DE202017105126U1 - exhaust gas control system - Google Patents

Abstract

Exhaust-gas routing system (1) for a spark-ignited or self-igniting engine (2) with an exhaust pipe (2.3) connectable to an exhaust manifold (2.1) of the engine (2), with an intake pipe (2.4) connectable to an intake manifold (2.2) of the engine (2) ) and with a in the exhaust pipe (2.3) arranged turbine (3) having a inlet opening (3.3) having turbine housing (3.1) to which the exhaust pipe (2.3) connects, wherein an exhaust gas recirculation line (1.1) is provided in the inlet line (2.4) opens, and wherein the exhaust pipe (2.3) has at least one bypass line (3.2) which opens downstream of the turbine (3) in the exhaust pipe (2.3), and wherein the exhaust gas recirculation line (1.1) and the bypass line ( 3.2) upstream of the turbine (3) have a common branch line (13) and in the branch line (13) a particulate filter (13.2) with a particulate filter housing (13.3) is provided, wherein the exhaust gas recirculation line (1.1) and the bypass line (3.2) have a common separation piece (13.4) and are formed downstream of the separation piece (13.4) separately, characterized in that the branch line (13) on the turbine housing (3.1) or upstream of the turbine housing (3.1) branches off at the exhaust line (2.3) at a branch point (13.5), wherein a branch-valve arrangement (13.1) is provided, by means of which the branch line (13) can be opened or closed.

Description

The invention relates to an exhaust gas guidance system for a spark ignition or a self-igniting engine with an exhaust pipe connectable to an exhaust manifold of the engine, with an inlet pipe connectable to an intake manifold of the engine and with a turbine disposed in the exhaust pipe and having a turbine housing having an intake opening to which the further exhaust pipe is connected, wherein an exhaust gas recirculation line is provided, which opens in the inlet line of the engine, and wherein the exhaust pipe has at least one bypass line for the turbine, which branches off upstream of the turbine and opens downstream of the turbine into the exhaust pipe, and wherein the Exhaust gas recirculation line and the bypass line upstream of the turbine have a common branch line and in the branch line a particulate filter is provided with a particulate filter housing, wherein the exhaust gas recirculation line and the bypass line a common s have separation piece and are formed separately downstream of the separation piece.

From the DE 10 2009 014 277 A1 an exhaust gas recirculation system is known in which the exhaust gas recirculation line has an exhaust gas recirculation valve and in addition the exhaust gas recirculation line can be coupled via a directional valve to the fresh air line or the main exhaust gas line. A decoupling or decoupling of the turbine is not possible with the two aforementioned valves. The exhaust gas recirculation line also forms a bypass line for the exhaust gas turbine.

From the US 2008/0000226 A1 Also, an exhaust gas recirculation system is known in which the exhaust gas recirculation line is connected via a valve to the exhaust pipe. In addition, a two-stage turbine is provided, wherein the low pressure stage has a bypass line, which is controllable via a bypass valve.

From the US 9,551,286 B2 Also, an exhaust gas recirculation system is known, in which the exhaust gas recirculation line is coupled via a valve to the exhaust pipe. In addition, a bypass line for the exhaust gas turbine is provided, which is switchable via a separate valve.

From the DE 10 2015 108 224 A1 is an exhaust system with an exhaust gas turbine known, but without wastegate or bypass line for this purpose.

From the DE 10 2015 108 223 A1 an exhaust gas routing system with an exhaust gas turbine and a bypass line or a wastegate is known.

The object of the invention is to design and arrange an exhaust gas routing system for an engine in such a way that improved exhaust gas dynamics and improved heating of the exhaust gas purification modules in the cold start mode are achieved.

The object is achieved according to the invention in that the branch line branches off at the turbine housing or upstream of the turbine housing to or from the exhaust pipe at a branch point, wherein a branch-valve arrangement is provided, by means of which the branch line can be opened or closed.

Through the branch-valve arrangement, which is preferably placed near the inlet opening of the turbine housing or near the manifold outlet, in the low-end torque mode of the engine, the volume of the branch line and the volume of the adjoining EGR line and the volume the connected bypass line to the exhaust pipe are sealed off. With the foreclosure of this dead volume of any adverse collapse of the performance of the turbine is avoided.

