DE102018205768B3 - Internal combustion engine with an exhaust system - Google Patents

Internal combustion engine with an exhaust system

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Publication number
DE102018205768B3
DE102018205768B3 DE102018205768.0A DE102018205768A DE102018205768B3 DE 102018205768 B3 DE102018205768 B3 DE 102018205768B3 DE 102018205768 A DE102018205768 A DE 102018205768A DE 102018205768 B3 DE102018205768 B3 DE 102018205768B3
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Germany
Prior art keywords
exhaust
exhaust gas
exhaust pipe
internal combustion
combustion engine
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DE102018205768.0A
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German (de)
Inventor
Dirk Christian Leinhos
Christian Schwarz
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Bayerische Motoren Werke AG
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Bayerische Motoren Werke AG
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Priority to DE102018205768.0A priority Critical patent/DE102018205768B3/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12Control of the pumps
    • F02B37/18Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01NGAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00Silencing apparatus characterised by method of silencing
    • F01N1/16Silencing apparatus characterised by method of silencing by using movable parts
    • F01N1/161Silencing apparatus characterised by method of silencing by using movable parts for adjusting resonance or dead chambers or passages to resonance or dead chambers
    • F01N1/163Silencing apparatus characterised by method of silencing by using movable parts for adjusting resonance or dead chambers or passages to resonance or dead chambers by means of valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01NGAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N13/00Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/08Other arrangements or adaptations of exhaust conduits
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01NGAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N3/00Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
    • F01N3/08Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/02Gas passages between engine outlet and pump drive, e.g. reservoirs
    • F02B37/025Multiple scrolls or multiple gas passages guiding the gas to the pump drive
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01NGAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N13/00Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/009Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00 having two or more separate purifying devices arranged in series
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01NGAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N13/00Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/011Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00 having two or more purifying devices arranged in parallel
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01NGAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N2240/00Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being
    • F01N2240/36Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being an exhaust flap
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01NGAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N2410/00By-passing, at least partially, exhaust from inlet to outlet of apparatus, to atmosphere or to other device
    • F01N2410/02By-passing, at least partially, exhaust from inlet to outlet of apparatus, to atmosphere or to other device in case of high temperature, e.g. overheating of catalytic reactor

Abstract

Internal combustion engine with at least four cylinders and with an exhaust system, wherein in the exhaust system, a turbine housing with a turbine of an exhaust gas turbocharger and in the flow direction of an exhaust gas behind the turbine housing, a first exhaust gas purification system is arranged, between the engine and the turbine housing, a first exhaust pipe exhaust pipe branches leading and after the exhaust gas turbocharger is a twin-scroll exhaust gas turbocharger or an exhaust gas turbocharger with a segmented turbine, wherein at least two cylinders are summarized according to a firing order of the internal combustion engine to a cylinder group and a first cylinder group via a second exhaust pipe with a first scroll and a second cylinder group via a third exhaust pipe with a second scroll exhaust gas leading connected, wherein the first exhaust pipe verbi with the second and the third exhaust pipe leading exhaust is ndbarbar and wherein in the first exhaust pipe, a second emission control system is arranged.Durch the inventive design higher specific power for the internal combustion engine can be achieved, with simultaneous thermal component protection.

