DE102008049091A1 - Method for operating internal combustion engine, involves integrating exhaust gas flows of each of two cylinders of cylinder bank having four cylinders in exhaust pipe - Google Patents

Abstract

The method involves integrating the exhaust gas flows of each of the two cylinders (3,3.1,3.2,3.3,3.4,3.5,3.6,3.7,3.8) of the cylinder bank (A,B,13) having four cylinders in an exhaust pipe (15). The two exhaust pipes of the respective cylinder bank are separated from each other to which an exhaust-gas turbocharger (4) assigned to the respective cylinder bank is guided. An independent claim is included for an internal combustion engine with an exhaust gas assembly.

Description

The The invention relates to a method for operating an internal combustion engine with eight cylinders arranged in two V-shaped cylinder banks are having a cross crankshaft and the at least one Exhaust gas turbocharger has.

The The invention further relates to such an internal combustion engine.

In internal combustion engines in V8 design, so-called V8 engines, a so-called crankshaft crankshaft is preferably used in which the four crankcurves, for example, continuously with 90 °, 180 °, 90 ° to each other are rotated, and wherein each a crank with the connecting rods of two opposite Cylinders are connected. Thus, a perfect balance of the rotating and oscillating masses of the crank mechanism can be realized when the angle between the cylinder rows is 90 °, the ignition order for the entire engine is even 90 ° (relative to the crankshaft angle), whereby a uniform output torque is ensured. For the firing order of the eight cylinders in the firing interval of 90 °, relative to the total engine, there are four firing sequences (given the direction of rotation and given numbering of the cylinders, in which the cylinder banks each have four cylinders and the cylinders of a bank from the front end with 1 to 4 and those of the other bank are numbered 5 to 8 from the front end), which are 1-5-4-8-6-3-7-2; 1-5-4-2-6-3-7-8; 1-5-7-2-6-3-4-8; 1-3-7-2-6-5-4-8. Here, ignite the four cylinders of a row of cylinders not at a uniform 180 ° intervals, as in a four-cylinder in-line engine, but at intervals of 90 ° -180 ° -270 ° -180 °. This results in a common exhaust manifold each cylinder bank to an overlap of about 200 ° to 220 ° continuous exhaust phases of two working at 90 ° distance cylinder. The exhaust pressure surge of the subsequent cylinder obstructs the outflow of the preceding or leads to the backflow and increases the exhaust gas residual volume in the faulty cylinder. When exhaust turbocharging this unwanted process is particularly pronounced due to the increased exhaust backpressure. Another disadvantage is the mitigation of the exhaust pressure surge, which degrades the rapid response of the turbocharger during a load change. From the publications DE 10 2006 042 443 A1 and DE 10 2006 042 464 A1 are known V-engines with eight cylinders and exhaust turbocharger, in which the exhaust gas streams are combined into two separate groups of four cylinders, the cylinders within a group have a firing interval of 180 ° and each group is separately connected to at least one turbine inlet channel. The reciprocal charge exchange disturbances of two cylinders are thereby not prevented, unless the summary is such that two cylinders are combined from the one cylinder bank with two cylinders from the other cylinder bank, but this is a complex and voluminous exhaust pipe design with undesirably high thermal capacity brings with it. Such a large volume is disadvantageous for the dynamics of charging, in particular, the high thermal capacity is also unfavorable for the effectiveness of catalytic exhaust gas cleaning systems. The connections between the cylinder banks require expensive thermal expansion compensators, so that the thermal expansion of the hot exhaust pipes does not lead to unacceptable stresses between the cylinder banks. Next, the shutdown of individual cylinders or subsets of cylinders in partial load operation is difficult. In particular, the independent supply of disconnected and operating cylinders spiral channels of a turbine housing of an exhaust gas turbocharger has the consequence that at cylinder shutdown the exhaust pipes to the turbine and the turbine housing itself are heated very different and there are harmful component voltages due to the different thermal expansions. Due to the ignition sequences described above would have to be ignited in torsional vibration and comfort reasons in the uniform 180 ° distance in a V8 engine in the V8 engine, which is why only a summary, as described above, from two cylinders of the two cylinder groups can be made into a four-cylinder group , which brings the mentioned thermal problems.

task the invention is to provide a V8-type internal combustion engine, the sake of vibration and comfort a cross crankshaft has, for performance reasons an exhaust gas turbocharger owns and for exhaust and consumption reduction with a temporary Cylinder shutdown can be operated, as well as providing a method of operating such an internal combustion engine.

