DE112018004444T5 - Internal combustion engine with fast responding secondary exhaust valve and associated procedure - Google Patents

Abstract

An internal combustion engine, ICE, (2) is disclosed herein. The ICE (2) comprises a second valve (40) which is arranged in an outlet line (6). The outlet line (6) extends from an outlet valve (26) to an inlet of a turbine (8). The second valve (40) is designed to open and close the outlet line (6). The second valve (40) is opened after the outlet valve (26) has started to open. The second valve (40) has a higher valve surface opening speed than the outlet valve (26). Within a range of 10 to 90 degrees of crankshaft angle after the exhaust valve (26) begins to open, the second valve (40) begins to open.

Description

Technical field

The present invention relates to an internal combustion engine. The present invention further relates to a method for controlling an internal combustion engine. According to further aspects, the invention relates to a computer program for performing a method for controlling an internal combustion engine and a computer program product for performing a method for controlling an internal combustion engine.

background

A piston of a four-stroke internal combustion engine (ICE) executes four strokes in an ICE cylinder, an intake stroke, a compression stroke, an operation stroke, and an exhaust stroke. A conventional four-stroke ICE has the same geometric compression rate and expansion rate, i.e. H. the compression cycle has the same length as the work cycle. The working medium is compressed during the compression stroke starting from bottom dead center (BDC), the piston to top dead center (TCD). A certain amount of energy is added around the TDC when the working medium burns. The working medium is then expanded during the work cycle. Because the operation of the conventional ICE includes the same geometric compression rate and expansion rate, there is still a lot of power left in the cylinder when the piston reaches the BDC. This is an inherent property of the conventional ICE. The power remaining in the cylinder corresponds to approximately 30% of a nominal power at high load and can theoretically be obtained, for example, in a turbine which is connected to an outlet arrangement of the cylinder. The nominal power of an ICE is the power that is available on an output shaft / crankshaft of the ICE.

An ICE exhaust assembly must be opened during the work cycle before the piston reaches its BDC. Otherwise, if the exhaust arrangement opened later, for example when the piston reached the BDC, the internal pressure of the exhaust gases (working medium) within the cylinder would impede the movement of the piston towards the TDC during the exhaust stroke. As a result, the available engine power would be reduced.

The outlet arrangement of a conventional four-stroke ICE comprises at least one poppet valve. A poppet valve is a reliable and durable solution, and is able to withstand a cylinder pressure of 25 MPa and a cylinder gas temperature of more than 2000 K while remaining gas-tight. However, a poppet valve controlled by a camshaft has a disadvantage in that when it starts to open, it is in a rest position, which results in a low initial poppet valve opening speed. Therefore, the poppet valve throttles outflow of exhaust gas through the exhaust assembly. At least a first amount of exhaust gas in the cylinder flows through the poppet valve as it opens and is throttled before the poppet valve provides a large opening for the exhaust gas to pass through. This reduces the available energy in the exhaust gas in a non-reversible process. In other words, a poppet valve creates a large percentage of irreversible pressure loss due to throttling of the exhaust gas as it passes through the poppet valve.

As indicated above, an ICE may include a turbine to utilize exhaust pressure to drive a turbine wheel of the turbine. From the discussion above it follows that a low exhaust pressure drop in a flow path from the cylinder to the turbine is difficult to achieve.

US 3961484 discloses an ICE. The ICE uses a power recovery turbine that is powered by the exhaust gases from the engine cylinders by dimensioning the wells that connect the exhaust valve surfaces to the turbine such that each well has a cross-sectional flow area that is smaller than the cross-sectional flow area of the exhaust valve when it is complete is open. While this results in a slight increase in friction losses in the shaft and pump losses to the pistons, such losses are allegedly offset by a reduction in throttle losses through the exhaust valve flow area during the valve opening process.

However, the throttling problem remains that is related to the poppet valve providing a slow increase in exhaust valve flow area, which is inherent in a poppet valve.

US 4535592 discloses a compound turbo-ICE having conventional reciprocating pistons, cylinders, manifolds, fuel-oxygen admixers or fuel injection, igniters, or auto-ignitions. The ICE comprises corresponding nozzle means for conveying the exhaust gas from the corresponding cylinders to one or more turbines. The inlet and outlet ends of the nozzle means are connected to the corresponding partition walls of corresponding combustion chambers or cylinders or to the inlet to a turbine. A quick opening valve releases exhaust gas from the corresponding Cylinders to the nozzle means. Therefore, an efficient use of exhaust gas is provided by a turbine that is used with the engine. A poppet valve may open later during an exhaust stroke after most of the useful exhaust energy has been expended through the quick opening valve and nozzle.

One problem with the quick opening valve is that it is difficult to provide a seal with the quick opening valve, the seal being able to withstand the high temperature and pressure within the respective cylinders.

DE 102010008264 discloses an exhaust gas turbocharged internal combustion engine with a small cubic capacity. The small size reduces fuel consumption, while turbocharging counteracts a reduction in performance. In an internal combustion engine with a small cubic capacity, only a small amount of energy is available for driving the turbocharger, in particular at low speeds at which the exhaust gas flow is low. As a result, such an internal combustion engine provides low torque at low speeds. DE 102010008264 suggests that the exhaust pipes lead to the exhaust gas turbine of the turbocharger via a shutdown device. The shutdown device is controlled such that a corresponding exhaust pipe is closed when the outlet valve of the corresponding cylinder opens. As a result of the closing of the exhaust pipe on the inflow side of the shutdown device, an exhaust gas pressure is built up, for example up to 10 bar. As a result, a pressure pulse is directed to the exhaust gas turbine when the shutdown device opens. The pressure pulse leads to an effective drive of the turbine and therefore permits an effective supercharging.

As a result, a higher boost pressure is achieved at low engine speeds, which can be advantageous for an internal combustion engine with a small cubic capacity. However, building up a high pressure in the exhaust pipe upstream of the shutdown device has its price. Instead of the piston in the relevant cylinder bore being able to move up freely with an open exhaust valve, the piston encounters resistance from the closed shutdown device and the resulting pressure build-up. Therefore, more energy is required to move the piston up in the cylinder bore.

Summary

It would be advantageous to achieve an internal combustion engine (ICE) that overcomes or at least mitigates some of the above disadvantages. It would be particularly desirable to enable low throttling losses in a flow of exhaust gas from a cylinder of the ICE to utilize a large amount of remaining energy in the exhaust gases in a turbine connected to an exhaust port of the ICE. In order to take one or more of these concerns into account, an ICE, a vehicle and a method for controlling an ICE are provided which have the features defined in the independent claims.

