CN100392216C - Piston type internal combustion engine - Google Patents
Piston type internal combustion engine Download PDFInfo
- Publication number
- CN100392216C CN100392216C CNB2004100635398A CN200410063539A CN100392216C CN 100392216 C CN100392216 C CN 100392216C CN B2004100635398 A CNB2004100635398 A CN B2004100635398A CN 200410063539 A CN200410063539 A CN 200410063539A CN 100392216 C CN100392216 C CN 100392216C
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- Prior art keywords
- air
- diesel engine
- large diesel
- stroke large
- gas
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- 238000002485 combustion reaction Methods 0.000 title abstract description 4
- 239000007789 gas Substances 0.000 claims description 88
- 239000002912 waste gas Substances 0.000 claims description 47
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 8
- 238000004064 recycling Methods 0.000 claims description 7
- 238000011144 upstream manufacturing Methods 0.000 claims description 6
- 230000005540 biological transmission Effects 0.000 claims description 5
- 238000010438 heat treatment Methods 0.000 claims description 4
- 239000003638 chemical reducing agent Substances 0.000 claims description 3
- 230000006835 compression Effects 0.000 claims description 3
- 238000007906 compression Methods 0.000 claims description 3
- 238000001816 cooling Methods 0.000 abstract description 6
- 238000002156 mixing Methods 0.000 abstract description 2
- 230000015572 biosynthetic process Effects 0.000 description 4
- 230000002349 favourable effect Effects 0.000 description 3
- 238000009833 condensation Methods 0.000 description 2
- 230000005494 condensation Effects 0.000 description 2
- 230000008021 deposition Effects 0.000 description 2
- 238000005265 energy consumption Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000005336 cracking Methods 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
- 230000008093 supporting effect Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
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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
- F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
- F02B29/04—Cooling of air intake supply
- F02B29/045—Constructional details of the heat exchangers, e.g. pipes, plates, ribs, insulation, materials, or manufacturing and assembly
- F02B29/0468—Water separation or drainage means
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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
- F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
- F02B29/04—Cooling of air intake supply
- F02B29/0406—Layout of the intake air cooling or coolant circuit
- F02B29/0425—Air cooled heat exchangers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/02—Drives of pumps; Varying pump drive gear ratio
- F02B39/08—Non-mechanical drives, e.g. fluid drives having variable gear ratio
- F02B39/10—Non-mechanical drives, e.g. fluid drives having variable gear ratio electric
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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
- F02M26/02—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
- 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
- F02M26/27—Layout, e.g. schematics with air-cooled heat exchangers
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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
- F02M26/34—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with compressors, turbines or the like 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
- F02M26/40—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with timing means in the recirculation passage, e.g. cyclically operating valves or regenerators; with arrangements involving pressure pulsations
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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
- F02M26/52—Systems for actuating EGR valves
- F02M26/59—Systems for actuating EGR valves using positive pressure actuators; Check valves therefor
- F02M26/61—Systems for actuating EGR valves using positive pressure actuators; Check valves therefor in response to exhaust pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/16—Control of the pumps by bypassing charging air
- F02B37/164—Control of the pumps by bypassing charging air the bypassed air being used in an auxiliary apparatus, e.g. in an air turbine
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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
- F02M26/02—EGR systems specially adapted for supercharged engines
- F02M26/09—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine
- F02M26/10—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine having means to increase the pressure difference between the exhaust and intake system, e.g. venturis, variable geometry turbines, check valves using pressure pulsations or throttles in the air intake or exhaust system
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Supercharger (AREA)
- Exhaust-Gas Circulating Devices (AREA)
Abstract
A reciprocating internal combustion engine comprises a cylinder(2) connected to a charging distributor(4) and an exhaust manifold(6), an exhaust gas turbocharger(7) operating by using exhaust gas from the exhaust manifold and compressing air to the charging distributor, an exhaust gas re-circulation system(16) mixing exhaust gas from the exhaust manifold with air from the exhaust gas turbocharger, and a compressor(20) flowing exhaust gas mixed with air. The compressor is driven by a turbine(19), and the turbine is operated by driving air. Driving air is branched from compressed air by the exhaust gas turbocharger, and heated by exhaust gas while cooling re-circulation exhaust gas.
