DE102010024008A1 - Combustion engine for motor car, has low pressure cylinders whose exhaust valves are closed before low pressure cylinders of respective cylinder banks reach maximum dead point, and inlet valves and exhaust valves driven by crankshaft - Google Patents

Abstract

The engine (10) has cylinder banks (11, 12) whose lifting cylinders are coupled with stroke spigots of a crankshaft (13), where the cylinders of the banks are controlled via an intake cam shaft (27) and an exhaust cam shaft (28). The two inlet valves are provided for fuel and combustion air and/or a fuel combustion air mixture, and exhaust valves are provided for exhaust gas, where the inlet and the exhaust valves are driven by the crankshaft. Exhaust valves of the low pressure cylinders are closed before the low pressure cylinders of respective cylinder banks reach a maximum dead point. An independent claim is also included for a method for operating a combustion engine.

Description

The invention relates to an internal combustion engine according to the preamble of claim 1 and a method for operating the same according to the preamble of claim 9.

From the EP 1 961 943 A1 an internal combustion engine having a plurality of cylinder banks is known, each cylinder bank having two outer, working with fuel supply in the four-stroke high-pressure cylinder and a medium, operating without own fuel supply in two-stroke low pressure cylinder, which is filled or acted upon by the two outer high-pressure cylinders of the respective cylinder bank with exhaust gas. Valves, namely intake valves and exhaust valves, of the cylinders of the cylinder banks of the internal combustion engine disclosed in this prior art can be actuated via camshafts. Reciprocating cylinders of the cylinder banks are coupled with crank pins of a crankshaft. The camshafts of the cylinder banks are drivable from the crankshaft.

Another internal combustion engine with two cylinder banks, each of which cylinder bank has two outer, working with fuel supply in the four-stroke cycle high-pressure cylinder and a medium, working without own fuel supply in two-stroke low pressure cylinder, is from the US 2009/0223482 A1 known. Thus, in this prior art reciprocating cylinder of the cylinder banks coupled via connecting rods with a crankshaft, wherein such crank pins of the crankshaft to which the connecting rod of the high-pressure cylinder attack lie in a common plane, whereas such crankpin the crankshaft to which the connecting rods attack the low pressure cylinder, are offset with respect to this plane seen in the direction of rotation or circumferential direction of the crankshaft, namely, a Kröpfungswinkel of 90 °. Reciprocating piston in the direction of rotation of the crankshaft or of opposite in the circumferential direction of the crankshaft cylinders of the different cylinder banks attack on their respective connecting rods on common crank pins of the crankshaft. Thus, the crank pins of the crankshaft, on which the reciprocating piston opposing high-pressure cylinder attack together via their connecting rods, in a common plane, wherein the crank pin of the crankshaft on which the reciprocating piston in the circumferential direction of the crankshaft opposite low pressure cylinder of the two cylinder banks in common via their connecting rods attack, offset from this plane by 90 °.

From the DE 31 21 301 A1 Another internal combustion engine is known, the two cylinder banks, each with three cylinders, namely with two outer, working with fuel supply in the four-stroke high-pressure cylinders and a medium, operating without own fuel supply in two-stroke low pressure cylinder, wherein the low-pressure cylinder of the respective cylinder bank of the two outer High-pressure cylinders of the respective cylinder bank is alternately filled with exhaust gas. From this prior art, it is already known to arrange the two cylinder banks in the form of a series engine or in the form of a V-engine or in the form of a boxer engine to each other.

Although it is already known from the above-cited prior art to use the exhaust gas of the four-stroke fuel-operated high-pressure cylinders in the low-pressure cylinders of the cylinder banks to increase the efficiency of an internal combustion engine, there is a need for further increasing the efficiency of such internal combustion engines with simple means.

Proceeding from this, the present invention has the object to provide a novel internal combustion engine and a method for operating the same.