According to one aspect of the invention, an internal combustion engine, ICE, is provided that includes a crankshaft, at least one cylinder arrangement, and a turbine. The at least one cylinder arrangement forms a combustion chamber and comprises a cylinder bore, a piston which is set up to move in the cylinder bore between a top dead center (TDC) and a bottom dead center (BDC). reciprocatingly, an exhaust valve and an exhaust port disposed on an inner delimiting surface of the combustion chamber, the exhaust valve including a valve head configured to seal against a valve seat of the exhaust port. An outlet line extends from the outlet opening to an inlet of the turbine. The internal combustion engine includes a second valve arranged in the exhaust line, the second valve being configured to close and open the exhaust line, the second valve being opened after the exhaust valve has started to open. The second valve has a higher valve area opening speed than the exhaust valve, and within a range of 10 to 90 degrees crankshaft angle after the exhaust valve begins to open, the second valve begins to open.

Because the ICE includes a second valve disposed in the exhaust line, the second valve configured to close and open the exhaust power and open within a range of 10 to 90 degrees crankshaft angle after the exhaust valve begins to open , is opened, the pressure between the cylinder bore and the outlet line upstream of the second valve is equalized, at least to a certain degree, before the second valve opens. Furthermore, the exhaust gases are subject to less throttling when they pass through the second valve to the turbine than when they pass through the exhaust valve because the second valve has a higher valve area opening speed than the exhaust valve. Therefore, a comparatively large percentage of the available energy of the exhaust gases can be recovered in the turbine connected to the exhaust pipe. As a result, the above object is achieved.

More specifically, the pressure in a first portion of the exhaust line gradually increases up to the closed second valve, since the exhaust valve opens before the second valve, preferably until the pressure between the cylinder bore and the first portion of the exhaust power has been substantially equalized. Therefore, exhaust gas flow through the exhaust valve may occur during an initial phase of opening the exhaust valve when the turbine is disconnected from the exhaust valve by the second valve. As soon as the second valve begins to open, the exhaust valve will have been opened to such an extent that the exhaust gases flow through the exhaust opening substantially unimpeded. Because the second valve has a higher valve area opening speed than the exhaust valve, the exhaust gases reach the turbine with less throttling than if there was no second valve and the exhaust port was in direct communication with the turbine via the exhaust power.

Therefore, the exhaust valve can be configured to withstand the high pressures and temperatures during combustion within the cylinder bore, while the second valve is located in the exhaust line, protected from the high pressures and temperatures, and therefore need not be configured to handle the same high pressures and withstand temperatures. Instead, the second valve can be set up for quick opening in order to provide low-loss transmission of the exhaust gases to the turbine.

The exhaust gases that are present in the cylinder at the end of the working stroke and at the beginning of the exhaust stroke will be available for a removal of the energy remaining therein with significantly less irreversible losses than was possible in connection with an ICE in which the exhaust gases through an exhaust valve was throttled if they passed directly through an exhaust pipe to a turbine. Therefore, in an ICE according to the present invention, recovery of energy from the exhaust gases can be made possible in the turbine arranged on the downstream side of the exhaust valve. This efficient transfer of exhaust gases from the cylinder to the turbine is achieved by the fast opening second valve, which significantly reduces the irreversible throttling losses that typically occur through the exhaust valve of an ICE in which the exhaust valve is directly connected to the turbine.

Thus, the invention provides increased utilization of the energy available in the cylinder at the end of the stroke. The invention provides the ability to increase energy recovery from the exhaust gases compared to an ICE that would otherwise have been wasted in a non-reversible throttling process through the exhaust valve.

• - die Arbeit zu erhöhen, die von der Turbine an einen Zentrifugalkompressor übertragen wird, um die positive Pumparbeit während einer Induktion zu verbessern, d. h. eine erhöhte Open-Cycle-Effizienz, OCE, oder um ein relatives Luft-/KraftstoffVerhältnis, A, zu erhöhen, d. h. eine erhöhte Closed-Cycle-Effizienz, CCE.
• - eine bestimmte Turbine anzutreiben, die Leistung an eine Elektromotor/Generatoreinheit (electrical motor/generator unit), MGU, liefert, die mit einer Welle der Turbine verbunden ist, oder an die Kurbelwelle des ICE, d. h. Turboverbund (turbo compounding), oder an Hilfsvorrichtungen, beispielsweise eines relevanten Fahrzeugs.

This increased recovered energy can be used to:

• - Increase the work transferred from the turbine to a centrifugal compressor to improve positive pumping work during induction, ie increased open cycle efficiency, OCE, or to increase relative air / fuel ratio, A , ie increased closed-cycle efficiency, CCE.
• - Drive a particular turbine that provides power to an electrical motor / generator unit (MGU) connected to a shaft of the turbine, or to the crankshaft of the ICE, ie turbo compounding, or to Auxiliary devices, for example a relevant vehicle.

Several of the above alternatives for harnessing the increased recovered energy can be used simultaneously, for example the combination of turbocharging with a turbo compound (electrical or mechanical) implemented with the use of a turbine. Furthermore, the negative piston pumping work during the work cycle will be eliminated or at least significantly reduced, which leads to an increased OCE. In summary, the present invention will result in an increase in Brake Thermal Efficiency, BTE, compared to an ICE in which exhaust valves are connected directly to the turbine via the exhaust pipe.

The ICE can be a four-stroke ICE or a two-stroke ICE. The ICE may include more than one cylinder assembly, each cylinder assembly forming a combustion chamber and a cylinder bore, a piston located in the cylinder bore and reciprocating, a connecting rod connecting the piston to a crankshaft, and an exhaust valve for includes an outflow of exhaust gas from the cylinder bore. The ICE may include more than one turbine, such as two turbines, or one turbine for each cylinder arrangement of the ICE. In the case of two turbines, the exhaust valves of a number of cylinder assemblies can be connected to one turbine and the exhaust valves of the remaining cylinder assemblies can be connected to the other turbine. For example, the turbine may form part of a turbocharger, the ICE may be a compound turbo engine to which the turbine is connected via the crankshaft, or the turbine may drive an electric generator.

The term valve surface opening speed refers to the speed at which a valve opens, ie the change in the opening surface of a valve per unit time, for example m ² / second. The valve surface opening speed can be linear or non-linear, for example increasing. That the second valve has a higher valve surface opening speed than the exhaust valve means that the second valve has a higher valve surface opening speed at the moment when the second valve starts opening than the opening speed of the exhaust valve when it starts opening. In this way, throttling losses through the second valve are less compared to throttling losses through the exhaust valve if the exhaust valve were directly connected to a turbine, as in a prior art ICE.