Description
Technical field
The present invention relates to a kind of internal-combustion piston engine, particularly two-stroke large diesel engine.
Background technique
Can reduce NOx content in the waste gas by the waste gas component to the mixing of pressurized air, this is always satisfactory.In the device of the known described form of beginning, promote to treat that the gas compressor of the waste gas component that mixes with pressurized air can be by means of a drive unit driving that consumes additional-energy.Additional-energy consumption such in two-stroke large diesel engine can surpass 1.5% of producible energy.Be cooled if treat the waste gas component that mixes with pressurized air, then getting in touch energy consumption with it.Because therefore described shortcoming reduces total efficiency.Another shortcoming of known devices is, may produce the variation of the mass flow rate that flows through motor and the unbalanced state on exhaust-gas turbocharger when Exhaust gas recirculation device is closed.
Summary of the invention
Therefore setting out thus the objective of the invention is, and starts the device of described form with the method improvement of simple and low expense, makes it can reach higher total efficiency and stable operating mode.
Reach like this according to this purpose of the present invention, promptly, two-stroke large diesel engine, it comprises that at least one can be connected to the cylinder on a pressurized air distribution piping and the exhaust manifold, at least one can be used to operate from exhaust manifold, compression can be defeated by exhaust-gas turbocharger and at least one Exhaust gas recirculation device of the pressurized air of pressurized air pipeline, by this recycling device the one waste gas component that can shunt from the waste gas that leaves exhaust manifold can be mixed in the downstream of exhaust-gas turbocharger with pressurized air, wherein be provided with a gas compressor, the waste gas component that this gas compressor promotion can mix with pressurized air; Wherein, the gas compressor of Exhaust gas recirculation device can be driven by means of a turbine, can supply with this turbine to drive air, this driving air is shunted from the pressurized air that compresses by means of exhaust-gas turbocharger as the air component, it is characterized in that: Exhaust gas recirculation device comprises a heat exchanger, but this heat exchanger can be crossed and on the other hand can be by the air component stream mistake of the driving air that constitutes turbine by the waste gas component stream of recirculation on the one hand, but makes and drive under the situation of waste gas component that air cools off recirculation at the same time by its heating.
But thereby the energy applications that temperature obtained that will be cooled to be suitable for to drive motor in this case in an advantageous manner by the waste gas component of recirculation is in the gas compressor that drives Exhaust gas recirculation device and be applied to the operation of Exhaust gas recirculation device.Therefore avoided adopting external energy to the full extent, this advantageously reaches the result of very high total efficiency.Thereby but reach the lower temperature of waste gas component and the favourable relative cylinder charge of recirculation simultaneously.Another advantage according to measure of the present invention is, the starting or close the variation that can not cause the mass flow rate by motor and realize balance on the exhaust-gas turbocharger of recycling device.Therefore utilize and achieve the above object according to the mode of measure of the present invention by open-and-shut and low expense.
The favourable structure of above-mentioned measure and the further formation that conforms with purpose are illustrated in the following content.Like this, Exhaust gas recirculation device conforms with the destination and comprises a low-pressure turbine gas compressor, and it has the gas compressor that at least one turbine that can be crossed by the air component stream and at least one can be crossed by the waste gas component stream.The application of low-pressure turbine gas compressor obtains the device of a compactness, and it can advantageously utilize energy of flow and heat energy for domination.
Advantageously, Exhaust gas recirculation device can comprise that one conforms with the heat exchanger that the destination constitutes rotary heat exchanger, but it can be crossed and on the other hand can be by constituting the air component stream mistake that gas compressor drives air by the waste gas component stream of recirculation on the one hand.Even rotary heat exchanger constitutes the member of a low expense and also produce very high efficient in an advantageous manner under little pressure difference.