This object is achieved by an internal combustion engine according to claim 1. According to the invention, the exhaust valves of the low pressure cylinder of the or each cylinder bank are closed before the low pressure cylinder of each cylinder bank reaches its top dead center. This makes it possible to minimize expansion losses of the exhaust gas in the overflow of the exhaust gas from the high-pressure cylinders in the respective low-pressure cylinder or each cylinder bank and so to increase the efficiency of such internal combustion engines with simple means.

According to an advantageous embodiment of the invention is during the open state of the exhaust valves of the low-pressure cylinder of the or each cylinder bank for the opening of the valves of a high-pressure cylinder of the respective cylinder bank before an overlap. By this overlap, the efficiency of such internal combustion engines can be further increased.

The inventive method for operating an internal combustion engine is defined in claim 9.

Preferred embodiments of the invention will become apparent from the dependent claims and the description below. Embodiments of the invention will be described, without being limited thereto, with reference to the drawings. Showing:

1 a perspective view of a detail of an embodiment of an internal combustion engine according to the invention with two cylinder banks;

2 : A perspective view of a detail of the internal combustion engine of 1 in the region of a cylinder bank and this cylinder bank associated camshafts;

3 a perspective view of a further detail of the internal combustion engine of 1 in the range of a crankshaft and with the crankshaft via connecting rod coupled cylinder;

4 : the detail of 4 in a front view;

5 : a view on valves of an internal combustion engine cylinder bank 1 ;

6 a first diagram to illustrate the operation of the internal combustion engine according to the invention; and

7 : A second diagram to illustrate the operation of the internal combustion engine according to the invention.

The present invention relates to an internal combustion engine of a motor vehicle. 1 shows a perspective view of an embodiment of an internal combustion engine according to the invention 10 , the two arranged in V-position cylinder banks 11 and 12 having each of the cylinder banks 11 and 12 each comprises three cylinders.

3 schematically shows the cylinder of the two cylinder banks 11 and 12 together with a crankshaft 13 , A first cylinder bank 11 includes two outer four-stroke fuel-fired high-pressure cylinders 14 and 15 and a middle, working without own fuel supply in the two-stroke process, alternately from the high-pressure cylinders 14 . 15 filled with exhaust low pressure cylinder 16 ,

Likewise, the second cylinder bank includes 12 two outer high-pressure cylinders powered by four-stroke fuel 17 and 18 and a middle, working without own fuel supply in the two-stroke process, alternately from the high-pressure cylinders 17 and 18 filled with exhaust low pressure cylinder 19 ,

How best 3 can be taken, are the cylinders 14 . 15 and 16 the first cylinder bank 11 as well as the cylinders 17 . 18 and 19 the second cylinder bank 12 each positioned in series with each other, the cylinders 14 . 15 and 16 the first cylinder bank 11 the cylinders 17 . 18 and 19 the second cylinder bank 12 in the direction of rotation or in the circumferential direction of the crankshaft 13 are opposite.

The cylinders of the cylinder banks 11 and 12 lie opposite each other in such a way that on the one hand high-pressure cylinder 14 . 17 and 15 . 18 and on the other hand low-pressure cylinder 16 . 19 are opposite. So can 3 . 4 be taken that the high-pressure cylinder 14 and 17 , the high pressure cylinder 15 and 18 as well as the low-pressure cylinder 16 and 19 the two cylinder banks 11 and 12 in the direction of rotation 34 the crankshaft 13 or in the circumferential direction of the same.

The cylinders of the two cylinder banks 11 and 12 valves are assigned. 5 shows a view of the valves of a cylinder bank 11 respectively. 12 the internal combustion engine according to the invention in the range of all cylinders of the respective cylinder bank 11 respectively. 12 , wherein according to 5 the two outer, working with fuel supply in the four-stroke high-pressure cylinder 14 . 15 respectively. 17 . 18 two intake valves each 20 for fuel and combustion air or a fuel-combustion air mixture and in each case an exhaust valve 21 for exhaust gas. Then, when the high pressure cylinders are operating with direct fuel injection, separate fuel injectors are present. The middle, working without own fuel supply in the two-stroke process low-pressure cylinder 16 respectively. 19 the respective cylinder bank 11 respectively. 12 includes two inlet valves 22 for exhaust gas and two exhaust valves 23 for exhaust. As already mentioned, the low-pressure cylinder 16 respectively. 19 each cylinder bank 11 respectively. 12 from the high pressure cylinders 14 . 15 respectively. 17 . 18 the respective cylinder bank 11 . 12 alternately filled with exhaust gas.