The combustion chamber is arranged inside the cylinder arrangement, above the piston. Intake air enters the combustion chamber through an intake assembly of the cylinder assembly during the intake stroke of the piston. The intake air can be compressed by a turbocharger. For example, the internal combustion engine may be a compression ignition (CI) engine, such as a diesel engine, or a spark engine, such as an Otto-type engine, and in the latter case it includes a spark plug or similar device in FIG the cylinder arrangement. Fuel may be injected into the combustion chamber during part of the compression stroke or intake stroke of the piston, or may be entrained in the intake air. The fuel can ignite near the TDC between the compression stroke and the piston stroke.

According to embodiments, the at least one cylinder arrangement forms a combustion chamber, the cylinder arrangement having a maximum volume, V _MAX , between a bottom dead center, BDC, of the piston and an inner delimiting surface of the combustion chamber. The second valve is arranged at a position in the outlet line within a range of 1% to 25% of the maximum volume, V _MAX , downstream of the outlet opening, preferably within a range of 1% to 15% of the maximum volume, V _MAX , downstream of the Outlet opening. In this way, a volume of a first portion of the exhaust line between the exhaust valve and the second valve can have a volume that allows pressure equalization, at least to a high degree, between the combustion chamber and the first portion of the exhaust power before the second valve begins to open. The fact that the second valve is arranged at a position in the exhaust line, expressed by a specific volume, means that the specific volume, in this case defined as a percentage of the maximum volume of the combustion chamber, is provided in the output power between the exhaust opening and the second valve .

According to embodiments, the second valve can comprise a valve body, wherein the valve body can comprise a flow-permeable section area, in which a flow of an exhaust gas passes through the second valve, and a zero-flow section area, in which the outlet line in the second valve is closed, and wherein the valve body is configured to be set in motion before the valve body reaches the flow-permeable section area. In this way, the second valve can provide a high valve surface opening speed. Compared to a poppet valve that needs to be accelerated from a rest position when opened, the valve body that is in motion can provide a higher valve area opening speed.

According to another aspect of the invention, there is provided a vehicle that includes an internal combustion engine according to one of the aspects and / or according to one of the embodiments described herein.

• - Öffnen des Auslassventils,
• - Drehen der Kurbelwelle um einen vorgegebenen Kurbelwellenwinkel innerhalb eines Bereichs von 10 bis 90 Grad, und danach
• - Öffnen des zweiten Ventils bei einer höheren Ventilflächenöffnungsgeschwindigkeit als das Auslassventil.

According to a further aspect of the invention, a method for controlling an internal combustion engine is provided, the internal combustion engine comprising at least one cylinder arrangement, a crankshaft and a turbine, wherein the at least one cylinder arrangement forms a combustion chamber and a cylinder bore, a piston, which is set up there to reciprocate in the cylinder bore between a top dead center and a bottom dead center, a connecting rod connecting the piston to the crankshaft, an exhaust valve, and an exhaust port disposed on an inner delimiting surface of the combustion chamber, the exhaust valve one Valve head, which is configured to seal against a valve seat of the outlet opening, wherein an outlet line extends from the outlet opening to an inlet of the turbine, wherein the internal combustion engine comprises a second valve, which is arranged in the outlet line, the second Valve is set up to close and open the outlet line. The procedure includes the following steps in the order given:

• - Opening the exhaust valve,
• - Rotating the crankshaft by a predetermined crankshaft angle within a range of 10 to 90 degrees, and thereafter
• - Opening the second valve at a higher valve surface opening speed than the outlet valve.

Further features and advantages of the invention will appear when the appended claims and the following detailed description are considered.

Figure list

• 1 stellt schematisch einen Verbrennungsmotor, ICE, gemäß Ausführungsformen dar,
• 2 stellt schematisch eine Zylinderanordnung eines ICE 2 dar,
• 3a bis 3c stellen schematisch Querschnitte durch ein zweites Ventil gemäß Ausführungsformen dar,
• 4a bis 4e stellen alternative Ausführungsformen eines zweiten Ventils dar,
• 5 und 6 stellen Ausführungsformen von ICEs mit mehr als einer Zylinderanordnung dar,
• 7 zeigt ein schematisches Beispiel eines Turbinendiagramms einer Turbine dar, und
• 8 stellt ein Verfahren zum Steuern eines ICE dar.
• 9 stellt schematisch ein Öffnen und Schließen eines Auslassventils und eines zweiten Ventils dar.

Various aspects and / or embodiments of the invention, including its specific features and advantages, will be readily understood from the exemplary embodiments that are set forth in the following detailed description and in the accompanying drawings, in which:

• 1 schematically illustrates an internal combustion engine, ICE, in accordance with embodiments,
• 2nd schematically represents a cylinder arrangement of an ICE 2nd dar,
• 3a to 3c schematically represent cross sections through a second valve according to embodiments,
• 4a to 4e represent alternative embodiments of a second valve,
• 5 and 6 represent embodiments of ICEs with more than one cylinder arrangement,
• 7 FIG. 4 shows a schematic example of a turbine diagram of a turbine, and
• 8th represents a method for controlling an ICE.
• 9 schematically represents an opening and closing of an exhaust valve and a second valve.

Detailed description

Aspects and / or embodiments of the invention are only described more fully. The same reference numerals refer to the same elements throughout. Known functions and designs are not necessarily described in detail for the sake of brevity and / or clarity.

1 schematically illustrates an internal combustion engine, ICE, 2 according to embodiments. In these embodiments, the ICE 2nd a four-stroke ICE. The ICE 2nd comprises at least one cylinder arrangement 4th , a crankshaft 20 and a turbine 8th . 1 also represents a vehicle 1 schematically represents an internal combustion engine 2nd according to an aspect and / or an embodiment as disclosed herein. The vehicle 1 can be, for example, a heavy vehicle such as a truck or a bus.

The at least one cylinder arrangement 4th forms a combustion chamber 23 and includes a cylinder bore 12th , a piston 10th , an outlet arrangement 14 , an inlet arrangement 16 and a fuel injection assembly 18th and / or an ignition device. The piston 10th is set up in the cylinder bore 12th to move back and forth between a top dead center (TDC) and a bottom dead center (BDC). In 1 is the piston 10th shown with solid lines on the BDC and with dashed lines on the TDC. The cylinder arrangement 4th has a maximum volume, V _MAX , between the BDC of the piston 10th and an upper inner delimiting surface 24th the combustion chamber 23 on. The combustion chamber 23 is above the piston 10th within the cylinder assembly 4th educated. A connecting rod 22 connects the piston 10th with the crankshaft.