In addition, during cold start operation of the engine, when the branch line is opened via the branch valve arrangement, the exhaust line can be closed via the branch valve arrangement, and thus the exhaust gas turbine can be sealed off. The exhaust gas can be passed via the branch line immediately upstream of the turbine directly into a small particle filter with catalytic coating. This can be heated up quickly and reach its light-off temperature. During the cold start of the engine, it is idling or at best in the range of low engine load, so that use of the turbine is not necessary. With the achievement of the light-off temperature can be promoted by the catalytic exothermic reaction on the filter surface and the regeneration effect of the particulate filter, which due to the oxidation of the particles in addition heat is generated. This can serve to heat the other exhaust system and in particular the downstream placed main 3-way catalyst. With this arrangement, the time to reach the light-off temperature of the catalysts can be significantly reduced, sometimes up to 90% compared to a conventional exhaust system without external turbine bypass.

During and after the engine start or engine cold start the turbocharger has not yet been charged, since the exhaust gas energy, in particular the exhaust pressure in these operating points is too low. On the contrary, the exhaust gas turbine represents a flow resistance that impairs engine operation. Therefore, the exhaust gas flow over the coated particulate filter of the EGR route and the Bypass line are completely or almost completely passed to the turbine over. The engine exhaust gas causes a faster heating of the catalyst coating of the particulate filter and thus an earlier conversion of unburned combustion products.

If more engine power is consumed starting from the idle range and the engine is in the low-end torque mode or in the load mode or the regulated boost mode, the turbine can be switched on again. At the desired time, the branch line can be opened and thus the exhaust gas recirculation line can be opened, as long as the engine does not come into the low end torque mode. The exhaust gas recirculation can be activated and regulated via the downstream EGR valve. In load operation, the bypass valve arrangement described below can be used as a wastegate valve. If the engine is in the low-end torque mode, the branch valve to the branch line is preferably closed.

The term manifold is used to describe any gas-combining element via which the gas flows to the engine or from the engine are distributed with respect to the individual cylinders.

Light-off is the time after engine start, during which the catalytic reaction within the catalyst takes place in the extent of at least 50%. The sooner this time comes after engine start, the cheaper or better is the conversion behavior of the catalyst. When cold starting, there is basically the problem of low temperatures of the catalyst and the associated loss of efficiency of the catalyst.

Although the heat provided by the engine via the exhaust gas flow serves to warm up the catalytic converter. But equally exhaust pipes and the exhaust gas turbine are warmed up. Therefore, it takes against the background of the limited amount of heat during cold start and the large masses aufheizenden long enough until the light-off temperature of the catalyst is reached.

The exhaust control system described here basically has an exhaust gas recirculation system (HP-EGR system) with an external turbine bypass system (wastegate function). An EGR system typically consists of at least one exhaust gas recirculation (EGR) line, one exhaust gas recirculation (EGR) cooler, and one exhaust gas recirculation (EGR) valve. The turbine bypass system consists of at least one bypass line located outside the turbine housing and a bypass valve.

In the context of this utility model application, a distinction is made between three operating zones of an engine, the cold start operation, the low end torque operation and the load operation. Cold start operation includes the low engine load range, even when the engine is at operating temperature and the turbine is not in use. The cold start operation could therefore also be referred to as "cold start and low load operation". In low-end torque mode, the turbine is in use, but gives due to the low exhaust energy only a limited recharging performance. In load operation, the exhaust gas energy is so great that it is sufficient to deliver the required turbine power or exceeds it.

• a) 3-Wege-Ventil in der Abzweigstelle von Abzweigleitung und Abgasleitung;
• b) Doppel-Ventil-Anordnung mit einem Haupt-Abzweig-Ventil in der Abzweigleitung und einem Neben-Abzweig-Ventil in der Abgasleitung;
• c) Einfach-Ventil-Anordnung mit einem Haupt-Abzweig-Ventil in der Abzweigleitung.

It may be advantageous for this purpose if the branch-valve arrangement is designed as

• a) 3-way valve in the branch point of branch line and exhaust pipe;
• b) a dual valve arrangement having a main branch valve in the branch line and a sub branch valve in the exhaust line;
• c) Single valve arrangement with a main branch valve in the branch line.

While variants a) and b) represent technical alternatives, variant c) is much simpler. Although the exhaust pipe can not be closed so. But this is then achieved by the bypass valve arrangement described below.

In connection with the design and arrangement according to the invention, it can be advantageous if an exhaust gas turbine outlet line with a flow cross-section A and at least one bypass valve arrangement are provided, wherein the bypass line and the exhaust gas turbine outlet line at the bypass valve arrangement medium or connect directly, via the bypass valve arrangement, the ratio between the exhaust gas flow rate of the bypass line and the exhaust gas turbine outlet is adjustable, via the bypass valve arrangement, the flow cross section A of the exhaust gas turbine outlet by at least 90%, ideally by 100% reduced is so that the exhaust gas turbine exhaust pipe is almost closed.

