DE10001489B4 - Internal combustion engine with at least one cylinder - Google Patents

Abstract

Internal combustion engine (2), in particular direct injection Otto internal combustion engine, with a plurality of cylinders (3), with an intake system (1) and with facilities (11) for exhaust gas recirculation, which with an exhaust gas recirculation valve (10) opposite the intake system (1) can be shut off, wherein the intake system (1) at least two independent has suction pipes (1a, 1b) formed from each other over which each air is sucked and which in each case with the at least a cylinder (3) are in communication with one of the intake pipes (1b) has a connection with the exhaust gas recirculation valve (10), while the other intake pipe (1 a) is sucked exclusively air, wherein the two intake pipes (1a, 1b) each have at least one throttle device (15, 18) for influencing one of the two intake pipes (1a, 1b) flowing through Have volume flow, and wherein the two intake pipes (1a, 1b) in each case a collecting pipe (8, 9) and for each of the cylinders respectively at least one of the respective manifold (8, 9) with the cylinder connecting intake duct (6, 7, 12).

Description

The The invention relates to an internal combustion engine, in particular a direct injection Otto internal combustion engine, with at least one cylinder after the defined in more detail in the preamble of claim 1 Art.

From the US 5,329,912 A For example, an intake system for an internal combustion engine is known, in which an intake pipe divides into two intake ports for each cylinder. It is provided in each case to supply one of the intake ducts fuel or a fuel-air mixture and the other intake duct recirculated exhaust gas. As a result, a sufficient power of the internal combustion engine is to be achieved with low exhaust emissions.

The JP 11148429 A describes an internal combustion engine in which lead to each cylinder two intake ports, which emanate from different intake manifolds.

Out The general state of the art is a variety of internal combustion engines with intake systems or intake pipes for the supply of air and / or recirculated exhaust gas known in the cylinder of the internal combustion engine. It is common that the internal combustion engine intake pipes, which with devices for throttling the intake air and for detecting the air mass or air quantity, which has been sucked, are provided. There are also There are internal combustion engines that provide a lockable connection of the intake manifold having the exhaust side of the internal combustion engine, so that in Part-load operation of the internal combustion engine exhaust gas into the intake pipe can. This operation of an internal combustion engine with a so-called Exhaust gas recirculation makes it possible in part-load operation of the internal combustion engine advantages in terms of fuel consumption and pollutant emissions of To reach internal combustion engine.

In addition, intake systems are known from the prior art, in which by selecting the tube length of the intake system, a resonance effect is achieved in the intake air oscillating in the intake system, so that it improves the charge of the respective cylinder with the intake air and thus to an improved Burning comes. Such a resonance intake manifold is for example in the DE 41 26 428 C2 described.

As a further development of these resonance intake manifolds and intake systems are known which change the decisive for the resonance effect length of the intake manifold via flaps, shut-off elements or the like. Such, so-called Schaltsaugrohr is in the DE 195 04 255 A1 described, in which case the switching elements are designed as throttle valves. To compensate for the thermal expansion of the intake pipe, these throttle valves are mounted longitudinally displaceable on their shafts to ensure their function in all thermal conditions which may be present in the internal combustion engine or the intake manifold.

One way of exhaust gas recirculation, so the supply of exhaust gas in the intake, for example, describes the DE 197 25 011 C1 in which the exhaust gas is supplied via a ring channel surrounding the intake line.

Besides that is it is additionally known from the general state of the art, internal combustion engines with two intake valves per cylinder. In this Case shares a collection volume with the respective cylinder connecting intake pipe in front of the cylinder in two sub-pipes, wherein each one of the sub-pipes connected to one of the intake valves is. In a particular embodiment this example designed as a riser pipe, which the actual intake manifold connects to the intake valves can arranged in one of the tubes a throttle or shut-off device be. This makes it possible that the inflowing into the cylinder Air or the air-exhaust mixture through one of the intake valves with a larger volume flow is initiated as by the other inlet valve. This will it possible the inflowing into the cylinder, sucked gas a roller-shaped To give movement or a spin. This so-called charge movement is predominantly in direct injection diesel or gasoline engines makes sense because thereby the fuel injected into the cylinder correspondingly can distribute this charge movement in the cylinder. This will it possible to optimize the combustion of the fuel accordingly, since one is able to do this by the combination of the charge movement, the location of the injector and the geometrical conditions in the cylinder, e.g. by a design of a piston surface of an oscillating in the cylinder Piston, influence.

The solutions described above for supplying an internal combustion engine with its intake air and / or recirculated exhaust gas have the disadvantage that, in particular in partial load operation to achieve a high exhaust gas recirculation rate, a considerable pressure difference between the exhaust gas and the air in the intake system is required for the recirculation a sufficient amount of exhaust gas in the intake system of Brennkraftma ensure that

One Another disadvantage of the systems described above is in their bad dynamic response. For example when changing from the partial load operation of the internal combustion engine, the Internal combustion engine works here with a comparatively high Amount of recirculated exhaust gas, to the full load operation of the internal combustion engine, which in general works without exhaust gas recirculation, the exhaust gas remaining in the entire intake system is used up first before the internal combustion engine is supplied exclusively with fresh air and thereby achieve their full potential performance.