Description

  • The invention relates to an internal combustion engine having an exhaust system with the features of the preamble of patent claim 1.
  • For technical environment is for example on the German disclosure DE 28 51 675 A1 pointed. From this publication, a Nachverbrennungsvorrichtung for the exhaust gases of internal combustion engines is known. It is proposed a device for afterburning of exhaust gases from internal combustion engines with a catalyst, for the oxidation of CO (carbon monoxide) and HC (hydrocarbons), in which in the upper load range of the internal combustion engine, a portion of the exhaust gas is passed bypassing a catalyst through an exhaust passage , wherein the catalyst in the exhaust passage, a second catalyst is arranged downstream.
  • A further education from the DE 28 51 675 A1 known Nachverbrennungsvorrichtung is described in the not yet published German patent application, with the official file number 10 2017 218 837.5. In this patent application, an internal combustion engine is described with an exhaust system having an exhaust manifold, which is connected to that of the internal combustion engine. In the exhaust system, a first and in the flow direction of the exhaust behind a second emission control system are arranged. The first exhaust gas purification system is bypassable via a bypass with a closure element, wherein the closure element is arranged in the exhaust manifold.
  • A generic internal combustion engine with an exhaust system is for example from the American patent application US 2011/0131978 A1 known.
  • For further technical environment is also on the German patent DE 10 2004 032 598 B4 and to the translation of the European Patent DE 697 23 307 T2 pointed.
  • In petrol engines, the fuel-air mixture is enriched (lambda <1) at high engine speeds and high power usually way to protect the exhaust gas-carrying components from thermal overload. This is especially true for supercharged internal combustion engines, in which the exhaust gas turbine and the catalyst could otherwise be destroyed by excessive exhaust gas temperatures.
  • The mixture enrichment leads to high CO concentrations in the exhaust gas and the CO is not oxidized disadvantageously in the catalyst due to the prevailing in the exhaust oxygen deficiency. The catalyst no longer works as a 3-way catalyst in this operating range because no stoichiometric mixture (lambda = 1) is set. This endangers the fulfillment of future approval requirements for motor vehicles.
  • Today's exhaust systems, in particular of turbocharged Otto internal combustion engines typically have a turbine bypass, also called waste gate, with adjustable exhaust gas mass flow through the waste gate. With this waste gate, the exhaust gas mass flow through the turbine and thus the turbine power and thus the desired boost pressure is set. After the turbine and after the supply of the waste gate channel to the main flow of the exhaust gas is typically as close as possible, to ensure a rapid heating after the start of the engine, a catalyst (also called close-coupled catalyst). When starting the engine, the waste gate is also wide open to direct as much hot exhaust gas directly to the close-coupled catalyst for heating.
  • In full load, at high power levels of the internal combustion engine, typically high exhaust gas mass flows (about 30 - 45%) have to be routed past the turbine via the waste gate. Since this exhaust gas is not expanded in the turbine, it is very hot. Thus, the average exhaust gas temperature after mixing turbine exhaust mass flow and wastegate exhaust mass flow is higher than the turbine exhaust temperature. It may exceed the maximum exhaust gas inlet temperature allowed for the catalyst. As a result, z. B. the performance of the internal combustion engine are throttled, which is not desirable.
  • The object of the present invention is to identify a measure with which higher specific powers of the internal combustion engine can be achieved without thermal damage to the catalyst close to the engine.
  • This object is solved by the features in the characterizing part of patent claim 1.
  • Advantageous developments of the invention are described in the subclaims.
  • Due to the inventive design of the internal combustion engine with the exhaust system significantly higher performance of the internal combustion engine can be achieved without thermal damage to the engine near catalyst. In order to ensure pollutant cleaning of the exhaust gas conducted through the waste gate, a second exhaust gas purification system is preferably provided in the first exhaust pipe.
  • With the embodiment according to claim 2, a controlled or regulated division of the exhaust gas mass flow can be displayed in order to avoid overheating of the first exhaust gas purification system after the turbine of the exhaust gas turbocharger.
  • In order to achieve the best possible emission control, a third emission control system is provided according to claim 3 in the exhaust system in the flow direction of the exhaust gas behind a junction of the first exhaust pipe.
  • In order to achieve the greatest possible variability in the heating behavior and with respect to the exhaust gas purification, a second shut-off element is preferably arranged in the first exhaust pipe in the flow direction of the exhaust gas behind the first shut-off element, the first exhaust pipe between the first and the second shut-off element with the exhaust system between the turbine housing and the first emission control system is connected via a fourth exhaust pipe exhaust gas leading.
  • In a further particularly preferred embodiment, a cooling device is provided for the fourth exhaust pipe according to claim 5, with the overheating of the first exhaust gas purification device is reliably avoided.
