WO2018114027A1 - Moteur à combustion interne à recirculation des gaz d'échappement - Google Patents

Moteur à combustion interne à recirculation des gaz d'échappement Download PDF

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Publication number
WO2018114027A1
WO2018114027A1 PCT/EP2017/001343 EP2017001343W WO2018114027A1 WO 2018114027 A1 WO2018114027 A1 WO 2018114027A1 EP 2017001343 W EP2017001343 W EP 2017001343W WO 2018114027 A1 WO2018114027 A1 WO 2018114027A1
Authority
WO
WIPO (PCT)
Prior art keywords
exhaust gas
exhaust
internal combustion
gas recirculation
combustion engine
Prior art date
Application number
PCT/EP2017/001343
Other languages
German (de)
English (en)
Inventor
Rolf Pfeifer
Günther Schmidt
Ralf Speetzen
Original Assignee
Mtu Friedrichshafen Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mtu Friedrichshafen Gmbh filed Critical Mtu Friedrichshafen Gmbh
Publication of WO2018114027A1 publication Critical patent/WO2018114027A1/fr

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Classifications

    • 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
    • F02M26/02—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
    • 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
    • F02M26/33—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 controlling the temperature of the recirculated gases
    • 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
    • F02M26/43—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 in which exhaust from only one cylinder or only a group of cylinders is directed to the intake of the engine