In 5 is by arrows 24 the fuel and combustion air supply and the fuel combustion air mixture supply to the respective outer high-pressure cylinders of the cylinder banks shown. arrows 25 visualize the overflow of exhaust gas from the outer high-pressure cylinders 14 . 15 respectively. 17 . 18 the respective cylinder bank 11 respectively. 12 in respective low-pressure cylinder 16 respectively. 19 the same. arrows 26 illustrate the discharge of exhaust gas from the respective low pressure cylinder 16 . 19 the respective cylinder bank 11 . 12 ,

The above-mentioned valves 20 . 21 . 22 and 23 the cylinder of the cylinder banks 11 and 12 are about camshafts 27 and 28 controllable, namely via so-called intake camshafts 27 and so-called exhaust camshaft 28 , The intake valves 20 the high pressure cylinder 14 . 15 respectively. 17 . 18 as well as the inlet valves 22 the low-pressure cylinder 16 respectively. 19 are doing over the respective intake camshaft 27 the respective cylinder bank 11 respectively. 12 driven, whereas the exhaust valves 21 the high pressure cylinder 14 . 15 respectively. 17 . 19 and the exhaust valves 23 of the low-pressure cylinder 16 respectively. 19 the respective cylinder bank 11 respectively. 12 from the respective exhaust camshaft 28 the respective cylinder bank 11 respectively. 12 be controlled.

As already stated, the high-pressure cylinders work 14 . 15 respectively. 17 . 18 the two cylinder banks 11 and 12 in four-stroke process, whereas the low-pressure cylinder 16 respectively. 19 the cylinder banks 11 . 12 work in two-stroke process. Here are the low pressure cylinder 16 respectively. 19 from the respective high-pressure cylinders 14 . 15 respectively. 17 . 18 alternately filled with exhaust, creating exhaust valves 23 the low-pressure cylinder 16 . 19 the cylinder banks 11 . 12 a different timing is required as for the other valves of the cylinders of the cylinder banks.

Therefore, according to 2 for controlling the exhaust valves 23 of the low-pressure cylinder 16 respectively. 19 the respective cylinder bank 11 respectively. 12 on the exhaust camshaft 28 the respective cylinder bank 11 respectively. 12 as double cams 29 trained cam positioned, whereas the cams for controlling the other valves 20 . 21 and 22 the cylinder of the respective cylinder bank 11 respectively. 12 as a single cam 30 are executed.

To ensure the overflow of the exhaust gas from the high-pressure cylinders 14 . 15 respectively. 17 . 18 the cylinder banks 11 . 12 in the low pressure cylinder 16 . 19 the respective cylinder bank overflow channels are present, wherein 2 such a transfer channel 31 shows.

The internal combustion engine 10 points the crankshaft 13 on, being over the crankshaft 13 the camshafts 27 . 28 the cylinder banks 11 . 12 are drivable. reciprocating 33 the cylinder 14 to 19 the two cylinder banks 11 and 12 are with the crankshaft 13 over connecting rod 32 coupled (see 3 and 4 ), the connecting rods 32 the reciprocating piston 33 at so-called crankpin of the crankshaft 13 attack.

As already stated, in the exemplary embodiment shown, the cylinder banks 11 and 12 the internal combustion engine 10 while ensuring a V-construction positioned to each other, namely according to 4 such that the high pressure cylinder 14 and 15 the first cylinder bank 11 and the high-pressure cylinders 17 and 18 the second cylinder bank 12 in the direction of rotation 34 the crankshaft 13 seen include a defined cylinder bank offset angle β.