In low-end torque mode, when the turbine is used, the exhaust gas turbine exhaust pipe is opened via the bypass valve assembly with the bypass line closed via the bypass valve assembly. In load operation, the exhaust gas volume flow in the bypass line is regulated operating point-dependent via the bypass valve arrangement. The bypass line then takes over the wastegate function of the turbine. A turbine-internal wastegate valve can thus be omitted.

The combination of bypass line including bypass valve arrangement and exhaust gas recirculation line including EGR valve allows an increase of the exhaust gas flow rate in the bypass line or foreclosure of the turbine in cold start operation on the one hand and an independent control of the exhaust gas flow rate in the exhaust gas recirculation line on the other. Both the EGR valve and the bypass valve arrangement can be controlled independently of one another so that the exhaust gas volume flow guided over them can be controlled accordingly.

When the bypass line is opened, part of the exhaust gas flow past the turbine is guided into the branch line and thus the part of the exhaust gas flow guided through the exhaust gas turbine is reduced. Thus, the regeneration of the particulate filter in the branch line is seated in phases with closed EGR valve, such as in overrun and in open EGR valve phases, such as in lean operation.

By additionally connectable branch line with subsequent bypass line, a portion of the exhaust gas can be passed to the exhaust gas turbine over. In this case, the branch line with the bypass line also assumes the said function of a wastegate valve, as it has been integrated in conventional turbochargers in the housing of the turbine so far. An integral turbo wastegate valve is not excluded and may be provided in addition. Thus, the branch line with the bypass line and the EGR line can be used not only in cold start operation, but also in load operation when the exhaust gas energy exceeds the necessary drive energy for the compressor of the exhaust gas turbocharger. Also in this case, due to the residual oxygen contained in the exhaust gas and the high exhaust gas temperature of the particulate filter can be regenerated.

• a) 3-Wege-Ventil in der Anbindungsstelle von Bypass-Leitung und Abgasleitung;
• b) Doppel-Ventil-Anordnung mit einem Haupt-Bypass-Ventil in der Bypass-Leitung und einem Neben-Bypass-Ventil in der Abgasleitung;
• c) Einfach-Ventil-Anordnung mit einem Haupt-Bypass-Ventil in der Bypass-Leitung.

It can be advantageous in particular if the bypass valve arrangement is designed as

• a) 3-way valve in the connection point of bypass line and exhaust pipe;
• b) double valve arrangement with a main bypass valve in the bypass line and a bypass valve in the exhaust line;
• c) Single valve arrangement with a main bypass valve in the bypass line.

While variants a) and b) represent technical alternatives, variant c) is much simpler. Although the exhaust pipe can not be closed so. But this is then achieved by the branch-valve arrangement described above.

Either the inlet opening of the turbine housing via the branch-valve arrangement or via the sub-branch valve can be sealed off or, alternatively, the Abgasturbinenauslassleitung via the bypass valve arrangement or via the secondary bypass valve closable. Thus, in cold start operation, a very fast light-off of the catalyst in the branch line can be achieved.

It may advantageously be provided that the separation piece is formed as part of the particulate filter housing. Thus, a simple and a compact construction is guaranteed.

In addition, it may be advantageous if the inlet opening of the turbine housing has a diameter D and the branch valve arrangement or the branch valve or the branch point is arranged upstream or downstream with a distance d to the inlet opening, with d <= x and 1, 5 D <= x <= 4 D. The distance d should be a maximum of 500 mm. The smallest possible distance has the advantage that the exhaust gases entering the branch line are little cooled. When placed downstream, the branch valve assembly is provided on the turbine housing. The latter flanged separately or integrally as part of the turbine housing. The short distance is accompanied by a shorter reaction time of the EGR route. In addition, a smaller thermal parasitic mass, which must be heated in foreclosed exhaust gas turbine in cold start operation.

It may also be advantageous if the inlet opening of the turbine housing has a diameter D and the branch valve or the main branch valve is arranged at a distance a to the branch point, with a <= X and 1.0 D <= X < = 10 D. The smallest possible distance has the advantage that the dead volume in the branch line is as small as possible during cold start operation with the turbine shut off.

For this purpose, it may be advantageous if the particulate filter has a catalytically active coating for the conversion of CO, HC and NOx or the particulate filter has an SCR coating, by means of which NOx can be reduced. Thus, even in the cold start, when the entire exhaust gas flow is passed through the branch line, a cleaning of the exhaust gases ensured.