It It is an object of the invention to provide an internal combustion engine with an intake system and with facilities for exhaust gas recirculation too which allows it with low differential pressure to the intake manifold a feeder of high exhaust gas recirculation quantities to realize and what about it In addition, a very high dynamic when changing from a part-load operation with exhaust gas recirculation too a full load operation without exhaust gas recirculation allows.

According to the invention this Problem solved by the features mentioned in claim 1.

By the at least two intake pipes in the intake system, each one the intake pipes in each case with the at least one cylinder in connection stands, it is possible the suction for the partial load operation and the full load operation on two separate intake pipes split up. It is only one of the two intake pipes with the exhaust gas recirculation valve in connection and forms practically a partial load suction pipe, which predominantly used in a motor operation up to about 3500 revolutions per minute becomes. This partial load intake pipe can be ideal for the introduction The exhaust gas can be tuned and can with a small volume and a short intake pipe length be educated.

The other intake pipe, namely a Vollastsaugrohr, can be designed for the full load conditions be and have a corresponding volume with a corresponding intake pipe. In addition, will it allows here the collection of the intake air exclusively via a cost-effective Sensor, e.g. a pressure sensor to detect because in full load the use of an air mass meter or similar device is not required. As the exhaust gas recirculation, so the introduction from very hot Exhaust gas into the intake system, only in the partial load intake pipe, This also gives the special advantage that the Vollastsaugrohr For example, be made of plastic or the like can, as for the Vollastsaugrohr not too high temperature resistance necessary is.

By the advantage that the partial load intake pipe with very small volume accomplished can be substantial advantages in terms of Dynamics when changing from part-load operation to full-load operation. In full load, here you can Both intake pipes are used to supply air, is thereby the residual exhaust gas located in the partial load intake pipe must be very small and this very small amount of residual exhaust gas gets very fast and in very high degree dilute supplied to the cylinders. As a result, in a very short time of exhaust gas containing exhaust gas on exhaust-free intake air and thus the best possible Power development of the internal combustion engine to be changed.

advantageous Refinements and developments of the invention will become apparent the dependent claims and the embodiments illustrated below with reference to the drawings.

It shows:

1 an inventive intake system for an internal combustion engine; and

2 an alternative embodiment of an intake system according to the invention for an internal combustion engine.

In 1 is intake system 1 for an internal combustion engine 2 recognizable. The internal combustion engine 2 has several cylinders 3 on, which in each case via an inlet valve 4 with a direction of flow of the sucked gases in front of the cylinder 3 arranged collecting space 5 keep in touch. The intake system 1 has two intake pipes 1a . 1b on, with each of the two intake pipes 1a . 1b from several intake ducts 6 . 7 and in each case a manifold 8th . 9 composed.

In each of the front of each cylinder 3 lying collection rooms 5 one of the intake ducts opens in each case 6 and 7 , wherein the intake duct 6 with the manifold 1a communicates, passing through this manifold 1a only air can be sucked in. Over the intake channel 7 is the collection room 5 in conjunction with the other manifold 9 , which in turn by means of an exhaust gas recirculation valve 10 , with an exhaust gas recirculation line 11 connected is.

In the in 1 illustrated embodiment, there is another intake passage 12 , which with a sub-channel 12 ' the collection room 5 With the manifold 9 in a node 13 connects and from the node 13 over another subchannel 12 '' a connection to the manifold 8th allows. In which the node 13 with the manifold 8th connecting sub-channel 12 '' is in each case a shut-off device 14 provided by which the connection between the two headers 8th . 9 is separable or that is controllable in the way that either exclusively the manifold 8th or only the manifold 9 with the collection room 5 of the respective cylinder 3 connected is.

The manifold 8th , which is mainly in full-load operation of the internal combustion engine 2 is used and therefore below as Vollastsammelrohr 8th is to be designated points in the flow direction of the sucked air before the branching of the first intake passage 6 to the cylinder 3 a throttle device 15 on. In front of the throttle device 15 , For example, an electronically controlled throttle the so-called e-gas 15 , is a connection with a vent line 16 arranged. This vent line 16 is connected to a crankcase (not shown) of the internal combustion engine and ensures that in the crankcase of the internal combustion engine 2 Collecting gases and vapors via the Vollastsammelrohr 8th can be returned to combustion. Because in the Vollastsammelrohr 8th a comparatively very low negative pressure of the sucked air is present, the diameter of this vent line 16 chosen comparatively large, with the pressure difference achieved initiating the from the crankcase of the internal combustion engine 2 originating gases and vapors in the Vollastsammelrohr 8th to enable. Furthermore, the Vollastsammelrohr 8th a pressure sensor 17 on. About this pressure sensor 17 can the pressure conditions in the Vollastsammelrohr 8th capture, which in turn allow conclusions about the intake air volume.