Conforming with the destination can be connected in the low-pressure turbine gas compressor with rotary heat exchanger in transmission, wherein conform with the destination and between low-pressure turbine gas compressor and rotary heat exchanger one speed reducer is set.These measures form Exhaust gas recirculation device self-centered formation in transmission.
In other further formation of above-mentioned measure, a helper motor can be set in the power train between low-pressure turbine gas compressor and the rotary heat exchanger.This measure can be carried out simple rotational speed regulation in an advantageous manner and provide an auxiliary drive simultaneously under the situation not enough for the driving air of domination.These measures can also be simplified the bearing of the axle of low-pressure turbine gas compressor in addition.
Another favourable measure can be, in air one side one air humidification device is set in the front of heat exchanger, and conforms with the destination and also in waste gas one side one waste gas humidifying device is set in the back of heat exchanger.Air humidification in the front of the passage by heat exchanger causes the cooling of air not have the heat content loss, improves with respect to the temperature difference of waste gas thus and improves heat exchange.Thereby the humidification of waste gas produces low especially exhaust gas temperature in an advantageous manner and produces low especially power consumpiton by gas compressor the time.The heating of the waste gas that certainly leads to by gas compressor the time causes the reliable evaporation of possible little water droplet.
Advantageously, but Exhaust gas recirculation device is designed so that the waste gas component of recirculation roughly is equivalent to be used as the air component that drives air.Guarantee whereby, because the starting or close and can not change relative cylinder charge in the motor of recycling device.
The structure of other of above-mentioned measure and the further formation that conforms with purpose are illustrated in the following description and by the following case description by means of accompanying drawing and can learn in more detail.
Description of drawings
Unique accompanying drawing illustrates a schematic representation for the recycling device of big-block engine configuration.
Embodiment
Main application fields of the present invention is a big-block engine, and particularly two-stroke large diesel engine such as its can be used as marine propulsion etc.The structure of this motor and action principle itself are known.
A kind of two-stroke large diesel engine 1 shown in the accompanying drawing, it comprises a plurality of cylinders 2 that in a row are provided with in succession, they are connected on the pressurized air distribution piping 4 and via an exhaust fitting 5 via a pressure inlet joint 3 respectively and are connected on the exhaust manifold 6.Pressurized air distribution piping 4 and exhaust manifold 6 are made of the large diameter pipe that extends along engine overall length.
Provide pressurized air by an exhaust-gas turbocharger 7, its turbine 8 can be supplied with waste gas via an exhaust piping of being told by exhaust manifold 69, and its air compressor 10 can be supplied with the pressurized air of compression via a steam line 11 by pressurized air distribution piping 4.The relief opening of turbine 8 is connected one and leads on the exhaust piping 12 of environment.Connection one ends at the Air suction pipe joint 13 of environment on the suction port of air compressor 10.Steam line 11 leads to a charger-air cooler 14, and it is connected with pressurized air distribution piping 4 via a water separator 15.
In order to reach good NOx value, a certain amount of waste gas is mixed with the pressurized air of being defeated by pressurized air distribution piping 4, this waste gas participates in combustion process once more.Be provided with an Exhaust gas recirculation device 16 for this reason, borrow it to be defeated by and to distribute a waste gas component the waste gas of turbine 8 of exhaust-gas turbocharger 7 and can mix with pressurized air from leaving exhaust manifold 6 in the downstream of exhaust-gas turbocharger 7.
Exhaust gas recirculation device 16 comprises a recirculation conduit 17, it is told from the exhaust piping 9 that leads exhaust-gas turbochargers 7 turbines 8 by exhaust manifold 6, and feeds the flow passage that increases the gas compressor 10 guiding pressurized air distribution pipings 4 of device 7 from exhaust gas turbine with its other end.Exhaust gas recirculation device 16 also comprises a low-pressure turbine gas compressor 18 and with a turbine 19 coupled gas compressor 20 in transmission, handles recirculation conduits 17 via gas compressor 20.Therefore will be compressed to the pressure that is suitable for infeeding the pressurized air from the waste gas component that exhaust piping 9 distributes by gas compressor 20, also be about to pressurized air one side that its waste gas one side from motor is pumped into motor.