  • In a further particularly preferred embodiment, in the fourth exhaust pipe according to claim 6, a third shut-off 20 is provided, with which the second and the third exhaust pipe 8th . 9 can be shut off.
  • In the following the invention is explained in more detail with reference to six figures.
    • 1 shows a first embodiment of an internal combustion engine according to the invention with an exhaust system.
    • 2 shows a second embodiment of an internal combustion engine according to the invention with an exhaust system.
    • 3 shows a third embodiment of an internal combustion engine according to the invention with an exhaust system.
    • 4 shows a fourth embodiment of an internal combustion engine according to the invention with an exhaust system.
    • 5 shows a fifth embodiment of an internal combustion engine according to the invention with an exhaust system.
    • 6 shows a sixth embodiment of an internal combustion engine according to the invention with an exhaust system.
  • The following apply in the 1 to 6 for same components the same reference numbers.
  • 1 schematically shows an internal combustion engine according to the invention 1 with an exhaust system 3 , As is known in the art, fresh air is supplied via an intake silencer 15 sucked. An influx of fresh air is shown symbolically by an arrow. Subsequently, the fresh air through an unnumbered suction line through a compressor 16 an exhaust gas turbocharger 5 passed, and after the compressor 16 continue in a charge air cooler 17 cooled. After the intercooler 17 the fresh air flows through a throttle element 18 such as a throttle. After the throttle element 18 the fresh air enters an air collector 19 a, from which the fresh air in the present embodiment to four cylinders 2 is split. In these four cylinders 2 the fresh air is mixed with fuel and burned.
  • The exhaust gas flows per cylinder 2 via two unnumbered, each by a circle symbolically represented Gaswechselauslassventile in the exhaust system 3 out. Two cylinders each 2 are according to a cylinder order of the internal combustion engine 1 combined into a cylinder group. A typical firing order for a present four-cylinder internal combustion engine is, for example, cylinders 1 , Cylinder 3 , Cylinder 4 , Cylinder 2 , In this firing order, the cylinders form 1 and 4 and cylinders 2 and 3 one cylinder group each. Another possible firing order is cylinder 1 , Cylinder 2 , Cylinder 4 , Cylinder 3 , Here, the first cylinder (cylinder 1 ) of the power output side / clutch cylinder opposite.
  • The first cylinder group is via a second exhaust pipe 8th with a first scroll and the second cylinder group via third exhaust pipe 9 with a second scroll of the turbocharger 5 connected exhaust gas. The turbocharger 5 is thus a so-called twin-scroll turbocharger or an exhaust gas turbocharger with a segment turbine. However, the exhaust gas turbocharger can also be designed with a mono-scroll turbine. Through the second and the third exhaust pipe 8th . 9 becomes a turbine 4 the exhaust gas turbocharger 5 driven, the rotation with the compressor 16 is in operative connection and compacts the fresh air.
  • After the exhaust gas turbocharger 5 The exhaust gas flows through a first emission control system 6 (close-coupled catalyst) and leaves the exhaust system 3 in the present embodiment in the ambient air. In reality, in this case, a downstream exhaust system with optionally further exhaust gas purification devices, such. B. catalysts may be provided. A leakage of the exhaust gas from the exhaust system 3 is represented symbolically by an arrow.
  • Between the internal combustion engine 1 and the exhaust gas turbocharger 5 are the second and the third exhaust pipe 8th . 9 with a first exhaust pipe 7 connected exhaust gas, wherein the first exhaust pipe 7 in the flow direction of the exhaust gas after the first emission control system 6 back in the exhaust system 3 empties. At the crossing of the second exhaust pipe 3 and the third exhaust pipe 9 in the first exhaust pipe 7 is a first shut-off element 10 , such as As an exhaust valve, provided with the passage of exhaust gas from the second exhaust pipe 8th and the third exhaust pipe 9 in the first exhaust pipe 7 can be prevented. The shut-off element 10 is shown in a closed position.
  • At a full load of the internal combustion engine 1 becomes the first shut-off element 10 open, leaving hot exhaust gas on the turbine wheel 4 the exhaust gas turbocharger 5 can flow past, so that the first emission control system 6 but also the turbine 4 itself, is thermally spared. Due to the configuration of the invention now significantly higher full load capacity for the internal combustion engine 1 representable, since the first emission control system 6 and also the turbine 4 , by at the turbine 4 passed through exhaust gas mass flow, is thermally protected.
    • - Advantage: Temperature reduction before the first emission control system 6 at nominal power against. the mixing of the waste gas exhaust gas mass flow before the first emission control system 6 ,
    • - Disadvantage: Catheying takes longer because the waste gas exhaust gas mass flow can not contribute.
  • 2 shows a second embodiment of the internal combustion engine according to the invention 1 with the exhaust system 3 , 2 differs from 1 in that in the first exhaust pipe 7 a second emission control system 11 is arranged. Because the second emission control system 11 significantly further from the internal combustion engine 1 is arranged away as the first emission control system 6 , This is only flowed through by already cooled exhaust gas, so that a thermal overheating is largely excluded. Advantageously, the exhaust gases conducted through the wastegate are also purified in this way.