For this purpose, a method for operating an internal combustion engine with eight cylinders is proposed, which are arranged in two V-shaped cylinder banks, which has a cross crankshaft and which has an exhaust gas turbocharger for at least each of the two cylinder banks. It is provided that the exhaust gas flows are combined by two cylinders of the four cylinders each having cylinder banks each in an exhaust pipe and that the two exhaust pipes of the respective cylinder bank are separated from each other to the respective cylinder bank associated exhaust gas turbocharger. The exhaust gas flows of the respective cylinder banks are thus zusammenge together sums up that each two cylinders of each cylinder bank each act on an exhaust pipe and the other two cylinders of the same cylinder bank another exhaust pipe. Overall, this results in four exhaust groups, namely two per cylinder bank. The four exhaust groups are then led to the exhaust gas turbochargers, namely in such a manner that each of the exhaust pipes of a cylinder bank are separated from each other on the exhaust gas turbocharger associated with the respective cylinder bank. In each case, two cylinders of each cylinder bank therefore have a common exhaust pipe, through which the exhaust gases are guided just this cylinder to the respective associated exhaust gas turbocharger.

In a further embodiment of the method is provided that at least one cylinder of each of the exhaust pipes associated cylinder can be turned off during operation of the internal combustion engine. It is Consequently, possible during operation of the engine cylinder individually or in groups, in such a way Way that a shutdown within the exhaust groups (namely of cylinders, each one of the exhaust pipes assigned) can take place. In particular, thus, a non-uniform Cooling and an undesirable torque change by non-uniform exhaust gas charging of the turbocharger each cylinder bank be avoided.

In Another procedural training, the two exhaust pipes each cylinder bank in each case to the associated exhaust gas turbocharger assigned to this cylinder bank. Both exhaust pipes of each cylinder bank, as described above, the individual turn-off cylinder Accordingly, are assigned to the exhaust gas turbocharger, the the cylinder bank is assigned as such.

In Further training is provided that at least one of the exhaust gas turbocharger with respect to the exhaust system has switchable and / or controllable exhaust gas turbine, depending on switched from an operating state of the internal combustion engine or is regulated. As operating condition of the internal combustion engine comes in particular a load condition into consideration. Depending on this is at least one of the exhaust gas turbochargers with regard to the exhaust system switched or regulated, the exhaust gas turbine being designed is that the circuit or regulation with regard to the exhaust system is possible. In particular, this is the case with so-called Twinscroll exhaust gas turbines, the two turbine housing in a spiral shape have, which jointly or individually / mutually subjected to exhaust gas can be and the exhaust through a turbine housing, both turbine housings or alternately the exhaust gas turbine feed, preferably selected a turbine geometry is, with respect to the exhaust gas supply over both turbine housings, one of the turbine housing or alternately one of the two turbine housing one different power delivery and / or a different one Efficiency has. The regulation or control happens here by an actuator, the appropriate control or adjusting elements in cooperation with the exhaust gas turbocharger or in the exhaust gas turbocharger, in particular the Exhaust gas supply of the exhaust gas turbine of the exhaust gas turbocharger, actuated. Preferably, the circuit or control by means of the actuator caused by a control unit of the internal combustion engine or, as previously known from the prior art, via vacuum cans.

In a training course is the circuit or regulation of Exhaust gas turbine of one of the exhaust pipes of the cylinder bank used. In this case, it is provided in particular, the exhaust pipe of the cylinder bank so form the exhaust flow that passed through the exhaust pipe is, for example via a valve assembly in the area the exhaust gas turbine connected to the other exhaust pipe of the same cylinder bank can be. In particular, it is provided that the exhaust gas flow of an exhaust pipe, a turbine housing of the exhaust gas turbine charged, while the exhaust pipe of the other cylinder tube the other turbine housing applied (Twinscroll arrangement). In this case, the exhaust gas volume flow of the one exhaust pipe is preferred in the field of Twinscroll arrangement also the one turbine housing assigned, so that both exhaust streams only one turbine housing be assigned.

The Introduction of the exhaust gas flow into the exhaust gas turbine is therefore via two spiral channels, each one of the exhaust pipes of the Cylinder bank in each case a spiral channel or both exhaust pipes in a spiral channel, in particular the same spiral channel, passed become.

In a further process training is a cylinder shutdown such that in each case one cylinder per exhaust pipe is switched off.

