cylinder 1
Second (residue) of exhaust stream partially combines.Therefore, whole exhausts from cylinder 1 are transported to turbine 6.However, with
The prior art is compared, and since high-pressure boiler 36 eliminates a part in energy, and the removal of energy is partially converted into steam,
Therefore lower towards the energy value of compressor 6 in the total flow of the exhaust of conveying.Therefore, turbocharger 5 and engine are perfect
Ground balance, although turbine 6 receives whole exhaust streams from cylinder 1.
A part of the total flow of exhaust from cylinder is transported to the air inlet of turbine 6, it is preferable that either exists
There is operation in the case where exhaust gas recirculatioon still to run in the case where no 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 exhaust pipe 18.
Figure 12 shows the fourth embodiment essentially identical with first embodiment, in addition to the air inlet connection of boiler tubing 35
To except exhaust pipe 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
Steam production in the low-load region to increase sustainer such as burner.
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 to be integrated into exhaust receiver, so that less sky
Between used and engine will be more compact.
It has been combined various embodiments herein and describes the present invention.However, those skilled in the art require to protect in practice
When 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.
Appended drawing reference used in claim is not necessarily to be construed as limitation range.
Claims (13)
1. the large-sized turbo-charging two-stroke compression ignition engine that one kind has crosshead (23) comprising:
Multiple cylinders (1), each cylinder (1) are equipped with scavenging port (19) and exhaust valve (4)；
Exhaust receiver (3), the exhaust receiver (3) are connected to the cylinder via the exhaust valve (4) of each cylinder
(1)；
Turbocharger (5)；
The gas outlet of the exhaust receiver (3) is connected to the turbine and increased by exhaust pipe (18), the exhaust pipe (18)
The turbine (6) of depressor (5)；
The turbocharger compressor (9) of the turbocharger (5), the turbocharger compressor (9) is by the turbine
The turbine (6) of booster (5) drives；
Scavenging pipeline (11), the scavenging pipeline (11) is by the turbocharger compressor (9) of the turbocharger (5)
Gas outlet be connected to the air inlets of scavenging receiver (2), the scavenging pipeline (11) includes a scavenging cooler (12), described
Scavenging receiver (2) is connected to the cylinder (1) via the scavenging port (19) of each cylinder (1)；
Exhaust gas recirculatioon pipeline (30), the exhaust gas recirculatioon pipeline (30) are used to a part of exhaust gas recirculatioon returning to the vapour
Cylinder (1), the exhaust gas recirculatioon pipeline (30) include: the air blower for forcing the exhaust of recycling to return to the cylinder (1)
(32) or compressor, and for passing through the scavenging pipeline by a part of hot scavenging from the scavenging cooler (12) upstream
(11) it is transported to the turbine (6) of the turbocharger (5) and bypasses the cylinder bypass duct (40) and pot of cylinder (1)
Furnace (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) the exhaust gas recirculatioon pipeline (30) is passed through to be delivered back into the cylinder (1) and a part of hot scavenging is passed through 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) of the turbocharger (5) 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 the engine is configured as running the auxiliary blower (16) to maximize the boiler (36)
Steam production.
4. engine according to claim 2, wherein described the of the first part of the exhaust and the exhaust
Two parts constitute total exhaust from the cylinder (1) together.
5. engine according to claim 1, the engine includes the boiler tubing (35) with the boiler (36),
The air inlet of the boiler tubing (35) is connected to the exhaust receiver (3) or the exhaust pipe (18) in first position.
6. engine according to claim 5, wherein the gas outlet of the boiler tubing (35) is connected in the third place
The exhaust gas recirculatioon pipeline (30), the third place are located at the upstream of the air blower (32) or compressor.
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 setting downstream is connected to the exhaust pipe (18).
8. engine according to claim 1, the engine includes being located in the exhaust gas recirculatioon pipeline (30)
First control valve (34).
9. engine according to claim 1, the engine includes the second control in the bypass duct (40)
Valve (41) processed.
10. engine according to claim 6, the engine includes third control valve (37), the third control valve
(37) it is located at the third place and the exhaust gas recirculatioon pipeline (30) is connected between the position of the exhaust pipe (18).