    • - Advantage: Temperature reduction before the first emission control system 6 at nominal power against. the admixing of the waste gas exhaust gas mass flow upstream of the first emission control system 6 ,
    • - Disadvantage: Catheying takes longer because the waste gas exhaust gas mass flow can not contribute.
  • 3 shows a third embodiment of the internal combustion engine according to the invention 1 with the exhaust system 3 , The internal combustion engine 1 in 3 differs from the internal combustion engine in 1 in that in the exhaust system 3 behind the junction of the first exhaust pipe 7 in the exhaust system 3 a third emission control system 12 is arranged. Also in this configuration, the exhaust gases conducted through the waste gate are passed through the third exhaust gas purification system 12 cleaned, the exhaust gases before entering the third emission control system 12 have already cooled down again and thus also a thermal protection for the third emission control system 12 is present.
  • 4 shows a fourth embodiment of the internal combustion engine according to the invention 1 with the exhaust system 3 , 4 different from the internal combustion engine 1 in the 1 to 3 in that now both the first emission control system 6 as well as the second emission control system 11 and also the third emission control system 12 in the exhaust system 3 are arranged. In this configuration, the best possible emission control is achieved, with simultaneous thermal protection for all emission control systems 6 . 11 . 12 , The emission control systems 6 . 11 . 12 For example, in all exemplary embodiments, three-way catalysts and / or particle filters and / or coated particle filters (four-way catalysts) and / or NOx storage catalysts and / or passive SCR catalysts or particle filters with SCR coating can be used.
    • - Advantage: Temperature reduction before the first emission control system 6 at nominal power against. the admixing of the waste gas exhaust gas mass flow upstream of the first emission control system 6 ,
    • - Disadvantage: Catheying takes longer because the waste gas exhaust gas mass flow can not contribute.
  • 5 shows a fifth embodiment of the internal combustion engine according to the invention 1 with the exhaust system 3 , The exhaust system 3 in 5 is different from the exhaust system in 4 in that in the first exhaust pipe 7 in the flow direction of the exhaust gas behind the first shut-off element 10 a second shut-off element 13 is arranged and the first exhaust pipe 7 between the first and the second shut-off element 10 . 13 exhaust gas leading with the exhaust system 3 between the turbine housing and the first emission control system 6 over a fourth exhaust pipe 14 connected exhaust gas. Both shut-off elements 10 . 13 are shown in a closed position. With this in 5 configuration shown is now the best possible variability for a thermally best possible allocation of the hot exhaust gas shown.
  • In a particularly preferred embodiment is for the fourth exhaust pipe 14 a cooling device, for example a connection to the coolant system of the internal combustion engine 1 intended.
    • - Advantage: Temperature reduction before the first emission control system 6 at nominal power against. the admixing of the waste gas exhaust gas mass flow upstream of the first emission control system 6 ,
    • - Catalyzing is possible via the Waste Gate Canal.
    • - Disadvantage: second shut-off element 13 in the hot area (tightness must be ensured).
  • 6 shows a sixth embodiment of the internal combustion engine according to the invention 1 with the exhaust system 3 , The exhaust system 3 in 6 differs from the exhaust systems in the 1 to 5 in that a first partial exhaust gas mass flow from the second and the third exhaust pipe 8th . 9 over the third shut-off element 20 and the fourth exhaust pipe 14 in the exhaust system 3 between the turbine 4 and the first emission control system 6 can be introduced and a second partial exhaust gas mass flow from the second and the third exhaust pipe 8th . 9 over the first shut-off element 10 and the first exhaust pipe 7 in the exhaust system 3 between the first emission control system 6 and the third emission control system 12 can be introduced. Both shut-off elements 10 . 20 are shown in a closed position.
  • The following operating modes are possible:
    • Partial load: second shut-off element 13 closed, boost pressure control via first shut-off element 10 , Katheizen on first shut-off 10 , Full load: first shut-off element 10 Closed, boost pressure control via second shut-off element 13 ,
      • - Advantage: Temperature reduction before the first emission control system 6 at nominal power against. the admixing of the waste gas exhaust gas mass flow upstream of the first emission control system 6 ,
      • - Katheizen is about the first shut-off 10 possible.
      • - Disadvantage: more elaborate exhaust manifold, two shut-off elements 10 . 13 , (Tightness must be ensured).
  • LIST OF REFERENCE NUMBERS
  • 1.
    Internal combustion engine
    Second
    cylinder
    Third
    exhaust system
    4th
    turbine
    5th
    turbocharger
    6th
    first emission control system
    7th
    first exhaust pipe
    8th.
    second exhaust pipe
    9th
    third exhaust pipe
    10th
    first shut-off element
    11th
    second emission control system
    12th
    third emission control system
    13th
    second shut-off element
    14th
    fourth exhaust pipe
    15th
    Ansauggeräuschdämpfer
    16th
    compressor
    17th
    Intercooler
    18th
    throttle element
    19th
    plenum
    20th
    third shut-off element