Prefers the cylinder deactivation takes place such that, based on the Internal combustion engine as a total engine, a cylinder deactivation of four which gives eight cylinders with a firing angle of 180 °. The ignition angle among the other, in operation Cylinders are therefore 180 °, resulting in a very good balance of moments and oscillating masses. Also When cylinder deactivation is therefore no loss of comfort the V8 arrangement.

Further, an internal combustion engine with eight cylinders is proposed, which are arranged in two V-shaped cylinder banks, the a crankshaft having a 0 ° -, 90 ° -, 180 ° -, 90 ° -Kraft sequence and has at least one exhaust gas turbocharger. It is provided that in each case two cylinders of a cylinder bank are combined to form an exhaust group in an exhaust pipe, wherein the two exhaust pipes of the respective cylinder bank are guided separately from each other to the exhaust gas turbocharger, and wherein at least one cylinder of each of the exhaust pipes associated cylinder is switched off.

Prefers is provided that each cylinder bank each have an exhaust gas turbocharger assigned.

Further is preferably provided that the two exhaust pipes of each cylinder bank each of the cylinder bank respectively associated exhaust gas turbocharger assigned. The exhaust pipes of each cylinder bank open Consequently, in the exhaust gas turbocharger, just this cylinder bank assigned. Accordingly, the exhaust groups described above become per cylinder bank in the assigned exhaust gas turbocharger over led the exhaust pipes.

In In another embodiment, at least one of Exhaust gas turbocharger switchable with respect to the exhaust system and / or controllable exhaust gas turbine. This is especially so-called Twinscroll turbines the case, which has an exhaust system in Provide separate spiral channels, with the separate spiral channels individually or together with exhaust gas can be applied. In particular, it is provided that each spiral channel a Exhaust pipe is assigned to the respective cylinder bank, and that the Exhaust duct of each exhaust pipe in the region of the exhaust gas turbine can be switched or regulated.

Further is provided that the engine cylinder with a firing order 1-5-4-8-6-3-7-2 having. In such a firing order can be with a cross crankshaft even in the shutdown mode, as proposed achieve a particularly quiet operation.

Further it is envisaged that the cylinder deactivation one the cylinders 5-8-3-2 and / or the cylinder 1-4-6-7 comprehensive cylinder group detected.

Further advantageous embodiments will become apparent from the dependent claims as well as combinations of the same.

For details, show the embodiments.

The Invention will be described below with reference to embodiments described in more detail, but without being limited thereto to be.

It demonstrate

1 a V8 engine with two turbochargers and two exhaust groups per cylinder bank with Zylinderabschaltemöglichkeit and