The cylinder arrangement 4th has a total swept volume, Vs, in the cylinder bore 12th between the BDC and the TDC of the piston 10th on. The cylinder arrangement 4th has a compression ratio, ε. V _MAX can be expressed as: $${\text{V}}_{\text{MAX}}={\text{V}}_{\text{S}}*\left(\mathrm{\epsilon }/\left(\mathrm{\epsilon }-1\right)\right).$$

The outlet arrangement 14 includes an exhaust valve and an exhaust port as below with reference to FIG 2nd is described. The outlet arrangement 14 is for exhaust gases from the cylinder bore 12th to the turbine 8th set up. An outlet pipe 6 extends from the outlet opening to an inlet 29 the turbine 8th . The ICE 2nd includes a second valve 40 that in the exhaust line 6 is arranged. The outlet arrangement 14 is configured to open and close an outlet flow area, A _CYL , of the outlet opening during an outlet _sequence of piston movement. The exhaust sequence can begin before the piston 10th reaches its BDC during the work stroke, and ends approximately at the TDC of the piston between the work stroke and the intake stroke.

The turbine 8th has an inlet 29 and includes a turbine wheel 27 .

2nd represents schematically the at least one cylinder arrangement 4th of the ICE 2nd of the 1 In particular, the outlet arrangement 14 shown in more detail. The outlet arrangement 14 includes a outlet valve 26 and an outlet opening 28 . The exhaust gases leave the combustion chamber 23 through the outlet opening 28 once the exhaust valve 26 it starts to open. The outlet pipe 6 extends from the outlet opening 28 to the inlet 29 the turbine 8th . The exhaust valve 26 includes a valve head 30th , which is set up against a valve seat 32 seal that around the exhaust port 28 extends around. The valve seat 32 can in the cylinder arrangement 4th be provided, for example on the upper inner delimiting surface 24th the combustion chamber 23 . The exhaust valve 26 can be a poppet valve, as is known from the prior art. In this way, a reliable and durable solution is provided which is able to withstand a cylinder pressure of up to 25 MPa and more and a cylinder gas temperature of more than 2000 K, while providing a gas-tight seal of the outlet opening 28 provides during the combustion cycle.

The ICE 2nd can be a camshaft 25th to control movement of the exhaust valve 26 and opening and closing the exhaust valve. The camshaft 25th includes a cam 34 which is set up to move the valve head 30th for opening and closing the outlet opening 28 to effect. If the camshaft 25th turns, the end section follows 36 of the exhaust valve 26 the cam what the movement of the valve head 30th causes. The exhaust valve 26 may be biased toward its closed position, as is known in the art, for example by means of a spring (not shown).

According to embodiments in which the ICE 2nd is a four-stroke ICE, the inlet arrangement can 16 an inlet valve 42 include whose movements from a camshaft 44 can be controlled in a similar manner as for the exhaust valve 26 how this in 2nd is shown. According to embodiments in which the ICE 2nd is a two-stroke ICE, an inlet port can instead be inserted into the cylinder bore 12th be provided as is known in the art. The inlet valve 42 or the inlet opening is from the outlet valve 26 trained separately. This means intake gas through the intake valve 42 or the inlet opening directly into the cylinder bore 12th flows in and not through the exhaust valve 26 passes through, and that the exhaust gases directly from the cylinder bore 12th through the exhaust valve 26 pass through and not through the inlet valve 42 or pass through the inlet opening.

The ICE 2nd includes a second valve 40 that in the exhaust line 6 is arranged. The second valve 40 is set up the outlet pipe 6 to close and open. The second valve 40 will open after the exhaust valve 26 has started to open within a range of 10 to 90 degrees crankshaft angle after the exhaust valve has started to open. The second valve 40 has a higher valve area opening speed than the exhaust valve 26 . In this way, exhaust gases are subject to little throttling when passing through the second valve 40 in comparison to when they pass through an outlet valve in a conventional ICE without a second valve in the outlet line. Less throttling means more energy for recovery from the exhaust gases in the turbine 8th is available with the outlet pipe 6 connected is.

If the exhaust valve 26 with that begins to open, pressure increases in a first section 60 the outlet pipe 6 from the outlet opening 28 to the second valve 40 gradually before the second valve begins to open. The pressure in the cylinder bore is suitable 12th and in the first section 60 the outlet line 6 substantially immediately before the second valve 40 it starts to open. Because the second valve 40 is closed while the exhaust valve 26 with this begins to open, exhaust gases act during the initial phase of opening the exhaust valve 26 through the exhaust valve 26 flow through, not to transfer exhaust gases to the turbine 8th out. The higher valve opening speed of the second valve 40 compared to the exhaust valve 26 provides an efficient transfer of exhaust gases through a second section 62 the outlet pipe 6 to the turbine safely. The second section 62 the outlet pipe 6 extends from the second valve 40 to the inlet 29 the turbine 8th .

9 represents schematically the opening and closing of the exhaust valve 26 and the second valve 40 A complete four-stroke cycle of a four-stroke ICE 2nd is in along the axis 9 shown. The exhaust valve 26 and the second valve 40 are opened and closed at the same frequency, ie the outlet valve 26 and the second valve 40 open the same number of times during ICE operation 2nd . However, they remain open for different lengths of time. For example, since the exhaust valve 26 before the second valve 40 opens, the outlet valve 26 stay open for a longer period of time than the second valve 40 to allow all exhaust gases, the combustion chamber 23 to leave. This is based on the solid line in 9 shown. The second valve 40 can simultaneously with the exhaust valve 26 close as shown by the solid line in 9 is shown. Alternatively, the second valve 40 close later than the exhaust valve, which is in 9 is shown by the dashed line. Of course, the second valve 40 getting closed, if the exhaust valve 26 it starts to open again.

According to some embodiments, the second valve 40 have a valve surface opening speed> 0.75 m ² / s. In this way, the second valve can open faster than through the outlet valve 26 be provided, and efficient recovery of energy from the exhaust gases in the turbine 8th can be achieved on the downstream side of the second valve 40 is arranged. The valve surface opening speed can be during the opening of the second valve 40 vary. For example, the valve surface opening speed may change during the opening of the second valve 40 increase.

Regarding 1 and 2nd can the second valve 40 be arranged at a position in the outlet line within a range of 1% to 25% of the maximum volume, V _MAX , downstream of the outlet opening, preferably within a range of 1% to 15% of the maximum volume, V _MAX , downstream of the outlet opening. This means that the first section 60 the outlet pipe 6 has a volume within a range of 1% to 25% of the maximum volume, V _MAX , or, according to alternative embodiments, within a range of 1% to 15% of the maximum volume, V _MAX . Hence the volume of the first section 60 the outlet pipe 6 a volume in relation to V _MAX , which is a pressure equalization between the combustion chamber 23 and the first section 60 the outlet pipe 6 allowed before the second valve 40 it starts to open, at least to a large extent. In other words, the second valve 40 opens when the pressure equalization between the cylinder bore and the first section 60 the outlet pipe 6 has taken place to a significant degree. Furthermore, the second valve 40 open when the exhaust valve 26 has released a sufficient area so as not to produce any appreciable throttling of the exhaust gases when the second valve 40 is opened.