It may also be advantageous if downstream of the particulate filter, a cooler is provided within the exhaust gas recirculation line, which is structurally separate from the particulate filter or at least thermally separated from the particulate filter, and if in the exhaust gas recirculation line downstream of the radiator, an EGR valve is provided via that the volume flow in the exhaust gas recirculation line is adjustable. The cooler is spatially or at least thermally separated from the particle filter, so that the particulate filter has high temperatures possible in wide engine operating conditions so that it regenerates at sufficient excess oxygen in the exhaust gas by oxidation of the filtered components. This achieves the largest possible working range of the particle filter for regeneration. The radiator is designed either as an exhaust air, exhaust gas engine cooling water or exhaust gas low-temperature cooling water cooler. In particular embodiments, a plurality of exhaust gas recirculation coolers, which may also be switchable, may be arranged in series or in parallel.

Via the EGR valve, the exhaust gas mass flow can be set in the exhaust gas recirculation line depending on the operating point. The EGR valve is advantageously placed downstream of the particulate filter. In overrun phases of the engine, the EGR valve can be used to influence the regeneration of the particulate filter via the amount of recirculated fresh air. In addition, it may be advantageous if the EGR valve is provided downstream of the radiator. Thus, this is protected from excessive temperature load.

Furthermore, it can be advantageous if the exhaust gas turbine outlet line is guided through the particle filter housing. Thus, the exhaust control system is overall very compact formable.

It may also be advantageous if the exhaust gas recirculation line opens upstream or downstream of a compressor. Depending on the operating point, an HD EGR or an MD EGR are advantageous. The branching of the EGR line upstream of the turbine ensures higher exhaust gas temperatures, which have an overall positive effect on the particle filter regeneration and the pollutant reduction. The mouth downstream of the compressor has the advantage that the controlled system is shorter. However, a sufficiently high pressure gradient between the exhaust system and the intake system may not be available for supplying the desired amount of recirculated exhaust gas in all desired operating states. In the event that additional cooling of the recirculated exhaust gas is required, the purified exhaust gas can also be fed to the intake system after the compressor and before the intercooler. Thus, the exhaust gas is cooled not only in the EGR cooler, but also in the intercooler. Also conceivable is an arrangement in which the intercooler is designed so effectively that no EGR cooler in the EGR line is required for the recirculated exhaust gas.

The MD-EGR ensures a large pressure difference within the EGR line even for larger required exhaust gas recirculation quantities. However, this makes the controlled system longer than in the case of the HD EGR and the compressor and the turbine must be adapted to the changed mass flow rates if necessary.

The object is also achieved by an exhaust system and / or a motor with an exhaust system as described above.

• a) im Kaltstart-Betrieb des Motors die Abzweigleitung über die Abzweig-Ventil-Anordnung geöffnet ist und die Bypass-Leitung über die Bypass-Ventil-Anordnung geöffnet ist und ergänzend – die Abgasleitung über die Abzweig-Ventil-Anordnung geschlossen ist oder – die Abgasturbinenauslassleitung über die Bypass-Ventil-Anordnung geschlossen ist;
• b) im Low-End-Torque-Betrieb des Motors die Abgasturbinenauslassleitung über die Bypass-Ventil-Anordnung geöffnet ist, wobei die Abzweigleitung über die Abzweig-Ventil-Anordnung geschlossen ist oder wobei die Bypass-Leitung über die Bypass-Ventil-Anordnung geschlossen ist;
• c) im Lastbetrieb des Motors die Abzweigleitung über die Abzweig-Ventil-Anordnung geöffnet ist und der Abgasvolumenstrom in der Bypass-Leitung über die Bypass-Ventil-Anordnung betriebspunktabhängig geregelt ist und die Abgasturbinenauslassleitung über die Bypass-Ventil-Anordnung geöffnet ist.

The object is also achieved by a method for operating an engine with an exhaust gas routing system or an exhaust system as described above, in which

• a) in cold start operation of the engine, the branch line is opened via the branch-valve arrangement and the bypass line is opened via the bypass valve arrangement and in addition - the exhaust pipe is closed via the branch-valve arrangement or - the Exhaust gas turbine outlet is closed via the bypass valve assembly;
• b) in the low-end torque mode of the engine, the exhaust gas turbine outlet line is opened via the bypass valve arrangement, wherein the branch line is closed via the branch valve arrangement or wherein the bypass line is closed via the bypass valve arrangement is;
• c) in load operation of the engine, the branch line is opened via the branch-valve arrangement and the exhaust gas volume flow in the bypass line via the bypass valve arrangement is controlled operating point dependent and the exhaust gas turbine outlet line is opened via the bypass valve arrangement.

In cold start operation, bypassing of the turbocharger with simultaneous flow through the coated particle filter located in the EGR path is thus made possible without exhaust gas entering the inlet line of the engine. This achieves faster heating of the catalysts. In low-end torque mode, the volume in front of the turbine is kept small, whereby the starting behavior of the turbocharger at low speeds is promoted by the pressure pulsations that occur. In load operation can be regulated at excessively high exhaust gas energy for the turbine, the waste gas exhaust gas mass flow. At the same time, with the desired EGR operation, the EGR mass flow can be regulated.