2 Such an engine with two switchable exhaust gas turbochargers (Twinscroll) with Zylinderabschaltemöglichkeit.

1 shows an internal combustion engine 1 namely a V8 engine 2 , with two cylinder banks 13 namely, a first cylinder bank A and a second cylinder bank B, wherein the first cylinder bank A is the cylinder 3.1 . 3.2 . 3.3 and 3.4 and the second cylinder bank B is the cylinder 3.5 . 3.6 . 3.7 and 3.8 , The internal combustion engine 1 has as a V8 engine 2 namely the eight cylinders 3.1 to 3.8 , Between the cylinder banks A and B are two exhaust gas turbochargers 4 arranged, each with a compressor 5 and an exhaust gas turbine 6 have, wherein the exhaust gas turbines 6 Twin-scroll turbines 7 are, so those, each two turbine housing 8th have, which surround a turbine wheel, not shown here, a spiral for the purpose of exhaust gas supply. Between the cylinder banks 13 one is here only schematically as symmetry axis 9 illustrated crankshaft 10 arranged, namely a cross crankshaft 11 , The two cylinder banks 13 namely, the first cylinder bank A and the second cylinder bank B constitute the whole engine 12 out. The crankshaft has a bend sequence of 0 °, 90 °, 180 °, 90 °. The total engine 12 has a firing order 1-5-4-8-6-3-7-2, whereby the cylinder 3.1 . 3.5 . 3.4 . 3.8 . 3.6 . 3.3 . 3.7 and 3.2 fire one after the other, each at a firing interval of 90 °. The cylinders 3 each cylinder bank 13 , That is, the first cylinder bank A and the second cylinder bank B are respectively such exhaust groups 14 summarized that each two cylinders 3 each cylinder bank 13 together an exhaust group 14 form, by in a gas pipe from 15 be summarized. Every exhaust pipe 15 acts on an exhaust gas turbocharger 4 such that it is a separate segment of the twin scroll turbine 7 applied. Accordingly, with regard to the first cylinder bank A, it is possible to distinguish an exhaust gas group A ₁ and an exhaust gas group A ₂ , correspondingly with respect to the second cylinder bank B an exhaust gas group B ₁ and an exhaust gas group B ₂ . The exhaust group A ₁ is formed here by the cylinders 3.1 and 3.3 , the exhaust group A ₂ from the cylinders 3.2 and 3.4 while the exhaust group B _{1 is} formed by the cylinders 3.5 and 3.6 and the exhaust group B ₂ from the cylinders 3.7 and 3.8 , In operation with cylinder deactivation 16 is therefore at the stated firing order of the entire engine 12 one cylinder each of each exhaust group 14 shut off, namely the cylinders 3.2 the exhaust group A ₂ , 3.3 the exhaust group A ₁ , 3.5 the exhaust group B ₁ and 3.8 the exhaust group B ₂ . Of course, in particular alternately and / or alternatively, also a cylinder deactivation by means of the cylinder 3.1 . 3.4 ., 3.6 and 3.7 realize, in particular to an undesirable uneven cooling of the entire engine 12 to avoid. In the exemplary cylinder shutdown shown 16 results, based on the total engine 12 , a remaining firing order of 3.1 . 3.4 . 3.6 and 3.7 so that the cylinders in operation 3.1 . 3.4 . 3.6 and 3.7 each at a distance of 180 ° ignite. This results in combination with the cross crankshaft 11 a uniform output torque without any loss of comfort with significant reduction in fuel consumption. At the same time undesirable overlaps of the exhaust phases of the working cylinders are avoided, so that the exhaust gas pressure surge of the respectively subsequently ignited cylinder does not hinder the outflow of the preceding or even leads to a backflow of residual exhaust gas volume into the disturbed cylinder. At the same time there is a sufficiently high exhaust gas pressure surge to the exhaust gas turbocharger 4 To move too fast response to load changes. The proposed summary of the exhaust gas flows of the cylinder, the exhaust gas turbocharger (generally Abgasaufladegeräte) are separated by the cylinder bank, which reduces the cost of exhaust gas piping and avoids the need for thermal expansion compensation of different heat-stressed components. The working processes of the cylinders 3 On the exhaust side, they are separated from each other in terms of ignition or charge, while at the same time meeting the requirements for space-saving, modular and integrated assemblies with clear advantages in terms of production and engine assembly. For the fast, dynamic response of the turbocharger 4 It is very advantageous here that in the proposed arrangement, the volumes of the exhaust pipes 15 can be small, as between the exhaust gas turbines 6 and the individual cylinders 3 (That is, their exhaust valves, not shown) is a relatively small distance.