Claims (6)

  1. Internal combustion engine (1) with at least four cylinders (2) and with an exhaust system (3), wherein in the exhaust system (3) a turbine housing with a turbine wheel (4) of an exhaust gas turbocharger (5) and in the flow direction of an exhaust gas behind the turbine housing, a first emission control system (6) is arranged, between the internal combustion engine (1) and the turbine housing, a first exhaust pipe (7) leading exhaust branches and after the first emission control system (6) back into the exhaust system (3), wherein the exhaust gas turbocharger (5) has a twin -Scroll exhaust gas turbocharger or an exhaust gas turbocharger with a segmented turbine, wherein at least two cylinders (2) according to a firing order of the internal combustion engine (1) are combined to form a cylinder group and a first cylinder group via a second exhaust pipe (8) with a first scroll and a second cylinder group via a third exhaust pipe (9) leading to a second scroll exhaust gas is connected, wherein the first Abgasroh r (7) with the second and the third exhaust pipe (8, 9) exhaust leading is connectable, characterized in that in the first exhaust pipe (7), a second emission control system (11) is arranged.
  2. Internal combustion engine after Claim 1 , characterized in that in the first exhaust pipe (7) a first shut-off element (10) is arranged, with which the second and the third exhaust pipe (8, 9) can be shut off.
  3. Internal combustion engine according to one of Claims 1 or 2 , characterized in that in the exhaust system (3) in the flow direction of the exhaust gas behind a junction of the first exhaust pipe (7), a third emission control system (12) is arranged.
  4. Internal combustion engine according to one of Claims 2 or 3 characterized in that a second shut-off element (13) is arranged in the first exhaust pipe (7) in the flow direction of the exhaust gas behind the first shut-off element (10) and the first exhaust pipe (7) between the first and the second shut-off element (10, 13) exhaust gas leading with the exhaust system (3) between the turbine housing and the first exhaust gas purification system (6) via a fourth exhaust pipe (14) exhaust leading leader is connected.
  5. Internal combustion engine after Claim 4 , characterized in that a cooling device is provided for the fourth exhaust pipe (14).
  6. Internal combustion engine according to one of Claims 4 or 5 , characterized in that in the fourth exhaust pipe (14), a third shut-off element (20) is provided, with which the second and the third exhaust pipe (8, 9) can be shut off.
DE102018205768.0A 2018-04-17 2018-04-17 Internal combustion engine with an exhaust system Active DE102018205768B3 (en)

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DE102018205768.0A DE102018205768B3 (en) 2018-04-17 2018-04-17 Internal combustion engine with an exhaust system
PCT/EP2019/057175 WO2019201546A1 (en) 2018-04-17 2019-03-22 Internal combustion engine with an exhaust gas system

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