This cylinder bank offset angle β is in accordance with 4 for example 120 °. However, the defined cylinder bank offset angle β can also be 90 ° or 180 °. Furthermore, other cylinder bank offset angle β are conceivable.

As 4 can still be found, is the low-pressure cylinder 16 the first cylinder bank 11 opposite the high pressure cylinders 14 and 15 the same offset by a first defined Zylinderversatzoffseldinkel β _OF11 . The low pressure cylinder 19 the second cylinder bank 12 is opposite the high pressure cylinders 17 . 18 the same offset by a second defined cylinder offset offset _angle β _OF12 .

Here are according to 4 these cylinder _{offset offset angles} β _OF11 and β _{OF12 are} preferably equal in magnitude, but have different signs. However, it is also possible that the amounts of the two cylinder _{offset offset angles} β _OF11 and β _OF12 are different from each other.

In 4 is the low-pressure cylinder 16 the cylinder bank 11 opposite the high pressure cylinders 14 and 15 the same in the direction of rotation 34 the crankshaft 13 offset by the cylinder offset offset _angle β _OF11 , whereas the low pressure cylinder 19 the cylinder bank 12 opposite the high pressure cylinders 17 . 18 the same opposite to the direction of rotation 34 the crankshaft 13 offset by the cylinder offset offset _angle β _OF12 . The cylinder _{offset offset angles} β _OF11 and β _OF12 have an amount between 1 ° and 10 °.

By the above offset the low pressure cylinder 16 and 19 opposite the high pressure cylinders 14 . 15 and 17 . 18 the cylinder banks 11 and 12 can overflow channels 31 be provided with relatively small volumes. A small volume in a transfer channel 31 minimizes losses in the relaxation of over the respective overflow 31 to be transferred exhaust gas. This has a positive effect on the achievable with the internal combustion engine efficiency.

The high pressure cylinder 14 . 15 . 17 and 18 the cylinder banks 11 and 12 are operated in a defined firing order with a defined firing interval, the firing interval is dependent on the cylinder bank offset angle β.

Preferably, the high pressure cylinder 14 . 15 . 17 and 18 the cylinder banks 11 and 12 operated with a defined ignition sequence such that first fuel or a fuel-combustion air mixture in a first high-pressure cylinder 14 a first cylinder bank 11 , then in a first high-pressure cylinder 11 in the circumferential direction of the crankshaft 13 seen opposite, first high pressure cylinder 17 a second cylinder bank 12 , then in a second High pressure cylinder 15 the first cylinder bank 11 , and then in a second high-pressure cylinder 15 the first cylinder bank 11 in the circumferential direction of the crankshaft 13 seen opposite, second high pressure cylinder 18 the second cylinder bank 12 is ignited.

The firing order of the high-pressure cylinder 14 . 15 . 17 and 18 the cylinder banks 11 and 12 the internal combustion engine according to the invention is therefore: cylinder 14 -Cylinder 17 -Cylinder 15 -Cylinder 18 respectively. 14 - 17 - 15 - 18 ,

In the above firing order of the high pressure cylinder 14 . 15 . 17 and 18 the cylinder banks 11 and 12 are fillings of low pressure cylinders 16 . 19 the cylinder banks 11 . 12 inserted, namely such that after each ignition in a high-pressure cylinder 14 . 15 . 17 . 18 a cylinder bank 11 . 12 and before the immediately subsequent ignition in a high-pressure cylinder 14 . 15 . 17 . 18 the other cylinder bank 11 . 12 Exhaust gas from the high pressure cylinder, in which the combustion is completed, in the low pressure cylinder of the respective cylinder bank 11 . 12 is transferred. So then, when in the high-pressure cylinder 14 the cylinder bank 11 the combustion is complete and before the ignition in the high-pressure cylinder 17 the cylinder bank 12 takes place, exhaust gas from the high-pressure cylinder 14 the cylinder bank 11 in the low pressure cylinder 16 the cylinder bank 11 transferred. Likewise, after ignition in the high-pressure cylinder 17 the cylinder bank 12 and before the subsequent ignition in the high-pressure cylinder 15 the cylinder bank 11 Exhaust from the high-pressure cylinder 17 the cylinder bank 12 in the low pressure cylinder 19 the cylinder bank 12 transferred. The order of the filling of the low-pressure cylinder 16 and 19 extended firing order of the high-pressure cylinder 14 . 15 . 17 and 18 is therefore: 14 - 16 - 17 - 19 - 15 - 16 - 18 - 19 ,