Within a range of 10 to 90 degrees crankshaft angle after the exhaust valve 26 has started to open, the second valve begins 40 thus opening, preferably within a range of 10 to 40 degrees crankshaft angle after the exhaust valve 26 has started to open, or within a range of 30 to 40 degrees crankshaft angle after the exhaust valve 26 has started to open. In this way there is pressure equalization between the combustion chamber 23 and the first section 60 the outlet pipe 6 allowed before the second valve 40 it starts to open, at least to a large extent. Suitably the second valve 40 Opened no more than 10 degrees crankshaft angle after the BDC.

As mentioned above, it forms at least one cylinder arrangement 4th a combustion chamber 23 out, and the cylinder assembly 4th has a maximum volume, V _MAX , between a bottom dead center, BDC, of the piston 10th and an upper inner delimiting surface 24th the combustion chamber 23 on. According to embodiments, the inlet 29 the turbine has a turbine inlet area, A _TIN , with the outlet conduit 6 has an outlet line volume, V _EXH , extending from the outlet opening 28 to the turbine inlet area, A _TIN , and wherein the outlet line volume, V _EXH ≤ 0.5 times the maximum volume, V _MAX . In this way, the outlet line 6 have a volume suitable for efficiently transferring the exhaust gases to the turbine 8th . Specifically, due to the above volume of the first section 60 the outlet pipe 6 , due to which the second section 62 the outlet pipe 62 has a volume within a range of 75% to 99% of V _MAX , the second section 62 a volume that is capable of efficiently exhausting the second valve 40 to the turbine 8th to transfer and therefore the turbine 8th to drive efficiently.

The turbine wheel inlet area, A _TIN , is provided at an opening of a housing of the turbine through which exhaust gases to the turbine wheel 27 be allowed through. The turbine wheel inlet area, A _TIN , may suitably be the nozzle throat area of the turbine 8th be. The nozzle neck surface may also be referred to as a turbine housing neck surface, critical turbine housing surface, or the like, and may often be specified for a particular turbine. If the nozzle throat for a particular turbine is not specified and / or if the position of the nozzle throat area is not specified, the Turbinenradeinlassfläche, A _TIN extends perpendicular to a flow direction of exhaust gas. In embodiments of turbines in which the exhaust line extends along a portion of the turbine wheel, for example in a worm, such as in a twin-scroll turbocharger, the turbine wheel inlet area, A _TIN , is defined as the section of the exhaust line in which the turbine wheel is first exposed to the exhaust gases emanating from the relevant cylinder arrangement.

As mentioned above, the outlet arrangement is 14 set up to have an outlet flow area, A _CYL , of the outlet _opening 28 open and close during an exhaust sequence. The outlet pipe 6 connects the outlet opening 28 with the turbine 8th . The outlet pipe 6 has an outlet line volume, V _EXH . In 1 the outlet pipe volume, V _EXH , is shown as a box. In practice, the outlet pipe extends 6 between the outlet flow area, A _CYL , and the turbine inlet area, A _TIN , on both sides of the second valve 40 . _Accordingly , the outlet line volume, V _EXH , is the volume of the outlet line between the outlet flow area, A _CYL , and the outlet _opening 28 the turbine inlet area, A _TIN .

According to these embodiments, the outlet pipe connects 6 only the outlet opening fluidly with the inlet 29 the turbine. This means that the outlet pipe 6 forms a separate conduit that extends between the outlet flow area, A _CYL , and the turbine inlet area, A _TIN . The separate line does not have to have any further inlets or outlets for exhaust gases. Therefore, the turbine wheel inlet area, A _TIN , is a dedicated inlet area of the turbine 8th for the specific outlet flow area, A _CYL , which is thus via the outlet line 6 connected is.

The turbine wheel 27 the turbine may have an impeller (not shown) for compressing and delivering intake air into the intake assembly 16 be connected. In some embodiments, the turbine wheel 27 be an axial turbine wheel. A turbine 8th , which comprises an axial turbine wheel, can have a low back pressure. According to embodiments, however, the turbine wheel can be a radial turbine wheel, which can also have a low back pressure.

In some embodiments, the cylinder assembly 4th a total swept volume, V _S , in the cylinder bore 12th between bottom dead center, BDC, and top dead center, TDC, of the piston 10th have, where 0.3 <Vs <4 liters. For example, it should be mentioned that in the lower area of V _S the cylinder arrangement 4th can form part of an internal combustion engine for a passenger vehicle, and that in the middle and upper region of Vs the cylinder arrangement 4th can form part of an internal combustion engine for a heavy vehicle such as a truck, a bus or a construction vehicle. The cylinder arrangement can also be in the upper range of V _S 4th form part of an internal combustion engine, for example a generator set (genset), for use in seafaring, or for rail-based use (train).

3a to 3c represent schematically cross sections through a second valve 40 that in an outlet pipe 6 is arranged, according to embodiments. The outlet line 6 and the second valve 40 illustrate an example of the exhaust pipe 6 and the second valve 40 of the 1 and 2nd .

The second valve 40 includes a valve body 64 that is in a valve body 66 is arranged. The valve body 64 has a through opening 68 on. The valve body 64 is in the valve housing 66 so movable that the through opening 68 either a fluid connection between the first section 60 the outlet pipe 6 and the second section 62 the outlet pipe 6 on both sides of the second valve 40 provides, or that the valve body 64 a fluid connection between the first section 60 and the second section 62 the outlet pipe 6 prevented.

In other words, the valve body 64 a flow-permeable section area in which a flow of an exhaust gas through the second valve 40 passes, and a zero flow section area where the outlet pipe 6 at the second valve 40 closed is. In 3a is the valve body 64 shown arranged within the zero flow section area. The zero flow section area includes all positions of the valve body 64 in which a flow through the second valve 40 is prevented. In 3b has the valve body 64 reaches the beginning of the flow-permeable section area, ie just when the second valve 40 it begins to open, connects the through opening 68 the first and the second section 60 , 62 the outlet pipe 6 fluidic. In 3c is the valve body 64 also shown within the flow-permeable section area, the through opening 68 has reached a position in which the second valve 40 is fully open. As a result, the valve body is located 64 within the flow-permeable section area, as long as the through-opening the first and the second section 60 , 62 the outlet pipe 6 fluidly connects.

As with 3a can be concluded, and since the valve body 64 together with the through opening 68 at a distance from the fluid line 6 is arranged is the valve body 64 set up to be set in motion before the valve body 64 reached the flow-permeable section area. This means that the valve body 64 can be accelerated while the valve body 64 located within the zero flow section area. Consequently, the valve body can have a considerable speed when the valve body 64 reached the flow-permeable section area. Therefore, the second valve can provide a high valve surface opening speed, especially compared to a valve that needs to be accelerated from a rest position when it is opened, for example a poppet valve. In an alternative embodiment, the valve body can be in constant motion, thereby avoiding the need to accelerate the valve body. Instead, the valve body can be moved at a speed that is higher Valve area opening speed provides as the exhaust valve. This can be done in the embodiments below 4a to 4e be achieved.