• a) im Kaltstart-Betrieb und/oder im Low-End-Torque-Betrieb die Abgasrückführungsleitung über das AGR-Ventil geschlossen ist;
• b) im Lastbetrieb der Abgasvolumenstrom in der Abgasrückführungsleitung über das AGR-Ventil geregelt wird. Mit einer verbesserten AGR-Führung gehen verbesserte Abgaswerte einher.

Furthermore, it may be advantageous if

• a) in cold start operation and / or in low-end torque operation, the exhaust gas recirculation line is closed via the EGR valve;
• b) in load operation, the exhaust gas volume flow in the exhaust gas recirculation line is controlled via the EGR valve. Improved EGR management is accompanied by improved emissions.

Further advantages and details of the invention are in the protection claims and in Description explained and illustrated in the figures. Show it:

1 . 2 a schematic diagram of a HD EGR with bypass line;

3 a schematic diagram after 1 with MD-EGR;

4 a schematic diagram of the structure;

5 a schematic diagram of a motor map of an engine.

In all principle sketches after the 1 to 3 is shown an exhaust control system 1 (EGR system), which in the exhaust and charge air system of an engine 2 with exhaust manifold 2.1 and intake manifold 2.2 as well as with exhaust gas turbine 3 and charge air compressor 4 is integrated. The exhaust and charge air system has one to the exhaust manifold 2.1 of the motor 2 connected exhaust pipe 2.3 on, in which the turbine 3 is integrated. At the end of the exhaust pipe 2.3 leaves exhaust 7 the exhaust control system 1 and flows into the other, not shown exhaust route. In addition, one to the intake manifold 2.2 of the motor 2 connected inlet line 2.4 provided in the the compressor 4 is integrated. The inlet pipe 2.4 is via an unillustrated air supply system with fresh air 8th provided. In addition, at least one exhaust gas recirculation line 1.1 . 1.1 ' (EGR line) with an exhaust gas recirculation valve (EGR valve) 1.3 . 1.3 ' provided in the inlet pipe 2.4 empties. There is also a bypass line 3.2 for the turbine 3 provided, the downstream of the turbine 3 in the exhaust pipe 2.3 empties.

The exhaust gas recirculation line 1.1 and the bypass line 3.2 have a common branch line 13 on, wherein in the branch line 13 a particle filter 13.2 with a particle filter housing 13.3 is provided. The branch line 13 points in the area after the exhaust manifold 2.1 a branch point 13.5 on. Downstream of the particulate filter 13.2 have the exhaust gas recirculation line 1.1 and the bypass line 3.2 a common separator 13.4 on and are downstream of the separator 13.4 trained separately.

In the branch line 13 is the particle filter 13.2 arranged, which is the recirculated or recirculated exhaust gas 7 filters. The particle filter 13.2 has a catalytic coating for the conversion of CO, HC and / or NOx, such as a 3-way catalyst, an SCR catalyst or an oxidation catalyst.

Further, in the EGR line 1.1 downstream of the particulate filter 13.2 at least one EGR cooler 1.2 intended. Downstream of the respective EGR cooler 1.2 or in front of the mouth into the inlet line 2.4 is an EGR valve 1.3 . 1.3 ' for regulating the mass flow within the EGR line 1.1 placed.

In the inlet pipe 2.4 is a charge air or fresh air throttle 2.6 upstream of the discharge point of the exhaust gas recirculation line 1.1 in the inlet pipe 2.4 intended. This part of the inlet pipe 2.4 is also called fresh air pipe 2.4a designated. The part of the inlet pipe 2.4 downstream of the point of introduction of the exhaust gas recirculation line 1.1 is also called charge air duct 2.4b designated. Inside the fresh air line 2.4a is also a fresh air cooler 6 intended. Additionally or alternatively, within the charge air line 2.4b a charge air cooler 2.5 intended.

Downstream of the turbine 3 is in the exhaust pipe 2.3 a main catalyst 5 provided, which may also be configured as a 3-way catalyst, as an SCR catalyst or as an oxidation catalyst.

Basically, a distinction is made between two variants of the exhaust gas recirculation depending on the branching of the EGR line 1.1 from the exhaust pipe 2.3 and the mouth of the EGR pipe 1.1 in the inlet pipe 2.4 , The combination of branching of the EGR line 1.1 upstream of the turbine 3 and mouth of the EGR pipe 1.1 downstream of the compressor 4 is referred to as high pressure EGR (HD-EGR). The combination of branching of the EGR line 1.1 upstream of the turbine 3 and mouth of the EGR pipe 1.1 upstream of the compressor 4 is referred to as maximum pressure EGR (MD-EGR).