The firing interval between the high pressure cylinders 14 . 15 . 17 and 18 the cylinder banks 11 and 12 in the above firing order, the cylinder bank offset angle β is the high pressure cylinder 14 and 15 the first cylinder bank 11 and the high-pressure cylinders 17 and 18 the second cylinder bank 12 in the direction of rotation or circumferential direction of the crankshaft 13 include, depending.

Then, when the cylinder bank offset angle β is 120 °, the firing interval is the firing order 14 - 17 - 15 - 18 the high-pressure cylinder 120 ° -240 ° -120 ° -240 °. The admission of the low-pressure cylinder 16 . 19 with exhaust gas of the high-pressure cylinder 14 . 15 . 17 and 18 then takes place at 90 ° or 120 °. Then, when the cylinder bank offset angle β is 90 °, the firing interval is the firing order 14 - 17 - 15 - 18 the high-pressure cylinder 90 ° -270 ° -90 ° -270 °, wherein the application of the low-pressure cylinder 16 . 19 with exhaust again at 90 ° or 120 °. Then, when the cylinder bank offset angle β is 180 °, the firing interval is the firing order 14 - 17 - 15 - 18 the high pressure cylinder 180 ° -180 ° -180 ° -180 °, the application of the low pressure cylinder 16 . 19 with exhaust gas of the high pressure cylinder is then preferably at 90 °.

For the purposes of the present invention, the exhaust valves are or will be 23 every low-pressure cylinder 16 . 19 the cylinder banks 11 . 12 closed before the respective low-pressure cylinder 16 . 19 the respective cylinder bank 11 . 12 reached its top dead center. As a result, expansion losses of the exhaust gas when flowing over from a high-pressure cylinder 14 . 15 . 17 . 18 the respective cylinder bank 11 . 12 in the low pressure cylinder 16 . 19 the respective cylinder bank 11 . 12 can be minimized or eliminated, whereby the efficiency of such an internal combustion engine can be further increased.

In 6 is this aspect of the invention for the low pressure cylinder 16 the cylinder bank 11 the internal combustion engine according to the invention shown. So are in 6 for the cylinder bank 11 above the crankshaft angle opening positions of the valves of the cylinder 14 . 15 and 16 the cylinder bank 11 shown, namely with the course A _14, the opening position of the exhaust valve 21 of the high-pressure cylinder 14 , With the course E _14, the opening position of the intake valves 20 of the high-pressure cylinder 14 , with the curve E _15, the opening position of the intake valves 20 of the high-pressure cylinder 15 , with the curve A _15, the opening position of the exhaust valve 21 of the high-pressure cylinder 15 , with the curve A _16, the opening position of the exhaust valves 23 of the low-pressure cylinder 16 , with the curve E _16/14 the opening position of the inlet valve 22 of the low-pressure cylinder 16 , which with the exhaust valve 21 of the high-pressure cylinder 14 _interacts with the curve E _16/15 the opening position of the inlet valve 22 of the low-pressure cylinder 16 , which with the exhaust valve 21 of the high-pressure cylinder 15 interacts.

So can 6 be taken that according to the curve A _16, the exhaust valves 23 of the low-pressure cylinder 16 be closed so that at the crankshaft angles γ ₁ and γ _2, the exhaust valves 23 of the low-pressure cylinder 16 the cylinder bank 11 are completely closed, these crankshaft angles γ ₁ and γ ₂ before top dead center OT _{16 of} the low-pressure cylinder 16 lie.