2 shows an internal combustion engine 1 , as above 1 described with the first cylinder bank A and the second cylinder bank B and the cylinders 3 working in exhaust pipes 15 to exhaust groups 14 are summarized, namely to an exhaust group A _{1 of} the first cylinder bank A, comprising the cylinder 3.1 and 3.3 , a second exhaust group A _{2 of} the first cylinder bank A, comprising the cylinders 3.2 and 3.4 , a first exhaust group B _{1 of} the second cylinder bank B, comprising the cylinders 3.5 and 3.6 and a second exhaust group B _{2 of} the second cylinder bank B, comprising the cylinders 3.7 and 3.8 , All four exhaust groups A ₁ , A ₂ , B ₁ , B ₂ each act on the respective cylinder bank 13 associated exhaust gas turbocharger 4 namely, its exhaust gas turbine 6 , in turn, as a twin scroll turbine 7 is trained. Notwithstanding the in 1 The arrangement shown has in each case one exhaust gas group of each cylinder bank, in the present case the second exhaust gas group A _{2 of} the first cylinder bank A and the second exhaust gas group B _{2 of} the second cylinder bank B, an actuator 17 on, the corresponding exhaust pipe 15 alternately on a first spiral channel 18 or a second spiral channel 19 the twin scroll turbine 7 can guide. The exhaust gases of the respective first exhaust group A ₁ and B ₁ are respectively on the first spiral channel 18 every exhaust gas turbine 6 whereas the exhaust gases of each second exhaust group A ₂ , B _{2 are directed} either to the second spiral channel 19 or on the first spiral channel 18 can be passed, including the exhaust gas turbine 6 by means of the actuator 17 with regard to the exhaust system of the respective second exhaust group A ₂ , B ₂ switchable and / or regulated. In particular, this is advantageously possible, limited in time the respective second exhaust gas flow A ₂ , B _{2 in} addition to the first spiral channel 18 zuzuschalten, which is acted upon by the respective first exhaust group A ₁ , B ₁ , whereby the kinetic energy of the exhaust gas flow is increased overall at the turbine wheel and the turbine shaft is accelerated more. Be advantageous, in particular for the rapid transition of load and speed conditions of the internal combustion engine 1 , Control devices for the respective exhaust gas flows provided, the amount of exhaust gas flow of the exhaust groups A ₁ ... B ₂ to the respective exhaust gas turbochargers 4 and / or the kinetic conditions at the respective inlets of the respective exhaust gas turbines 6 make it controllable. In this case, the quantity control can be realized simply by, for example, a flap valve in the manner of a so-called waste gate, which releases two bypass channels on the respective turbine wheel to the outlet of the turbines, if required, or in the case of double-flow turbine housings (in particular twinscroll). Furthermore, an adaptation of the kinetics at the inlet / inlet of the respective turbine wheel, for example, by adjustable or variable vane geometries take place, as it is already known from the prior art. In this way, both in the overall engine operation as well as in operation with cylinder deactivation 16 a highly comfortable, dynamic and at the same time fuel-saving operation possible. Because of that also in operation with cylinder deactivation 16 one cylinder per exhaust group 14 is in operation, a cooling of the individual exhaust groups 14 rather, it results in a uniform heating of all exhaust-carrying components, each working cylinder works in his group with the four-stroke process distance of 720 ° crank angle without charge alternation.