In the diagram after 1 and 2 a HD EGR is shown formed by the EGR pipe 1.1 that are upstream of the turbine 3 branches off and the downstream of the compressor 4 empties. The mouth is downstream of the charge air or fresh air throttle 2.6 ,

In the embodiment according to 3 are combined a HD-AGR and an MD-AGR. Downstream of the radiator 1.2 Branches the EGR line 1.1 and discharges both upstream and downstream of the compressor 4 , In the respective AGR line 1.1 . 1.1 ' is an EGR valve 1.3 . 1.3 ' intended. Instead of the two EGR valves 1.3 . 1.3 ' can according to the dashed alternative 1 . 2 Also find a 3-way valve application, by which the ratio between the exhaust gas flow rate of both EGR lines 1.1 . 1.1 ' is adjustable.

According to embodiment 1 branches the branch line 13 at a branch point 13.5 from the exhaust pipe 2.3 from. Within the branch line 13 is a branch valve arrangement 13.1 in Shape of a branch valve 13.1 provided via which the branch line 13 can be opened or closed. In contrast, in the embodiment according to 2 the branch valve arrangement 13.1 designed as a 3-way valve, wherein the 3-way valve, the branch point 13.5 forms. Via the 3-way valve can also the branch line 13 be opened or closed. In addition, the exhaust pipe 2.3 closed or the exhaust gas turbine are sealed off.

Alternatively to the design as a 3-way valve can (dashed lines) as a branch-valve arrangement 13.1 also find a double valve arrangement application with a main branch valve 13.1a in the branch line 13 and a sub branch valve 13.1b in the exhaust pipe 2.3 , The ratio between the waste gas volume flow of the branch line is via the 3-way branch valve 13 and the exhaust gas turbine exhaust pipe 3.4 or the exhaust pipe 2.3 adjustable.

According to embodiment 1 open the exhaust pipe 2.3 and the bypass line 3.2 in a bypass valve arrangement 3.5 , which is designed as a 3-way valve. About the bypass valve arrangement 3.5 is the ratio between the exhaust gas volume flow of the bypass line 3.2 and the exhaust gas turbine exhaust pipe 3.4 adjustable and is in the other exhaust pipe 2.3 derived. In addition, the Abgasturbinenauslassleitung 3.4 through the bypass valve assembly 3.5 closed, thus the turbine be sealed off.

Alternatively to the design as a 3-way valve can (dashed lines) as a branch-valve arrangement 3.5 also find a double valve arrangement application with a main bypass valve 3.5a in the bypass line 3.2 and a by-pass valve 3.5b in the exhaust pipe 2.3 ,

According to embodiment 2 is just a bypass valve 3.5 in the bypass line 3.2 provided, via which the exhaust gas flow in the bypass line 3.2 is controllable.

The embodiments according to 1 and 2 With respect to the architecture of the aforementioned valve assemblies, alternatives are alternatives. When the branch valve assembly 13.1 is designed as a 3-way valve or as a double-valve arrangement, it is necessary for the bypass valve arrangement 3.5 just a simple bypass valve 3.5 , When the bypass valve assembly 3.5 is designed as a 3-way valve or as a double-valve arrangement, it is necessary for the branch-valve arrangement 13.1 just a simple branch valve 13.1 ,

The embodiment according to 3 goes back to the characteristics of the valve arrangement 3.5 . 13.1 on 1 , To 3 the already mentioned MD-AGR is provided in addition.

This design of MD-AGR is also for the embodiment according to 2 and the existing there form of branch-valve arrangement 13.1 and bypass valve arrangement 3.5 possible.

The basic structure of the exhaust system is in the 4a . 4b shown. In both alternatives is a turbine 3 with a turbine housing 3.1 as well as an entrance opening 3.3 provided, to which a further exhaust pipe 2.3 or an exhaust outlet of the engine can be connected. To the turbine housing 3.1 closes an exhaust gas turbine exhaust pipe 3.4 as part of the exhaust pipe 2.3 at. In the area of the entrance opening 3.3 is the branch line 13 provided at the branch point 13.5 directly via the branch valve arrangement 13.1 is connected, over which it can be opened or closed. The branch line 13 flows into the particle filter 13.2 or a particle filter housing 13.3 , The exhaust side provides the particulate filter housing 13.3 a separator 13.4 to which the exhaust gas recirculation line 1.1 as well as the bypass line 3.2 connect. While the exhaust gas recirculation line 1.1 leads to a not further shown EGR valve, the bypass line opens 3.2 together with the exhaust gas turbine exhaust pipe 3.4 in a bypass valve arrangement 3.5 , about which the ratio of the exhaust gas flow between both lines 3.2 . 3.4 is controllable. About the bypass valve arrangement 3.5 the exhaust gas flow leads into the further exhaust pipe connected to it 2.3 ,