For the low pressure cylinder 19 the cylinder bank 12 analogous conditions apply.

Preferably, the outlet cylinders 23 the low-pressure cylinder of the respective cylinder bank at the latest in a crankshaft angle completely closed, which is 5 ° to 25 ° before reaching the top dead center of the respective low-pressure cylinder. Particularly preferred is a variant of the invention, in which the exhaust valves 23 the low-pressure cylinder already 10 ° to 20 ° before reaching the top dead center of the respective low-pressure cylinder 16 . 19 are completely closed.

6 can be further taken that, according to an advantageous embodiment of the invention during the open state of the exhaust valves 23 of the low-pressure cylinder 16 for opening the valves of the high-pressure cylinder 14 and 15 the respective cylinder bank 11 there is an overlap. So can 6 be taken that according to the curve A _14, the exhaust valve 21 of the high-pressure cylinder 14 is still open while already according to the curve E _14, the intake valves 20 of the high-pressure cylinder 14 are already open, this overlap then occurs when according to the curve A _16, the exhaust valves 23 of the low-pressure cylinder 16 are open, in such a way that this overlap, the in 6 in the range indicated by X ₁₁ , in the region of top dead center OT _{14 of} the high-pressure cylinder 14 lies. For the other high-pressure cylinder 15 the cylinder bank 11 is according to 6 this overlap Y ₁₁ also with open exhaust valves 23 of the low-pressure cylinder 16 before, in the area of top dead center OT _{15 of} the high-pressure cylinder 15 ,

In 7 are above the crankshaft angle of the crankshaft 13 for both cylinder banks 11 and 12 Opening positions of the valves of the respective cylinder 14 . 15 . 16 . 18 and 19 registered, namely according to the curves E ₁₄ , E ₁₅ , E ₁₇ and E _18, the opening positions of the intake valves 20 the high pressure cylinder 14 . 15 . 17 and 18 the cylinder banks 11 and 12 , According to the curves A ₁₄ , A ₁₅ , A ₁₇ and A _18, the opening positions of the exhaust valves 21 the high pressure cylinder 14 . 15 . 17 . 18 the cylinder banks 11 and 12 , According to the curves A ₁₆ and A _19, the opening position of the exhaust valves 23 the low-pressure cylinder 16 and 19 the cylinder banks 11 and 12 and according to the curves E _16/14 , E _16/15 , E _19/17 and E _19/18, the opening position of the intake valves 22 the low-pressure cylinder 16 . 19 , namely the inlet valves 22 connected to the respective outlet valve 21 of the respective high-pressure cylinder 14 . 15 . 17 and 18 when overflowing the exhaust gas in the respective low pressure cylinder 16 respectively. 19 interact.

So can 7 the above-mentioned overlap in the opening of the valves of the high pressure cylinder 14 . 15 . 17 and 18 the two cylinder banks 11 and 12 during the open state of the exhaust valves of the respective low-pressure cylinder 16 . 19 through the areas X ₁₁ , Y ₁₁ , X ₁₂ and Y _{12 are} removed.

The details according to the invention can also be used in an internal combustion engine having a single cylinder bank or more than two cylinder banks.

LIST OF REFERENCE NUMBERS

10

Internal combustion engine

11

cylinder bank

12

cylinder bank

13

crankshaft

14

High pressure cylinder

15

High pressure cylinder

16

Low-pressure cylinder

17

High pressure cylinder

18

High pressure cylinder

19

Low-pressure cylinder

20

intake valve

21

outlet valve

22

intake valve

23

outlet valve

24

Fuel and combustion air supply

25

Exhaust gas flow over

26

exhaust removal

27

intake camshaft

28

exhaust

29

double cams

30

simply cams

31

overflow

32

pleuel

33

reciprocating

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

• EP 1961943 A1 [0002]
• US 2009/0223482 A1 [0003]
• DE 3121301 A1 [0004]

Claims (9)