The turbine 19 of low-pressure turbine gas compressor 18 is supplied with pressurized air as driving air.It shunts from the steam line of being told by the air compressor 10 of exhaust-gas turbocharger 7 11 as the air component.Be provided with a driving air conduit 21 of telling from steam line 11, it was led the turbine 19 of low-pressure turbine gas compressor 18 and can feed exhaust manifold 6 by its other end for this reason.
The waste gas component of recirculation is cooled to be suitable for driving the temperature of motor 1 after telling from exhaust piping 9.But the energy that regain this moment from the waste gas component is not eliminated, and is used as the pressurized air component that turbine 19 drives air and be defeated by, and therefore it be heated.Exhaust gas recirculation device 16 comprises a heat exchanger 22 for this reason, and packing into its another side on one side it packs recycling device 17 into it drives air conduit 21.Heat exchanger 22 can constitute fixing plate heat exchanger.What conform with purpose is, heat exchanger 22 is constituted the rotary heat exchanger of speed driving that can be low, to also illustrating in greater detail below it.
In order in the zone of heat exchanger 22, to reach high heat exchange, between the air of the waste gas of heat release and heat absorption, provide high temperature difference.Make the driving air that flows through heat exchanger 22 in the cooling of the front of the passage that passes through heat exchanger 22 for this reason.Be provided with for this reason one pack in the upstream of heat exchanger 22 drive air conduit 21, be provided with a water and take over 23 humidifying device 24, borrow it will lead its air component water humidification, this produces cooling and does not have the heat content loss.
For in the zone of the gas compressor 20 of low-pressure turbine gas compressor 18 by realizing alap exhaust gas temperature, further the waste gas component of gas compressor 20 is defeated by in cooling in the back of the passage by heat exchanger 22, it had carried out cooling for the first time in this passage.In recirculation conduit 17, be provided with one for this reason equally and be provided with a water and take over 23 humidifying device 24a, but borrow its humidification to lead its waste gas in the upstream of the downstream of heat exchanger 22 and gas compressor 20.
Above-mentioned the be incorporated into humidifying device 24, the 24a that drive in air conduit 21 or the recirculation conduit 17 conform with purpose, but are not indispensable.Also can imagine,, thereby can be switched on or switched off each humidifying device selectively for each humidifying device disposes closable arm.Can imagine equally, be switched on or switched off water supply simply selectively to humidifying device 24,24a.
The waste gas component of leading gas compressor 20 is compressed and is heated simultaneously.Because this heating makes the little water-drop evaporation that still is present in the waste gas.If avoid condensation deposition, then recirculation conduit 17 can feed the flow channel of the guiding pressurized air distribution piping 4 of pressurized air in the downstream of charger-air cooler 14, as in the accompanying drawing by shown in the adapter 17a that represents with solid line.Recirculation conduit 17 feeds water separator 15 in the downstream of charger-air cooler 14 in the example shown.
If wish condensation deposition in charger-air cooler 14, then recirculation conduit 17 can feed steam line 11 in the upstream of charger-air cooler 14, as in the accompanying drawing by shown in the adapter 17b that dots.Wherein to the ingress of cooler 14 sparger 25 can be set, be connected to and take on the 17b at steam line 11.Sparger 25 can suck waste gas.
The shunt of leaving the driving air conduit 21 of low-pressure turbine gas compressor 18 turbines 19 can feed in the exhaust manifold 6 as previously discussed, as in the accompanying drawing with shown in the solid line.But also can imagine, as in the accompanying drawing with shown in the dotted line, the driving air that leaves turbine 19 is defeated by another device for other utilization, a turbine 26 for example, borrow it for example can drive a gas compressor that is not shown in further detail, the outlet of this turbine 26 can be connected with the inlet of the air compressor 10 of exhaust-gas turbocharger 7, thereby forms a dual stage apparatus.For rotational speed regulation with in order to guarantee auxiliary drive, can be connected to the motor 27 of a power supply for turbine 26 configurations one.