Definitions

  • the invention relates to an exhaust system for an internal combustion engine with an exhaust gas recirculation and a control unit and an internal combustion engine.
  • Such internal combustion engines and exhaust gas stirring systems are known from the prior art such as DE 10 2004 015 108 AI or DE 10 2007 01 1 680 AI.
  • the exhaust gas cooler is exposed to changes in the operating state, in particular between operating points with and without exhaust gas recirculation, thermal load changes, which leads to shortening the service life of the exhaust gas cooler. Desirable is therefore an extension of the life.
  • an exhaust system for an internal combustion engine with an exhaust gas recirculation, wherein the internal combustion engine having a first cylinder group having at least one cylinder and a second cylinder group having at least one cylinder and at least the second cylinder group on the exhaust side via a Manifold is connected to an exhaust gas recirculation device, wherein the exhaust gas recirculation device comprises an exhaust gas cooler, characterized in that in the exhaust gas recirculation means a first exhaust valve for controlling the exhaust gas recirculation rate downstream of the exhaust gas cooler is arranged and that a first exhaust pipe for non-recirculated exhaust gas with a second exhaust valve downstream of the exhaust gas cooler is arranged.
  • the first and second exhaust valves are used to set a desired EGR rate for the respective operating state.
  • the desired EGR rate is determined by the setting set of advantageously matched opening states of the first and second exhaust valve.
  • the opening states may include full-opening states or partial opening states of the first and / or second exhaust gas flap, which are advantageously matched to one another.
  • the required back pressure for the pressure gradient between an exhaust gas side and a charge air side of the internal combustion engine is set via the first and second exhaust gas flaps.
  • the amount of cooled exhaust gases can be adjusted via the exhaust flaps.
  • the exhaust flaps can be designed for example as valves or fixed blinds. The invention is based on the consideration that the life of the exhaust gas cooler is largely determined by the number of thermal load changes.
  • any change in the exhaust gas temperature and / or the exhaust gas mass flow leads to internal stresses of the exhaust gas cooler and thus to a lifetime consumption.
  • the control of the exhaust valves causes additional thermal load alternation as the engine operating condition approaches, for example, a map point without exhaust gas recirculation a map point with exhaust gas recirculation changes.
  • the exhaust gas cooler is cooled almost to coolant temperature (80 ° C to 95 ° C), at other map points, the inlet temperature of the exhaust gas depending on the concept rise to 700 ° C.
  • the invention is based on the recognition that a low thermal load can be achieved by thermal load changes in the exhaust gas cooler when the amount of exhaust gas that is passed through the exhaust gas cooler can be adjusted independently of the EGR rate. This is realized via the arrangement of the first exhaust pipe downstream of the exhaust gas cooler.
  • the minimum temperature in the exhaust gas cooler of about 85-90 ° C is increased to 200 ° C, which reduces the maximum temperature difference between two operating points of the internal combustion engine in the exhaust gas cooler from 620 K to about 500 K. Due to the low thermal load change as an extension of the life of the exhaust gas cooler is achieved.
  • Exhaust gas recirculation may be a low pressure exhaust gas recirculation, a high pressure exhaust gas recirculation or an exhaust gas recirculation according to the donor cylinder concept.
  • the exhaust gas cooler is integrated with a bypass in an exhaust stream or an exhaust pipe of the internal combustion engine and the first and second exhaust valve downstream of the exhaust gas cooler, the EGR rate and the pressure gradient is controlled or regulated.
  • the first exhaust pipe (211) for non-recirculated exhaust gas is arranged with the second exhaust valve downstream of the exhaust gas cooler between the exhaust gas cooler (EGR-WT) and a turbine.
  • the amount of cooled exhaust gas supplied to a turbine can be adjusted via the first and second exhaust valves.
  • an exhaust gas recirculation in the form of a donor cylinder exhaust gas recirculation is advantageous, with only the second cylinder group is connected on the exhaust side via a manifold with a Abgasriere arrangements driven.
  • FIG. 1 A prior art dispenser cylinder system is shown in FIG. The system only takes part of the cylinders of the engine as exhaust gas recirculation dispensers.
  • An exhaust flap (dispenser cylinder flap) accumulates the exhaust gas flow to the donor cylinders and thus ensures the necessary pressure gradient between the exhaust and charge air side.
  • the charge can be optimized to very good efficiencies, of the charge cycle losses are affected only the donor cylinder.
  • the known donor cylinder concept ensures less consumption, because it reduces the motor charge cycle losses and allows higher turbocharger efficiencies. This requires an additional dispenser cylinder exhaust damper compared to high pressure exhaust gas recirculation.