Internal combustion engine, having at least one cylinder bank, wherein the or each cylinder bank has two outer, working with fuel supply in the four-stroke high-pressure cylinder and a middle, operating without fuel supply in two-stroke alternately filled from the high pressure cylinders of the respective cylinder bank with exhaust low pressure cylinder, wherein the piston of the cylinder or the each cylinder bank are coupled via connecting rods with crankpin crankshaft, and wherein valves, namely intake valves and exhaust valves, the cylinder of the or each cylinder bank are controlled via camshafts which are drivable from the crankshaft, characterized in that the exhaust valves ( 23 ) of the low-pressure cylinder ( 16 . 19 ) of the or each cylinder bank ( 11 . 12 ) are closed before the low pressure cylinder ( 16 . 19 ) of the respective cylinder bank ( 11 . 12 ) reaches its top dead center. Internal combustion engine according to claim 1, characterized in that the exhaust valves ( 23 ) of the low-pressure cylinder ( 16 . 19 ) of the or each cylinder bank ( 11 . 12 ) at the latest in a crankshaft angle of 5 ° to 25 ° before reaching the top dead center of the low-pressure cylinder ( 16 . 19 ) are completely closed. Internal combustion engine according to claim 2, characterized in that the exhaust valves ( 23 ) of the low-pressure cylinder ( 16 . 19 ) of the or each cylinder bank ( 11 . 12 ) at the latest in a crankshaft angle of 10 ° to 20 ° before reaching the top dead center of the low-pressure cylinder ( 16 . 19 ) are completely closed. Internal combustion engine according to one of claims 1 to 3, characterized in that during the open state of the exhaust valves ( 23 ) of the low-pressure cylinder ( 16 . 19 ) of the or each cylinder bank ( 11 . 12 ) for the opening of the valves ( 20 . 21 ) of a high-pressure cylinder of the respective cylinder bank is an overlap. Internal combustion engine according to claim 4, characterized in that the overlap in the opening of the valves ( 20 . 21 ) of the high-pressure cylinder of the cylinder bank ( 11 . 12 ) is present in the region of top dead center of the respective high-pressure cylinder. Internal combustion engine according to one of Claims 1 to 5, characterized in that it comprises two cylinder banks, the high-pressure cylinders ( 14 . 15 . 17 . 18 ) of the cylinder banks ( 11 . 12 ) are operated with a defined ignition sequence such that first fuel or a fuel-combustion air mixture in a first high-pressure cylinder ( 14 ) a first cylinder bank ( 11 ), then in a first high pressure cylinder ( 14 ) of the first cylinder bank ( 11 ) in the direction of rotation or circumferential direction of the crankshaft ( 13 ) opposite, first high-pressure cylinder ( 17 ) a second cylinder bank ( 12 ), then in a second high pressure cylinder ( 15 ) of the first cylinder bank ( 11 ) and then in a second high pressure cylinder ( 15 ) of the first cylinder bank ( 11 ) in the direction of rotation or circumferential direction of the crankshaft ( 13 ) opposite, second high-pressure cylinder ( 18 ) of the second cylinder bank ( 12 ) is ignited. Internal combustion engine according to claim 6, characterized in that in the above ignition sequence fillings of the low-pressure cylinder ( 16 . 19 ) of the cylinder banks ( 11 . 12 ) are pushed in such a way that after each ignition in a high pressure cylinder of a cylinder bank and before the immediately subsequent ignition in a high pressure cylinder of the other cylinder bank exhaust gas from the high pressure cylinder, in which the ignition is completed, is transferred to the low pressure cylinder of the respective cylinder bank. Internal combustion engine according to claim 6 or 7, characterized in that the high-pressure cylinder ( 14 . 15 . 17 . 18 ) of the cylinder banks ( 11 . 12 ) are operated in the defined firing order with a defined firing interval, which is dependent on the cylinder bank offset angle (β). Method for operating an internal combustion engine according to one or more of claims 1 to 8, characterized in that the exhaust valves of the low pressure cylinders are closed so that they are completely closed before the respective low-pressure cylinder of the respective cylinder bank reaches its top dead center.

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