What conform with purpose is that heat exchanger 22 is constituted the rotary heat exchanger that can drive than the slow-speed of revolution, as previously discussed.The driving of heat exchanger 22 can conform with the destination and be produced by low-pressure turbine gas compressor 18, as shown in the drawing.Be provided with one speed reducer 28 in order to slow down, its output terminal is connected with heat exchanger 22 its input end with low-pressure turbine gas compressor 18 in transmission.
In the example shown, be provided with a helper motor 29 in the power train between low-pressure turbine gas compressor 18 and heat exchanger 22, it can regulate rotating speed, if and the air short weight that at first provides is used for this reason, this for example may take place when beginning, and it just can support the driving of low-pressure turbine gas compressor 18.Helper motor 29 is arranged in the zone between low-pressure turbine gas compressor 18 and the retarder 28 in the example shown.The housing of helper motor 29 can be fixed on the member of fixing.The bearing 30 of the rotor of helper motor 29 by two sides is bearing on the extending portion of input end of guiding retarder 28 of a side of axle 31 of low-pressure turbine gas compressor 18.Therefore have only another bearing 32 supportings just enough in the zone of low-pressure turbine gas compressor 18 again when axle 31, its middle (center) bearing 32 conforms with in the turbine 19 and the zone between the gas compressor 20 that the destination is arranged on low-pressure turbine gas compressor 18.
The shunt of the upstream that is positioned at gas compressor 20 of recirculation conduit 17 is provided with one and is located at the safety check 33 of heat exchanger 22 back at this, as long as gas compressor 20 produces enough suction forces, this safety check 33 is just automatically opened.Conforming with purpose safety check 33 is constituted, to make its cracking pressure be adjustable.In order to start and to close recycling device 16, in driving air conduit 21, promptly in the shunting in the zone of steam line 11, be provided with shut off valve 34 what drive air conduit 21.Waste gas passing capacity by recirculation conduit 17 should roughly be identical with air passing capacity by driving air conduit 21.The air passing capacity can be regulated by the adjusting of shut off valve 34.The waste gas passing capacity can be regulated by means of adjustable safety check 33 when needed.Also can imagine an additional modulating valve.
Claims (19)
1. two-stroke large diesel engine, it comprises that at least one can be connected to the cylinder (2) on a pressurized air distribution piping (4) and the exhaust manifold (6), at least one can be used to operate from exhaust manifold (6), compression can be defeated by exhaust-gas turbocharger (7) and at least one Exhaust gas recirculation device (16) of the pressurized air of pressurized air pipeline (4), by this recycling device the one waste gas component that can shunt from the waste gas that leaves exhaust manifold (6) can be mixed in the downstream of exhaust-gas turbocharger (7) with pressurized air, wherein be provided with a gas compressor (20), the waste gas component that this gas compressor promotion can mix with pressurized air; Wherein, the gas compressor (20) of Exhaust gas recirculation device (16) can be driven by means of a turbine (19), can supply with this turbine (19) to drive air, this driving air is shunted from the pressurized air that compresses by means of exhaust-gas turbocharger (7) as the air component, it is characterized in that: Exhaust gas recirculation device (16) comprises a heat exchanger (22), but this heat exchanger can be crossed and on the other hand can be by the air component stream mistake of the driving air that constitutes turbine (19) by the waste gas component stream of recirculation on the one hand, but makes and drive under the situation of waste gas component that air cools off recirculation at the same time by its heating.
2. according to the described two-stroke large diesel engine of claim 1, it is characterized in that, Exhaust gas recirculation device (16) has a low-pressure turbine gas compressor (18), and this low-pressure turbine gas compressor comprises the gas compressor (20) of the waste gas component that can supply with the turbine (19) that drives air and promote to mix with pressurized air.