  • EGR rates exhaust gas recirculation rates
  • the first exhaust gas flap from the region of the uncooled exhaust gas with temperatures of up to 700 ° C. (as known in the prior art) is laid according to the invention in the region of the cooled exhaust gas, where the maximum exhaust gas temperature is only 140 ° C.
  • the thermal requirements for the first exhaust flap are thus significantly reduced. This contributes to a longer life of the first exhaust flap and thus lower costs.
  • a second exhaust gas line with a third exhaust gas valve is arranged in addition to the first exhaust gas line, which is connected via the manifold to the second cylinder group and connects them directly to the turbine.
  • the third exhaust flap for adjusting the required back pressure for the pressure gradient between the exhaust gas side and the charge air side of the internal combustion engine can be used in addition.
  • the second and the third Exhaust damper sets the amount of non-recirculated exhaust gas to be cooled, which is passed over the exhaust gas cooler. This amount of exhaust gas is correspondingly not conducted via the second exhaust pipe to the turbine, but via the first exhaust pipe.
  • the exhaust gas cooler has a coolant circuit with a bypass around the exhaust gas cooler, in which a bypass flap is arranged.
  • the amount of coolant in the exhaust gas cooler can be regulated so that in the event that less or colder exhaust gas is passed in the current operating state via the exhaust gas cooler.
  • the cooling can be reduced and the temperature of the exhaust gas cooler is subject to reduced fluctuations despite reduced exhaust gas quantity or temperature in certain operating states.
  • the invention relates to a control unit for an internal combustion engine with an exhaust gas routing system as described above, wherein the control unit is designed, to a detected current operating state out, a required exhaust gas recirculation rate and a quantity of cooling gas needed to maintain a predetermined temperature range in the exhaust gas cooler not to determine recirculated exhaust gas and to cause one of the required Abgas Wegschreibungsrate and the required amount corresponding matched opening of the first exhaust valve and the second and / or the third exhaust valve.
  • the control unit is additionally designed to initiate the setting of a predetermined coolant rate in the exhaust gas cooler via a corresponding opening of the bypass valve according to the required exhaust gas recirculation rate and the required amount of non-recirculated exhaust gas to be cooled.
  • the temperature of the exhaust gas cooler is influenced both by the amount of exhaust gas and by the amount of coolant.
  • a regulation of the exhaust gas cooler temperature is possible that at lower Exhaust gas amounts or low exhaust gas temperature less coolant is used to cool the exhaust gas and so the temperature of the exhaust gas cooler can be maintained at a higher level than in conventional exhaust system and thus the life of the exhaust gas cooler can be further extended.
  • the invention relates to an internal combustion engine with a previously described exhaust system according to the first aspect.
  • the internal combustion engine shares the advantages of the exhaust system according to the first aspect.
  • an internal combustion engine is advantageous, which additionally has a control device according to the second aspect of the invention.
  • Fig. 1 is a schematic representation of an internal combustion engine with exhaust gas recirculation according to the donor cylinder concept according to the prior art
  • FIG. 2 shows a schematic representation of an embodiment of an internal combustion engine with an exhaust system according to the invention
  • FIG. 3 shows a schematic illustration of an alternative embodiment of an internal combustion engine with an exhaust gas duct according to the invention
  • an internal combustion engine 100 with exhaust gas recirculation according to the dispenser cylinder concept according to the prior art is shown.
  • the internal combustion engine 100 includes an engine 101 with two cylinder groups 120, 130 and a control unit ECU - shown here only symbolically.
  • the internal combustion engine 100 further comprises a high-pressure turbocharger 121 with a turbine and a compressor and two low-pressure turbochargers 122, 123, wherein a respective air filter LF upstream and downstream of the compressor of the low-pressure turbocharger each intercooler ZwK is arranged upstream of the compressor air side.
  • the charge air is then passed through a high-pressure turbocharger 121 and fed to a throttle valve 4 a charge air cooler 140 and then the cylinders Al -A6, Bl - B6 of the two cylinder groups 120, 130.
  • a throttle valve 4 a charge air cooler 140
  • the exhaust gases of the cylinders of the respective cylinder group 120, 130 are collected.
  • the exhaust gases of the first cylinder group 130 are then supplied to the turbine of the high-pressure turbocharger 121.
  • a portion of the exhaust gases of the first cylinder group 130 is thereby passed via a bypass of the high-pressure turbocharger HD stage of the first cylinder group 130 directly to the turbines of the low-pressure turbocharger LP stage.