1

Internal combustion engine

2

V8 engine

3

cylinder

3.1

cylinder 1

3.2

cylinder 2

3.3

cylinder 3

3.5

cylinder 4

3.5

cylinder 5

3.6

cylinder 6

3.7

cylinder 7

3.8

cylinder 8th

4

turbocharger

5

compressor

6

exhaust turbine

7

Twin-scroll turbine

8th

turbine housing

9

axis of symmetry

10

crankshaft

11

cross crankshaft

12

total motor

13

cylinder bank

14

exhaust gas group

15

exhaust pipe

16

cylinder deactivation

17

actuator

18

first spiral channel

19

second spiral channel

A

1. cylinder bank

B

Second cylinder bank

A ₁

1. Exhaust group of the cylinder bank A

A ₂

Second Exhaust group of the cylinder bank A

B ₁

1. Exhaust group of the cylinder bank B

B ₂

Second Exhaust group of the cylinder bank B

QUOTES INCLUDE IN THE DESCRIPTION

This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.

Cited patent literature

• - DE 102006042443 A1 [0003]
• DE 102006042464 A1 [0003]

Claims (29)

Method for operating an internal combustion engine with eight cylinders, which are arranged in two V-shaped cylinder banks, which has a cross crankshaft and at least for each of the two banks of cylinders has an exhaust gas turbocharger, characterized in that the exhaust gas streams of two cylinders each of the four cylinders having cylinder banks are combined in each case in an exhaust pipe and that the two exhaust pipes of the respective cylinder bank are separated from each other on the exhaust gas turbocharger associated with the respective cylinder bank. Method according to claim 1, characterized in that in that at least one cylinder is assigned to each of the exhaust pipes Cylinder can be turned off during operation of the internal combustion engine. Method according to one of the preceding claims, characterized in that the two exhaust pipes of each cylinder bank each assigned to the associated exhaust gas turbocharger this cylinder bank become. Method according to one of the preceding claims, characterized in that at least one of the exhaust gas turbochargers a switchable with respect to the exhaust system and / or has controllable exhaust gas turbine, depending on an operating state of the internal combustion engine switched or regulated becomes. Method according to one of the preceding claims, characterized in that the circuit or regulation of the exhaust gas turbine one of the exhaust pipes of the cylinder bank is used. Method according to one of the preceding claims, characterized in that the exhaust gas turbine two spiral channels and that in each case one of the exhaust pipes of the cylinder bank in each case a spiral channel or both exhaust pipes in a spiral channel be directed. Method according to one of the preceding claims, characterized in that a cylinder deactivation takes place in such a way that in each case one cylinder per exhaust pipe is switched off. Method according to one of the preceding claims, characterized in that the cylinder deactivation takes place in such a way that, based on the internal combustion engine as a total engine, a Cylinder shutdown of four of the eight cylinders with one ignition angle of 180 ° results. Internal combustion engine with eight cylinders, which are arranged in two V-shaped cylinder banks, which has a cross crankshaft and which has at least one exhaust gas turbocharger, characterized in that in each case two cylinders ( 3 ) a cylinder bank ( 13 ) to an exhaust group ( 14 ) in an exhaust pipe ( 15 ), the two exhaust pipes ( 15 ) of the respective cylinder bank ( 13 ) separated from each other to the exhaust gas turbocharger ( 4 ), wherein at least one cylinder ( 3 ) of each of the exhaust pipes ( 15 ) associated cylinder ( 3 ) can be switched off. Internal combustion engine according to claim 9, characterized in that each cylinder bank ( 13 ) an exhaust gas turbocharger ( 4 ) assigned. Internal combustion engine according to one of the preceding claims, characterized in that the two exhaust pipes ( 15 ) of each cylinder bank ( 13 ) each of the cylinder bank ( 13 ) each assigned exhaust gas turbocharger ( 4 ) assigned. Internal combustion engine according to one of the preceding claims, characterized in that at least one of the exhaust gas turbochargers ( 4 ) with regard to the exhaust gas guide switchable and / or controllable exhaust gas turbine ( 6 ) having. Internal combustion engine according to one of the preceding claims, characterized in that the cylinders ( 3 ) have a firing order 1-5-4-8-6-3-7-2. Internal combustion engine according to one of the preceding claims, characterized in that the cylinder deactivation ( 16 ) the cylinders 5, 8, 3, 2 and / or the cylinders 1, 4, 6, 7 detected. Internal combustion engine according to one of the preceding claims, characterized in that the cylinder banks ( 13 ) have outside exhaust outlets. Internal combustion engine according to one of the preceding claims, characterized in that the cylinder banks ( 13 ) have inside exhaust outlets. Internal combustion engine according to one of the preceding claims, characterized in that the exhaust pipes ( 15 ) on the outside of the cylinder banks ( 13 ) are arranged. Internal combustion engine according to one of the preceding claims, characterized in that the exhaust pipes ( 15 ) inside the cylinder banks ( 13 ) are arranged, in particular in an internal V of the internal combustion engine ( 1 ) Internal combustion engine after one of the before going claims, characterized in that the exhaust gas turbocharger ( 4 ) on the outside of the cylinder banks ( 13 ) are arranged. Internal combustion engine according to one of the preceding claims, characterized in that the exhaust gas turbocharger ( 4 ) inside the cylinder banks ( 13 ) are arranged, in particular in an internal V of the internal combustion engine ( 1 ). Internal combustion engine according to one of the preceding claims, characterized in that an exhaust gas turbocharger ( 4 ) on the outside of a cylinder bank ( 13 ) and the other exhaust gas turbocharger ( 4 ) inside the cylinder banks ( 13 ) is arranged, in particular in an internal V of the internal combustion engine ( 1 ). Internal combustion engine according to one of the preceding claims, characterized in that at least one exhaust gas turbocharger ( 4 ) substantially the front side of the internal combustion engine ( 1 ) is arranged. Internal combustion engine according to one of the preceding claims, characterized in that at least one exhaust gas turbocharger ( 4 ) has a variable turbine geometry and / or at least one Abgasstromverstell- or -leiteinrichtung. Internal combustion engine according to one of the preceding claims, characterized in that the exhaust pipe ( 15 ), welded and / or made of sheet metal shells. Internal combustion engine according to one of the preceding claims, characterized in that the exhaust pipe ( 15 ) with at least one region of the exhaust gas turbocharger ( 4 ) is cast or welded or has a releasable flange connection. Internal combustion engine according to one of the preceding claims, characterized in that the exhaust pipe ( 15 ) in the cylinder head of at least one cylinder bank ( 13 ) is poured. Internal combustion engine according to one of the preceding claims, characterized in that at least one turbine housing ( 8th ) at least one exhaust gas turbocharger ( 4 ) on a cylinder bank ( 13 ) is flanged. Internal combustion engine according to one of the preceding claims, characterized in that at least one turbine housing ( 8th ) and / or at least one exhaust pipe ( 15 ) and / or at least one cylinder bank ( 13 ) comprises a coolant jacket and / or a heat insulating coating and / or an air heat insulating layer. Internal combustion engine according to one of the preceding claims, characterized in that the crankshaft ( 10 ) has split crank pins (split pin).