11. engine according to claim 1, wherein the exhaust gas recirculatioon pipeline (30) includes that exhaust gas recirculatioon is cold
But device (39).
12. engine according to claim 1, wherein when running in the second mode of operation, according to desired
The balance of turbocharger (5) controls the distribution of the exhaust stream between the boiler (36) and the exhaust pipe (18).
13. engine according to claim 1, wherein the boiler (36) is integrated into the exhaust receiver (3)
In.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DKPA201671013 | 2016-12-21 | ||
| DKPA201671013A DK179313B1 (en) | 2016-12-21 | 2016-12-21 | Large turbocharged two-stroke compression-igniting engine with exhaust gas recirculation |
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| CN108223203A CN108223203A (en) | 2018-06-29 |
| CN108223203B true 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) |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| 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 |
| 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 |
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|---|---|---|---|---|
| JPH0338410Y2 (en) * | 1985-02-21 | 1991-08-14 | ||
| JPH0533662A (en) * | 1991-07-31 | 1993-02-09 | Isuzu Ceramics Kenkyusho:Kk | Two-stroke turbo-compound engine |
| JPH08165925A (en) * | 1994-12-14 | 1996-06-25 | Toyota Motor Corp | Cooling water circulating device for egr cooler of internal combustion engine |
| US6003315A (en) * | 1997-03-31 | 1999-12-21 | Caterpillar Inc. | Exhaust gas recirculation system for an internal combustion engine |
| FR2770582B1 (en) * | 1997-10-31 | 2000-01-28 | Valeo Thermique Moteur Sa | GAS EXHAUST AND RECIRCULATION LINE FOR MOTOR VEHICLE ENGINES |
| JP2002332919A (en) * | 2001-02-26 | 2002-11-22 | Mitsubishi Heavy Ind Ltd | Exhaust gas recirculation system |
| JP4114535B2 (en) * | 2003-05-06 | 2008-07-09 | 株式会社デンソー | Thermoelectric generator |
| JP4418273B2 (en) * | 2004-03-25 | 2010-02-17 | 三菱重工業株式会社 | Power generation device with premixed combustion engine |
| JP2009127513A (en) * | 2007-11-22 | 2009-06-11 | Toyota Motor Corp | Control device of internal combustion engine |
| DE102010003002B4 (en) * | 2010-03-18 | 2018-10-31 | Man Diesel & Turbo Se | Exhaust gas turbocharger arrangement with exhaust gas recirculation device and exhaust gas compressor |
| JP5377532B2 (en) * | 2011-01-26 | 2013-12-25 | エムエーエヌ・ディーゼル・アンド・ターボ・フィリアル・アフ・エムエーエヌ・ディーゼル・アンド・ターボ・エスイー・ティスクランド | Large turbocharged diesel engine with energy recovery configuration |
| DK177388B1 (en) * | 2011-01-31 | 2013-03-04 | Man Diesel & Turbo Deutschland | Large turbocharged two-stroke diesel engine with exhaust gas recirculation |
| JP2013032751A (en) * | 2011-08-03 | 2013-02-14 | Aisin Seiki Co Ltd | Engine system |
| DK177700B1 (en) * | 2012-04-19 | 2014-03-24 | Man Diesel & Turbo Deutschland | A large slow running turbocharged two stroke internal combustion engine with crossheads and exhaust- or combustion gas recirculation |
| JP6064575B2 (en) * | 2012-12-17 | 2017-01-25 | いすゞ自動車株式会社 | Exhaust heat recovery device for internal combustion engine and exhaust heat recovery method for internal combustion engine |
| CN104358627B (en) * | 2014-11-04 | 2016-11-30 | 哈尔滨工程大学 | Boat diesel engine NOx and SOx associating emission reduction device and control method |
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2016
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| Publication number | Publication date |
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| CN108223203A (en) | 2018-06-29 |
| DK201671013A1 (en) | 2018-04-30 |
| DK179313B1 (en) | 2018-04-30 |
| KR102019931B1 (en) | 2019-11-04 |
| JP6595571B2 (en) | 2019-10-23 |
| JP2018100669A (en) | 2018-06-28 |
| KR20180072552A (en) | 2018-06-29 |
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