3a to 3c represent the functioning of the second valve.

3a to 3c also put a second valve 40 in accordance with embodiments in which the valve body is configured to reciprocate. This means that the valve body 64 is set up in the valve housing 66 move linearly back and forth. If the valve body 64 moves back and forth, it moves between the zero flow section area and the flow permeable section area.

Alternative embodiments of the second valve 40 , which provide a high valve area opening speed, are shown schematically in 4a to 4e shown.

In the embodiments of the second valve according to 4a to 4e is the valve body 64 set up to turn.

According to the embodiments according to 4a and 4b is the valve body 64 set up to center around an axis of rotation 70 to rotate, which is substantially perpendicular to the outlet pipe 6 extends. This means that the axis of rotation 70 substantially perpendicular to the through opening 68 extends. If the valve body 64 around the axis of rotation 70 turns, the valve body moves 64 from the zero flow section area to the flow permeable section area. In 4a is the valve body 64 shown in the zero flow section area. As described above, the valve body is 64 set up to be set in motion before the valve body 64 reached the flow-permeable section area. In 4b is the valve body 64 shown in the flow-permeable section area. The valve body 64 may rotate one or more revolutions as it moves between the zero flow section area and the flow permeable section area. The valve body 64 can be rotated continuously. Alternatively, the valve body 64 swing back and forth as it moves between the zero flow section area and the flow permeable section area.

4c shows a cross section along the outlet line 6 , while 4d and 4e Cross sections perpendicular to the outlet pipe 6 through the second valve 40 represent. In the embodiments according to 4c to 4e is the valve body 64 set up to center around an axis of rotation 72 to rotate, which is essentially parallel to the outlet line 6 extends. This means that the axis of rotation 70 essentially aligned with the through opening 68 extends. If the valve body 64 around the axis of rotation 72 turns, the valve body moves 64 from the zero flow section area to the flow permeable section area. As described above, the valve body is 64 set up to be set in motion before the valve body 64 reached the flow-permeable section area. The valve body 64 may rotate one or more revolutions as it moves between the zero flow section area and the flow permeable section area. The valve body 64 can be rotated continuously. Alternatively, the valve body 64 swing back and forth as it moves between the zero flow section area and the flow permeable section area.

In the embodiments according to 3a to 4e became the through opening 68 shown with the same diameter as the outlet pipe 6 . In alternative embodiments, the through opening 68 have a larger diameter than the outlet line 6 .

According to alternative embodiments, the valve body 64 not be provided with a through opening. For example, the valve body can be provided with a recess instead of a through opening. A further alternative can represent that the valve body blocks the outlet line in the zero flow section area and that it is at least partially moved out of the outlet line in the flow-permeable section area.

According to some embodiments, the movement of the valve body 64 controlled by a mechanical connection, for example to a crankshaft or a camshaft of the ICE, for example by means of gear wheels, a chain, a belt or a rocker arm mechanism. Such a mechanical connection is set up to coordinate the opening and closing of the second valve with the hooks of the piston in the cylinder bore and in such a way that the second valve opens after the exhaust valve. A Geneva drive can form part of the mechanical connection.

In the embodiment according to 2nd becomes the movement of the second valve 40 , ie the valve body of the second valve 40 , from a control unit 54 and an electric motor 50 controlled. The control unit 54 controls the electric motor 50 to the valve body of the second valve 40 to move between the zero flow section area and the flow permeable section area. The Control unit 54 poses using a sensor 52 that with the control unit 54 is connected, a rotational position of the crankshaft 20 forth. Hence the control unit 54 able to open and close the second valve for example with the exhaust valve 26 to schedule. The control unit 54 can be set up to set different times for opening and / or closing the second valve 40 based on, for example, a speed of the crankshaft 20 , the current load on the ICE 2nd and / or ICE operating conditions 2nd or a vehicle 1 in which the ICE 2nd is installed. The electric motor 50 can directly with the valve body of the second valve 40 be connected, or via a transmission or other mechanisms, such as a Maltese cross gear.

The control unit 54 may include a computing unit that may take substantially the form of any suitable type of processor circuit or microcomputer, such as a digital signal processor (DSP) circuit, a central processing unit (CPU), a processing unit, one Processing circuit, a processor, an application specific integrated circuit (ASIC), a microprocessor or other processor logic that can interpret and execute instructions. The term computing unit used herein may represent a processor circuit that includes multiple processor circuits, such as one, some, or all of the above. The control system may include a storage unit. The calculation unit is connected to the storage unit, which supplies the calculation unit, for example, with stored program code and / or with stored data, which the calculation unit requires in order to be able to carry out its calculations. The calculation unit can also be set up to store partial or final results of calculations in the storage unit. The storage device may comprise a physical device used to store data or programs on a temporary or permanent basis, ie sequences of instructions. The control unit 54 can be set up to further functions of the ICE 2nd to control, and it can, for example, be part of an engine control system of the ICE 2nd form. The control unit 54 can be via one or more communication buses, for example with the electric motor 50 and / or the sensor 52 communicate.

5 and 6 represent embodiments of the ICE 2nd represent where more than one cylinder assembly with a turbine 8th can be connected.

5 illustrates embodiments in which two cylinder arrangements 4th with a turbine 8th are connected via a turbine wheel inlet area, A _TIN , ie the two cylinder arrangements 4th share the same turbine inlet area, A _TIN . As a result, those of the outlet port arrangements 14 outgoing outlet pipe branches 6 ' , 6 " of the two cylinder arrangements 4th connected to a common outlet line 6 train that to the turbine 8th and leads to the turbine inlet area, A _TIN . Because a certain degree of exchange flow between the two outlet pipe branches 6 ' , 6 " is present when exhaust gases from one of the cylinder assemblies 4th to the turbine inlet area, A _TIN , the condition described above can _apply : V _EXH ≤ 0.5 * V _MAX for the total exhaust power volume, V _EXH . More specifically, the total exhaust line volume, V _EXH , is from the volume of A _{CYL of} an exhaust valve 26 in a first of the outlet line branches 6 ' , 6 " and from the second valve 40 in a second one of the outlet line branches 6 ' . 6 "to A _{TIN of} the turbine 8th educated. Because when exhaust gases from the cylinder arrangement 4th that with the first outlet line branch 6 ' connected to the turbine inlet face, A _TIN , the second valve assembly 40 in the second outlet line branch 6 appropriately closed and vice versa.