The branch valve arrangement 13.1 or the branch point 13.5 point to the inlet opening 3.3 a distance d which is about as large as the diameter D of the inlet opening 3.3 ,

The branch valve arrangement 13.1 is directly on the turbine housing 3.1 provided or arranged. Alternatively (dashed line) is a branch valve 13.1 provided that a distance a to the branch point 13.5 having. This distance should be as low as possible and is the embodiment 4a about as large as the diameter D of the inlet opening 3.3 ,

According to an alternative embodiment (not shown), the structure differs from the embodiment 4 in that the exhaust gas turbine line 3.4 through the particle filter housing 13.3 is guided so that the exhaust gas turbine line 3.4 from the particulate filter housing 13.3 is surrounded.

To 5 is a typical engine map of a turbocharged engine, where the load is above the speed. The engine map is divided into three areas A, B, C. The area A at low load is called cold start operation. The exhaust gas turbine is not in operation there. Above area A, two areas B and C are indicated. Area B is the low-end torque area, while area C is called the load area. In both areas B, C, the exhaust gas turbine is in operation.

In cold start mode A are the branch line 13 and the bypass line 3.2 opened while the exhaust pipe 2.3 , thus the turbine, foreclosed and the EGR line are closed. In the low-end torque mode B of the engine is the branch line 13 and thus also the EGR line 1.1 as well as the bypass line 3.2 closed while the exhaust pipe 2.3 to operate the turbine is open. In the load range C are both the branch line 13 , hence the bypass line 3.2 as well as the EGR line 1.1 and also the exhaust pipe 2.3 open. Both the exhaust gas flow in the bypass line 3.2 as well as the exhaust gas flow in the EGR line 1.1 be through the appropriate valve 3.5 . 1.3 regulated.

LIST OF REFERENCE NUMBERS

1

Exhaust system / exhaust control system

1.1

Exhaust gas recirculation line, EGR line

1.1 '

Exhaust gas recirculation line, EGR line

1.2

Radiator, EGR cooler

1.3

AGR valve

1.3 '

AGR valve

2

engine

2.1

exhaust manifold

2.2

intake manifold

2.3

exhaust pipe

2.4

inlet line

2.4a

Fresh air line

2.4b

Turbo pipe

2.5

Intercooler

2.6

Charge air throttle, fresh air throttle

3

(Exhaust) turbine

3.1

turbine housing

3.2

Bypass line

3.3

inlet opening

3.4

Abgasturbinenauslassleitung

3.5

Bypass valve assembly, bypass valve

3.5a

Main bypass valve

3.5b

In addition bypass valve

4

Compressor, charge air compressor

5

Catalyst, 3-way catalyst, SCR catalyst, oxy-catalyst

6

Fresh air coolers

7

exhaust

8th

fresh air

13

Branch line for 1.1 and 3.2

13.1

Branch valve assembly, branch valve

13.1a

Main branch valve

13.1b

In addition to branch valve

13.2

particulate Filter

13.3

particulate filter housing

13.4

separation pieces

13.5

branching point

A

Flow area

a

distance

D

diameter

d

distance

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102009014277 A1 [0002]
• US 2008/0000226 A1 [0003]
• US 9551286 B2 [0004]
• DE 102015108224 A1 [0005]
• DE 102015108223 A1 [0006]

Claims (12)