3. according to the described two-stroke large diesel engine of claim 2, it is characterized in that heat exchanger (22) constitutes rotary heat exchanger.
4. according to the described two-stroke large diesel engine of claim 3, it is characterized in that rotary heat exchanger is connected with low-pressure turbine gas compressor (18) in transmission.
5. according to claim 3 or 4 described two-stroke large diesel engines, it is characterized in that, be provided with one speed reducer (28), its input end is connected with low-pressure turbine gas compressor (18) and its output terminal is connected with rotary heat exchanger.
6. according to the described two-stroke large diesel engine of claim 5, it is characterized in that, be low-pressure turbine gas compressor (18) configuration one helper motor (29).
7. according to the described two-stroke large diesel engine of claim 6, it is characterized in that helper motor (29) is arranged between low-pressure turbine gas compressor (18) and the retarder (28).
8. according to one of claim 1-4 described two-stroke large diesel engine, it is characterized in that, be provided with an air humidification device (24) in air one side in the front of heat exchanger (22).
9. according to one of claim 1-4 described two-stroke large diesel engine, it is characterized in that, be provided with a waste gas humidifying device (24a) in waste gas one side in the back of heat exchanger (22).
10. according to one of claim 1-4 described two-stroke large diesel engine, it is characterized in that, but in a recirculation conduit (17) that disposes for the waste gas component of recirculation, an adjustable safety check (33) is set.
11. according to one of claim 1-4 described two-stroke large diesel engine, it is characterized in that, in a driving air conduit (21) that disposes for the air component that is used as the driving air, a shut off valve and/or modulating valve (34) be set.
12. according to one of claim 1-4 described two-stroke large diesel engine, it is characterized in that, Exhaust gas recirculation device (16) is constituted like this, make the waste gas component that can mix roughly be equivalent to be used as the air component that can from pressurized air, distribute that drives air with pressurized air.
13. according to the described two-stroke large diesel engine of claim 10, it is characterized in that, but the waste gas component of recirculation can be defeated by pressurized air in the downstream of a charger-air cooler (14).
14., it is characterized in that recirculation conduit (17) has one and takes over (17a) according to the described two-stroke large diesel engine of claim 13, this adapter feeds one in the water separator (15) that charger-air cooler (14) is provided with later.
15., it is characterized in that recirculation conduit (17) has one and takes over (17b) according to the described two-stroke large diesel engine of claim 13, this is taken in the upstream of charger-air cooler (14) and feeds in the flow channel that disposes for pressurized air.
16. according to the described two-stroke large diesel engine of claim 15, it is characterized in that, one sparger (25) be set in an ingress that feeds in the flow channel that disposes for pressurized air for the steam line (11) of pressurized air configuration.
17., it is characterized in that the adapter (17b) that feeds in the upstream of charger-air cooler (14) is connected on the sparger (25) of the ingress that is located at charger-air cooler (14) according to the described two-stroke large diesel engine of claim 16.
18. according to the described two-stroke large diesel engine of claim 16, it is characterized in that, leave the air component of the turbine (19) of low-pressure turbine gas compressor (18) and can be defeated by exhaust manifold (6).