6 illustrates embodiments in which two cylinder arrangements 4th with a turbine 8th via two separate outlet lines 6 are connected, each leading to a turbine wheel inlet area, A _TIN . The turbine wheel inlet areas, A _TIN , are arranged such that it can be assumed to be with the turbine 8th at one position of the turbine 8th are connected. Consequently, the turbine in these embodiments is a multi-input turbine that has at least one additional inlet 29 ' has, in addition to the inlet 29 . This means that further admission 29 ' from the inlet 29 is separate. The exchange flow between two turbine inlet faces, A _TIN , is negligible in these embodiments. Consequently, for each of the outlet lines 6 the condition described above: V _EXH ≤ 0.5 * VMAx apply.

Generally there are volumes of connections to or from the outlet line 6 not considered forming part of the exhaust pipe volume, V _EXH , if such connections have a cross-sectional area below a limit. According to embodiments, the outlet line volume, V _EXH , may not include all volumes associated with the outlet line 6 are connected via a connection which has a total connection cross-sectional area, A _CON ≤ 0.022 times the maximum volume, V _MAX , ie A _CON ≤ 0.022 * V _MAX . With such a small cross-sectional area, A _CON , any flow of exchange is through a Connection negligible. It should be noted that the factor 0.022 implies a conversion from volume to area and in this case has the unit m ^-1 .

In 6 were two exemplary connections 7 with total minimum connection cross-sectional areas, A _CON . Such compounds can be mentioned purely by way of example 7 form part of an exhaust gas recirculation (EGR) system, or they can be connected to sensors, etc.

For a specific turbine, turbine test results are entered in a turbine map. On the basis of such turbine diagrams, a suitable turbine can be selected for a certain type of ICE. In one type of turbine diagram, multiple turbine speed lines can be plotted against the turbine over a corrected flow and pressure ratio. Such turbine speed lines can represent so-called reduced turbine speeds, RPM _RED , for example. The corrected flow can be represented, for example, by a reduced mass flow, m ' _RED . The SAE J1826 and SAE standards J922 relate to test procedures, nomenclature and terminology of turbochargers and are incorporated herein by reference for further details of turbine diagrams and parameters related to turbochargers. m ' _RED = m' * (T) ^1/2 / P, where m 'is an actual mass flow rate through the turbine wheel, T is the exhaust gas temperature upstream of the turbine wheel, and P is the exhaust gas pressure upstream of the turbine wheel. In 7 FIG. 4 is a schematic example of a turbine diagram of a turbine such as a turbocharger.

For a relevant turbine, a normalized effective flow rate, γ, can be defined as γ = A _TURB / V _MAX . Therefore, the turbine inlet area, A _TIN , can be defined relative to the maximum volume, V _MAX , of the cylinder assembly. As follows, A _TURB = (ATIN / ATOT) * m'RED * (R / (K (2 / (K + 1) ^X ))) ^1/2 , where X = (κ + 1) / (K - 1). As mentioned above, A _{TIN is} the turbine inlet area connected to the outlet flow area, A _CYL , of the cylinder _assembly . The turbine can have more than one inlet surface. Consequently, A _{TOT is} an entire inlet area of the turbine, ie A _TIN and all other turbine inlet areas, A _TINX etc. (A _TOT = A _TIN + A _TINX + ...). R is the specific gas constant. An exemplary value for R can be 287. κ = C _p / C _v , where C _{p is} the specific heat capacity at constant pressure of the exhaust gases, and where C _{v is} the specific heat capacity of the exhaust gases at constant volume. An exemplary value of κ can be 1.4, at a temperature of 293 K.

A _TURB can be obtained as a reduced mass flow, m ' _RED , of the turbine with a pressure ratio between an inlet side and an outlet side of the turbine of, for example, 2.5 to 3.5 and with a wing tip speed of the turbine wheel of, for example, 450 m / s. A _TURB for a particular turbine can be obtained, for example, by taking the reduced mass flow, m ' _RED , from a relevant turbine diagram for a turbine speed that corresponds to the relevant wing tip speed at the relevant pressure ratio, and by A _TURB with relevant data for the turbine and their operating conditions is calculated. Then γ can be calculated. According to embodiments herein, γ> 0.22 m ^-1 .

In some embodiments, the turbine has a normalized effective flow area, γ, which is defined as γ = A _TURB / V _MAX , where γ> 0.22 m ^-1 , where A _TURB = (A _TIN / A _TOT ) * m ' _RED * (R / (K (2 / (K + 1) ^X ))) ^1/2 , where X = (κ + 1) / (K - 1), where A _{TOT is} an entire inlet area of the turbine ( 8th ) and where A _TURB with a reduced mass flow, m ' _RED , of the turbine 8th at a pressure ratio of 2.5 to 3.5 between an inlet side and an outlet side of the turbine 8th and at a wing tip speed of 450 m / s of the turbine wheel ( 27 ) is preserved.

In such a turbine 8th energy from the exhaust gases can be harnessed by the quick opening second valve 40 step through. As a result, a small pressure drop can be provided when the second valve 40 opens and exhausts through the second section of the exhaust line 6 are directed to the turbine, and much of the energy in the exhaust gases can be converted into useful work if the exhaust gases pass through the turbine wheel of the turbine 8th expand.

8th represents a procedure 100 to control an ICE. The ICE can be an ICE 2nd according to an aspect and / or an embodiment as described herein. Reference is therefore made to the above embodiments.

• - Öffnen 102 des Auslassventils 26,
• - Drehen 104 der Kurbelwelle 20 um einen vorgegebenen Kurbelwellenwinkel innerhalb eines Bereichs von 10 bis 90 Grad, und danach
• - Öffnen 106 des zweiten Ventils 40 bei einer höheren Ventilflächenöffnungsgeschwindigkeit als das Auslassventil 26.

The procedure 100 includes the steps in the order given:

• - To open 102 of the exhaust valve 26 ,
• - Rotate 104 the crankshaft 20 by a predetermined crank angle within a range of 10 to 90 degrees, and thereafter
• - To open 106 of the second valve 40 at a higher valve surface opening speed than the exhaust valve 26 .

In this way the pressure in the combustion chamber 23 and the outlet pipe 6 upstream of the second valve 40 be balanced before the second valve at the high valve surface opening speed by a predetermined crankshaft angle after the exhaust valve 26 is opened.

According to a further aspect, a computer program for performing a method for controlling an ICE 2nd provided, which comprises instructions which, when the program is executed by a computer, cause the computer to carry out the method 100 according to an aspect and / or an embodiment as described herein. The computer can, for example, be a central processing unit of the control unit 54 be described above.

According to another aspect, there is provided a computer readable medium comprising instructions that, when executed by a computer, cause the computer to perform the method 100 according to an aspect and / or an embodiment as described herein. The computer can in turn be a central processing unit of the control unit 54 be described above.