  • an exhaust bypass door 3 is arranged.
  • the cylinders A1-A6 serve as donor cylinders.
  • Their exhaust gas is partly via an exhaust gas recirculation device, in which an exhaust gas cooler AGR-WT is arranged, which is designed here as a heat exchanger, mixed with charge air from the intercooler and the charge air side the cylinders of the first and second cylinder group fed again.
  • the exhaust gas recirculation rate is set via the exhaust flaps 1 and 2.
  • the exhaust valves 1 and 2 also serve the backflow of the exhaust gas to produce a necessary for the functioning of the system back pressure for the required pressure difference between the charge air and exhaust side.
  • the amount of exhaust gas required to comply with the emissions becomes set in the system shown here with donor cylinder exhaust gas recirculation through the exhaust valves 1 and 2 and only this amount of exhaust gas is passed through the exhaust gas cooler, the rest of the exhaust gas from the donor cylinder flows through the exhaust valve 1 on the exhaust gas cooler over to the turbine.
  • the internal combustion engine shown in FIG. 2 is also constructed according to the dispenser cylinder concept for exhaust gas recirculation. Therefore, the differences between the internal combustion engine with exhaust gas routing system according to the prior art of FIG. 1 and that with exhaust gas routing system according to FIG. 2 will be described below, wherein like reference numerals generally designate like components and configurations.
  • the internal combustion engine 200 like the internal combustion engine 100, has an engine 101 with two cylinder banks 120, 130 as well as a control unit ECU.
  • the internal combustion engine 200 further comprises a high-pressure turbocharger 121 with a turbine and a compressor and two low-pressure turbochargers 122, 123, wherein an air filter LF upstream of the compressor of the low-pressure turbocharger and an intercooler ZwK downstream is arranged upstream of the compressor of the low-pressure turbocharger.
  • the charge air is subsequently conducted via a high-pressure turbocharger 121 and a throttle valve 4 is supplied to a charge air cooler 140 and then to the cylinders AI-A6, B-B6 of the two cylinder groups 120, 130.
  • the exhaust gases of the cylinders of the respective cylinder group 120, 130 are collected.
  • the exhaust gases of the first cylinder group 130 are then supplied to the turbine of the high-pressure turbocharger 121.
  • a portion of the exhaust gases of the first cylinder group 130 is thereby passed via a bypass of the high-pressure turbocharger HD stage of the first cylinder group 130 directly to the turbines of the low-pressure turbocharger LP stage.
  • an exhaust bypass door 3 is arranged.
  • the cylinders A1-A6 serve as donor cylinders. Some of their exhaust gas is mixed with charge air from the intercooler 140 via an exhaust gas routing system 210, in which an exhaust gas cooler AGR-WT is arranged here as a heat exchanger, and returned to the cylinders of the first and second cylinder groups on the charge air side.
  • the exhaust gas recirculation rate is set via a first exhaust gas flap 2 'and a second exhaust gas flap.
  • all of the exhaust gas from the donor cylinders of the second cylinder group 120 is directed via the exhaust gas cooler EGR-WT, thus increasing the minimum temperature in the exhaust gas cooler compared to the system of FIG.
  • the second exhaust flap also serves the backflow of the exhaust gas to generate a necessary for the functioning of the system dynamic pressure for the required pressure gradient between the charge air and exhaust side.
  • the flaps are controlled so that only a subset of the cooled exhaust gas is mixed via the first exhaust flap 2 'of the fresh air, the remaining cooled exhaust gas is mixed via the second exhaust valve the uncooled exhaust gas of the other cylinder of the first cylinder group 130 and the turbine of the high-pressure turbocharger 121st directed.
  • FIG. 3 shows a further embodiment of an internal combustion engine 300 with a donor cylinder exhaust gas recirculation.
  • the exhaust gas routing system 310 here, like that in FIG. 2, has a first exhaust gas line 31 1 with a second exhaust gas valve, which connects the latter with the turbine downstream of the exhaust gas cooler AGR-WT.
  • the exhaust gas routing system 310 has a second exhaust pipe 312, which is connected via a manifold 313 on the exhaust side with the second cylinder group 120.
  • a third exhaust valve 5 is arranged in the second exhaust pipe 312.
  • the amount of exhaust gas needed to maintain the emissions is set to an operating condition of the internal combustion engine via the first and third exhaust gas flaps 2 ', 5.
  • the second exhaust valve may be closed in this operating state.
  • the exhaust gas cooler AGR-WT has a coolant circuit 320 with a bypass 321 around the exhaust gas cooler EGR-WT. In the bypass 321, a bypass flap 6 is arranged. By way of the bypass 321 and the bypass flap 6, the coolant quantity in the exhaust gas cooler AGR-WT can be regulated in this embodiment.
  • the bypass flap 6 here designed as a bypass valve, opens so far that the coolant quantity through the exhaust gas cooler is reduced.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
  • Supercharger (AREA)