Exhaust control system ( 1 ) for a spark-ignited or a self-igniting engine ( 2 ) with one to an exhaust manifold ( 2.1 ) of the motor ( 2 ) connectable exhaust pipe ( 2.3 ), with one to an intake manifold ( 2.2 ) of the motor ( 2 ) connectable inlet line ( 2.4 ) and with one in the exhaust pipe ( 2.3 ) arranged turbine ( 3 ) with an entrance opening ( 3.3 ) turbine housing ( 3.1 ), to which the exhaust pipe ( 2.3 ), wherein an exhaust gas recirculation line ( 1.1 ) provided in the inlet duct ( 2.4 ), and wherein the exhaust pipe ( 2.3 ) at least one bypass line ( 3.2 ) downstream of the turbine ( 3 ) in the exhaust pipe ( 2.3 ), and wherein the exhaust gas recirculation line ( 1.1 ) and the bypass line ( 3.2 ) upstream of the turbine ( 3 ) a common branch line ( 13 ) and in the branch line ( 13 ) a particle filter ( 13.2 ) with a particle filter housing ( 13.3 ) is provided, wherein the exhaust gas recirculation line ( 1.1 ) and the bypass line ( 3.2 ) a common separator ( 13.4 ) and downstream of the separator ( 13.4 ) are formed separately, characterized in that the branch line ( 13 ) on the turbine housing ( 3.1 ) or upstream of the turbine housing ( 3.1 ) on the exhaust pipe ( 2.3 ) at a branch point ( 13.5 ), wherein a branch-valve arrangement ( 13.1 ) is provided, by means of the branch line ( 13 ) can be opened or closed. Exhaust control system ( 1 ) according to claim 1, characterized in that the branch-valve arrangement ( 13.1 ) is designed as a) 3-way valve in the branch point ( 13.5 ) of branch line ( 13 ) and exhaust pipe ( 2.3 ); b) double valve arrangement with a main branch valve ( 13.1a ) in the branch line ( 13 ) and a secondary branch valve ( 13.1b ) in the exhaust pipe ( 2.3 ); c) single valve arrangement with a main branch valve ( 13.1 ) in the branch line ( 13 ). Exhaust control system ( 1 ) according to claim 1 or 2, characterized in that an exhaust gas turbine exhaust pipe ( 3.4 ) with a flow cross section A and at least one bypass valve arrangement ( 3.5 ) are provided, wherein the bypass line ( 3.2 ) and the exhaust gas turbine exhaust pipe ( 3.4 ) at the bypass valve arrangement ( 3.5 ) via the bypass valve arrangement ( 3.5 ) the ratio between the exhaust gas volume flow of the bypass line ( 3.2 ) and the exhaust gas turbine exhaust pipe ( 3.4 ) is adjustable, via the bypass valve arrangement ( 3.5 ) the flow cross section A of the exhaust gas turbine outlet line ( 3.4 ) is reducible by at least 90%. Exhaust control system ( 1 ) according to claim 3, characterized in that the bypass valve arrangement ( 3.5 ) is designed as a) 3-way valve in the connection point of bypass line ( 3.2 ) and exhaust pipe ( 2.3 ); b) double valve arrangement with a main bypass valve ( 3.5a ) in the bypass line ( 3.2 ) and a by-pass valve ( 3.5b ) in the exhaust pipe ( 2.3 ); c) Single valve arrangement with a main bypass valve ( 3.5 ) in the bypass line ( 3.2 ). Exhaust control system ( 1 ) according to one of the preceding claims, characterized in that the separating piece ( 13.4 ) as part of the particulate filter housing ( 13.3 ) is trained. Exhaust control system ( 1 ) according to one of the preceding claims, characterized in that the inlet opening ( 3.3 ) of the turbine housing ( 3.1 ) has a diameter D and the branch-valve arrangement ( 13.1 ) or the branch valve ( 13.1 ) or the branch point ( 13.5 ) upstream or downstream with a distance d to the inlet opening ( 3.3 ), with d <= x and 1.5 D <= x <= 4 D. Exhaust control system ( 1 ) according to one of the preceding claims, characterized in that the inlet opening ( 3.3 ) of the turbine housing ( 3.1 ) has a diameter D and the branch valve ( 13.1 ) or the main branch valve ( 13.1a ) with a distance a to the branch point ( 13.5 ), with a <= X and 1.0 D <= X <= 10 D. Exhaust control system ( 1 ) according to one of the preceding claims, characterized in that the particulate filter has a catalytic coating for the conversion of CO, HC and NOx or that the particulate filter has an SCR coating, by means of which NOx is reducible. Exhaust control system ( 1 ) according to one of the preceding claims, characterized in that downstream of the particulate filter ( 13.2 ) a cooler ( 1.2 ) within the exhaust gas recirculation line ( 1.1 ) is provided, the structurally separate from the particulate filter ( 13.2 ) is executed or at least opposite the particulate filter ( 13.2 ) is thermally separated, and that in the exhaust gas recirculation line ( 1.1 ) downstream of the radiator ( 1.2 ) an EGR valve ( 1.3 ) is provided, via which the volume flow in the exhaust gas recirculation line ( 1.1 ) is adjustable. Exhaust control system ( 1 ) according to one of the preceding claims, characterized in that the exhaust gas turbine outlet pipe ( 3.4 ) through the particulate filter housing ( 13.3 ) is guided. Exhaust control system ( 1 ) according to one of the preceding claims, characterized in that the exhaust gas recirculation line ( 1.1 ) upstream or downstream of a compressor ( 4 ) opens. Exhaust system and / or engine ( 2 ) with an exhaust gas routing system ( 1 ) according to one of the preceding claims.

Images