It should be understood that the foregoing illustrates several exemplary embodiments and that the invention is defined only by the appended claims. One skilled in the art will recognize that the exemplary embodiments may be modified and that different features of the exemplary embodiments may be combined to produce embodiments other than those described herein without departing from the scope of the invention as defined by the appended claims.

QUOTES INCLUDE IN THE DESCRIPTION

This list of documents listed by the applicant has been generated automatically and is only included 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.

Patent literature cited

• US 3961484 [0006]
• US 4535592 [0008]
• DE 102010008264 [0010]

Claims (15)

Internal combustion engine (2) comprising a crankshaft (20), at least one cylinder arrangement (4) and a turbine (8), the at least one cylinder arrangement (4) forming a combustion chamber (23) and a cylinder bore (12), a piston (10 ), which is arranged to move back and forth in the cylinder bore (12) between a top dead center and a bottom dead center, comprises an exhaust valve (26) and an exhaust opening (28), which on an inner delimiting surface of the combustion chamber ( 23), the outlet valve (26) comprising a valve head (30) which is set up to seal against a valve seat (32) of the outlet opening (28), an outlet line (6) closing from the outlet opening (28) an inlet of the turbine (8), wherein the internal combustion engine (2) comprises a second valve (40) which is arranged in the outlet line (6), the second valve (40) being arranged to close the outlet line (6) close and open , and wherein the second valve (40) is opened after the outlet valve (26) has started to open, characterized in that the second valve (40) has a higher valve surface opening speed than the outlet valve (26), within a range from 10 to 90 degrees crankshaft angle after the exhaust valve (26) starts opening, the second valve (40) starts opening. Internal combustion engine (2) after Claim 1 , the at least one cylinder arrangement (4) forming a combustion chamber (23), the cylinder arrangement (4) having a maximum volume, V _MAX , between a bottom dead center, BDC, of the piston (10) and an upper inner delimiting surface (24) of the combustion chamber (23), and wherein the second valve (40) is arranged at a position in the exhaust line (6) within a range of 1% to 25% of the maximum volume, V _MAX , downstream of the exhaust opening (28), preferably within a range of 1% to 15% of the maximum volume, V _MAX , downstream of the outlet opening (28). Internal combustion engine (2) after Claim 1 or 2nd , the at least one cylinder arrangement (4) forming a combustion chamber (23), the cylinder arrangement (4) having a maximum volume, V _MAX , between a bottom dead center, BDC, of the piston (10) and an upper inner delimiting surface (24) of the combustion chamber (23), the inlet (29) of the turbine (8) having a turbine inlet area, A _TIN , the outlet line (6) having an outlet line volume, V _EXH , which extends from the outlet opening (28) to the Turbine inlet area, A _TIN , and wherein the outlet pipe volume, V _EXH ≤ 0.5 times the maximum volume, V _MAX . Internal combustion engine (2) according to any one of the preceding claims, wherein within a range of 10 to 40 degrees crankshaft angle after the exhaust valve (26) begins to open, the second valve (40) begins to open, preferably within a range of 30 to 40 degrees crankshaft angle after the exhaust valve (26) begins to open. Internal combustion engine (2) according to any one of the preceding claims, wherein the second valve (40) comprises a valve body (64), the valve body (64) a flow-permeable portion in which a flow of an exhaust gas passes through the second valve (40), and comprises a zero flow section area in which the outlet line (6) at the second valve (40) is closed, and wherein the valve body (64) is set up to be set in motion before the valve body (64) allows the flow-through Section area reached. Internal combustion engine (2) according to any one of the preceding claims, wherein the valve body (64) is arranged to rotate. Internal combustion engine after Claim 6 , wherein the valve body (64) is set up to rotate about an axis of rotation (70) which extends substantially perpendicular to the outlet line (6). Internal combustion engine (2) after Claim 6 , wherein the valve body (64) is set up to rotate about an axis of rotation (70) which extends substantially parallel to the outlet line (6). Internal combustion engine (2) according to one of the Claims 1 to 5 wherein the valve body (64) is arranged to move back and forth. Internal combustion engine (2) according to one of the preceding claims, wherein the outlet power (6) only fluidly connects the outlet opening (28) to the inlet (29) of the turbine (8). Internal combustion engine (2) according to one of the preceding claims, wherein the turbine is a multi-inlet turbine which comprises at least one further inlet (29 '). Internal combustion engine (2) after Claim 2 or 3rd , wherein the outlet line (6) has an outlet line volume, V _EXH , and wherein the outlet power volume does not include all volumes which are connected to the outlet line (6) via a connection (7) which has a total connection cross-sectional area, A _CON ≤ 0.022- times the maximum volume, V _MAX . Internal combustion engine (2) after Claim 2 or 3rd , the turbine (8) having a normalized effective flow area, γ, which is defined as γ = A _TURB / V _MAX , where γ> 0.22 m ^-1 , where A _TURB = (A _TIN / A _TOT ) * m ' _RED * (R / (K (2 / (K + 1) ^X ))) ^1/2 , where X = (κ + 1) / (K - 1), where ATOT covers an entire inlet area of the turbine (8) and where A _TURB at a reduced mass flow, m ' _RED , of the turbine (8) at a pressure ratio of 2.5 to 3.5 between an inlet side and an outlet side of the turbine (8) and at a wing tip speed of 450 m / s of the turbine wheel (27) is obtained. Vehicle (1) comprising an internal combustion engine (2) according to one of the preceding claims. Method (100) for controlling an internal combustion engine (2), the internal combustion engine (2) comprising at least one cylinder arrangement (4), a crankshaft (20) and a turbine (8), the at least one cylinder arrangement (4) comprising a combustion chamber (23 ) and a cylinder bore (12), a piston (10) which is set up to move back and forth in the cylinder bore (12) between a top dead center and a bottom dead center, a connecting rod which moves the piston (10) connects to the crankshaft (20), comprises an exhaust valve (26) and an exhaust opening (28) which is arranged on an inner delimiting surface of the combustion chamber, the exhaust valve (26) comprising a valve head (30) which is set up to sealing against a valve seat (32) of the outlet opening (28), an outlet line (6) extending from the outlet opening (28) to an inlet of the turbine (8), the internal combustion engine (2) comprising a second valve (40), that in the A outlet line (6) is arranged, the second valve (40) being set up to close and open the outlet line (6), and the method (100) comprises the steps in the order given: - opening (102) the exhaust valve (26), - Rotating (104) the crankshaft (20) by a predetermined crankshaft angle within a range from 10 to 90 degrees, and thereafter - Opening (106) of the second valve (40) at a higher valve surface opening speed than the outlet valve (26).

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