19. according to claim 2 or 18 described two-stroke large diesel engines, it is characterized in that, leave the air component of the turbine (19) of low-pressure turbine gas compressor (18) and can be defeated by another flow device (26) for other utilization.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE10331187.4 | 2003-07-10 | ||
| DE10331187A DE10331187B4 (en) | 2003-07-10 | 2003-07-10 | reciprocating internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1576539A CN1576539A (en) | 2005-02-09 |
| CN100392216C true CN100392216C (en) | 2008-06-04 |
Family
ID=34071608
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004100635398A Expired - Lifetime CN100392216C (en) | 2003-07-10 | 2004-07-09 | Piston type internal combustion engine |
Country Status (3)
| Country | Link |
|---|---|
| KR (1) | KR101127082B1 (en) |
| CN (1) | CN100392216C (en) |
| DE (1) | DE10331187B4 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SE528621C2 (en) * | 2005-05-18 | 2006-12-27 | Scania Cv Ab | Arrangements for the recirculation of exhaust gases of a supercharged internal combustion engine |
| JP4609243B2 (en) | 2005-08-30 | 2011-01-12 | 株式会社デンソー | Exhaust gas recirculation device |
| DE102005057207B4 (en) * | 2005-12-01 | 2011-07-21 | Man Diesel & Turbo, Filial Af Man Diesel & Turbo Se, Tyskland | Internal combustion engine and method for reducing the NOx emission in such a motor |
| WO2008050178A1 (en) * | 2006-10-24 | 2008-05-02 | Renault Trucks | Internal combustion engine comprising an exhaust gas recirculation system |
| CN101012925B (en) * | 2007-01-31 | 2012-08-22 | 徐建明 | Recycle burning utilization method reclaimed exhaust generated by combustion of hydrocarbon fuel and water or water vapour |
| DE102008058612B4 (en) * | 2008-11-22 | 2017-05-24 | Man Diesel & Turbo, Filial Af Man Diesel & Turbo Se, Tyskland | Internal combustion engine and exhaust valve housing and Rezirkulationsgassammelbehälter this |
| DK201000077U4 (en) * | 2010-04-29 | 2012-05-25 | Beco Consult Aps | Closing mechanism for boxes and lids |
| JP4997336B2 (en) * | 2010-01-29 | 2012-08-08 | 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 two-cycle diesel engine with exhaust gas recirculation system |
| DE102010007124B4 (en) * | 2010-02-05 | 2014-04-10 | Pierburg Gmbh | Heat transfer device and arrangement for exhaust gas recirculation with such a heat transfer device |
| US8549854B2 (en) | 2010-05-18 | 2013-10-08 | Achates Power, Inc. | EGR constructions for opposed-piston engines |
| FR2962507B1 (en) * | 2010-07-12 | 2013-04-05 | Valeo Equip Electr Moteur | DEVICE FOR TRANSMITTING A MECHANICAL TORQUE BETWEEN A LEADING BODY AND A POWERED BODY AND SYSTEM FOR COMPRESSING THE SUPPLY AIR OF AN ENGINE USING SUCH A DEVICE. |
| US8943823B2 (en) | 2010-11-18 | 2015-02-03 | Caterpillar Inc. | Fluid handling system having dedicated EGR turbo-generator |
| DK177388B1 (en) * | 2011-01-31 | 2013-03-04 | Man Diesel & Turbo Deutschland | Large turbocharged two-stroke diesel engine with exhaust gas recirculation |
| US20130174548A1 (en) * | 2011-05-16 | 2013-07-11 | Achates Power, Inc. | EGR for a Two-Stroke Cycle Engine without a Supercharger |
| DE102012009315B4 (en) | 2012-05-10 | 2021-04-22 | MAN Energy Solutions, branch of MAN Energy Solutions SE, Germany | Internal combustion engine |
| DE102012009314B4 (en) | 2012-05-10 | 2020-01-30 | Man Diesel & Turbo, Filial Af Man Diesel & Turbo Se, Tyskland | internal combustion engine |
| DE102012009319B4 (en) | 2012-05-10 | 2018-11-08 | Man Diesel & Turbo, Filial Af Man Diesel & Turbo Se, Tyskland | Two-stroke large diesel engine with Rezirkulationsgasverdichter and thus coupled steam turbine |
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Also Published As
| Publication number | Publication date |
|---|---|
| KR101127082B1 (en) | 2012-03-23 |
| DE10331187B4 (en) | 2007-09-06 |
| CN1576539A (en) | 2005-02-09 |
| DE10331187A1 (en) | 2005-02-17 |
| KR20050007185A (en) | 2005-01-17 |
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