Abstract

L'invention concerne un système de guidage des gaz d'échappement pour un moteur à combustion interne à recirculation des gaz d'échappement. Le moteur à combustion interne présente au moins un deuxième groupe de cylindres qui comprend au moins un cylindre et qui est relié côté gaz d'échappement à un dispositif de recirculation des gaz d'échappement par l'intermédiaire d'un collecteur. Le dispositif de recirculation des gaz d'échappement comprend un refroidisseur des gaz d'échappement. L'invention est caractérisée en ce que dans le dispositif de recirculation des gaz d'échappement, un premier clapet d'échappement destiné à réguler la vitesse de recirculation des gaz d'échappement est agencé en aval du refroidisseur des gaz d'échappement et en ce qu'un premier tuyau d'échappement pour le gaz d'échappement non amené à recirculer et pourvu d'un deuxième clapet d'échappement est agencé en aval du refroidisseur de gaz entre le refroidisseur de gaz et une turbine.
PCT/EP2017/001343 2016-12-21 2017-11-16 Moteur à combustion interne à recirculation des gaz d'échappement WO2018114027A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016125285.9A DE102016125285A1 (de) 2016-12-21 2016-12-21 Brennkraftmaschine mit Abgasrückführung
DE102016125285.9 2016-12-21

Publications (1)

Publication Number Publication Date
WO2018114027A1 true WO2018114027A1 (fr) 2018-06-28

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PCT/EP2017/001343 WO2018114027A1 (fr) 2016-12-21 2017-11-16 Moteur à combustion interne à recirculation des gaz d'échappement

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WO (1) WO2018114027A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111779582A (zh) * 2020-06-23 2020-10-16 河南柴油机重工有限责任公司 一种柴油机的egr系统的控制方法、系统及应用

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4249382A (en) * 1978-05-22 1981-02-10 Caterpillar Tractor Co. Exhaust gas recirculation system for turbo charged engines
DE102004015108A1 (de) 2004-03-27 2005-10-20 Mtu Friedrichshafen Gmbh Brennkraftmaschine mit einer Abgasrückführung
DE102007011680A1 (de) 2007-03-09 2008-09-11 Mtu Friedrichshafen Gmbh Brennkraftmaschine
DE102011080694A1 (de) * 2011-08-09 2013-02-14 Robert Bosch Gmbh Brennkraftmaschine mit externer Abgasrückführung und verbessertem Kaltstartverhalten
US20150013651A1 (en) * 2013-07-09 2015-01-15 GM Global Technology Operations LLC Dedicated EGR Engine with Dynamic Load Control
DE102014118813A1 (de) * 2014-12-17 2016-06-23 Tenneco Gmbh AGR-System mit Partikelfilter für Ottomotor

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4843035B2 (ja) * 2005-07-11 2011-12-21 マック トラックス インコーポレイテッド エンジン排気温度を維持するエンジンおよび方法
JP2011017296A (ja) * 2009-07-09 2011-01-27 Toyota Motor Corp 内燃機関の排気還流装置
US8763394B2 (en) * 2010-10-25 2014-07-01 General Electric Company System and method for operating a turbocharged system
DE102013201710B4 (de) * 2013-02-01 2018-05-03 Mtu Friedrichshafen Gmbh Brennkraftmaschine mit Spenderzylinderkonzept

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4249382A (en) * 1978-05-22 1981-02-10 Caterpillar Tractor Co. Exhaust gas recirculation system for turbo charged engines
DE102004015108A1 (de) 2004-03-27 2005-10-20 Mtu Friedrichshafen Gmbh Brennkraftmaschine mit einer Abgasrückführung
DE102007011680A1 (de) 2007-03-09 2008-09-11 Mtu Friedrichshafen Gmbh Brennkraftmaschine
DE102011080694A1 (de) * 2011-08-09 2013-02-14 Robert Bosch Gmbh Brennkraftmaschine mit externer Abgasrückführung und verbessertem Kaltstartverhalten
US20150013651A1 (en) * 2013-07-09 2015-01-15 GM Global Technology Operations LLC Dedicated EGR Engine with Dynamic Load Control
DE102014118813A1 (de) * 2014-12-17 2016-06-23 Tenneco Gmbh AGR-System mit Partikelfilter für Ottomotor

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