The manifold 9 which is mainly in partial load operation of the internal combustion engine 2 is used and therefore below as partial load collection tube 9 is referred to, also has a throttle device 18 or an e-gas 18 on. It is also in the partial load manifold 9 a pressure sensor 19 arranged. As in the partial load range, however, via the exhaust gas recirculation valve 11 additionally exhaust gas from the internal combustion engine 2 is sucked in, it is correspondingly complex on the basis of the pressure conclusions on the amount of gas in the partial load manifold 9 to draw. About the composition of the partial load manifold 9 gas does not allow the pressure alone accurate conclusions. However, this composition of the sucked gas for the control of the internal combustion engine 2 important is about a facility 20 for detecting the volume or the mass of the sucked air, in particular a Heißfileinuftmassenmesser 20 , which captures sucked portion of air, so that together with that of the pressure sensor 19 supplied pressure the composition of the partial load accumulation pipe 9 located sucked gas is known.

In the flow direction of the sucked gas after the exhaust gas recirculation valve 10 flows into the partial load collection pipe 9 another conduit element 21 , About a pipe element 21 stands the part load collection pipe 9 with a filter device (not shown) in combination, which filters out the resulting in a fuel tank, eg refueling, resulting vapors and these fuel vapors at a taking place from time to time regeneration of this filter device to the intake system 1 leads to this there again the combustion in the internal combustion engine 2 supply. Alternatively, the conduit element 21 divided into four individual lines (not shown), wherein the vent line 22 as close as possible to the intake valve or manifold 8th after the valve device 23 be arranged (not shown).

Another vent line 22 , which for venting the crankcase of the internal combustion engine 2 is provided, each opens into the intake ducts 7 the intake pipe 1b , Under certain circumstances, the vent line may also be in the manifold 8th , after the valve device 23 , are arranged (not shown). Due to the unlike the vent line 16 comparatively high pressure difference between the crankcase and the intake manifold 1b can the diameter of the vent line 22 in comparison to the vent line 16 be much smaller, because due to the higher pressure difference, the supply of gases or vapors from the crankcase in the intake manifold 1b or the intake ports 7 easily possible. Since the supply of highly oily vapors and gases in the flow direction to the exhaust gas recirculation valve 10 takes place, it can here to no pollution of the exhaust gas recirculation valve 10 come through the oils in the gases and vapors. In the systems according to the prior art, there is often formation of carbon deposits and / or crusting of the exhaust gas recirculation valve heated by the hot exhaust gas 10 by the oils contained in the gases and vapors. The intake system 1 On the other hand, it is relatively easy to keep clean and the amount of exhaust gas supplied remains in the region of the exhaust gas recirculation valve due to the constant flow cross sections and the lack of contamination 10 over the entire life of the intake system 1 at least approximately constant.

In the intake channels 6 the intake pipe 1a are in the area just above the cylinder 3 or collection space 5 valve devices 23 recognizable. These valve devices 23 allow it through the intake duct 6 to restrict or completely shut off incoming air. Is doing additionally via the intake duct 7 - or with open shut-off device 14 and / or the intake passage 12 - Air in the collection room 5 or cylinder 4 introduced, so it can cause a movement of the cylinder 3 to be introduced air, a so-called charge movement, come.

At the in 1 illustrated embodiment with a plenum 5 , which via the one inlet valve 4 with the cylinder 3 This would only matter if the injection of fuel into the plenum 5 takes place and this by the charge movement, which due to the valve device 23 can be generated so that in the plenum 5 can be better atomized or distributed. At the later in 2 to be described construction with two inlet valves 4a . 4b can the through the valve device 23 generated charge movement or a twist in the cylinder 3 incoming gases directly in the cylinder 3 be achieved, and so, especially in direct-injection internal combustion engines, optimize the quality of combustion in terms of exhaust gases and power output.

Because in the intake pipe 1b an air / exhaust mixture and in the intake pipe 1a Only air can be found by opening the valve device 23 , For example, from its closed position, the exhaust gas recirculation rate can be changed very quickly, as now added to the air / exhaust gas mass flow, an air mass flow.

2 now shows an alternative construction of an intake system 1 in combination with an alternative embodiment of the internal combustion engine 2 , As already mentioned above, the internal combustion engine 2 two inlet valves 4a . 4b for every cylinder 3 on, with the inlet valve 4a with the intake channel 6 and thus with the full load manifold 9 and the inlet valve 4b with intake channel 7 and thus with the partial load manifold 8th connected is.

In principle, the structure of the internal combustion engine 2 with the two intake valves 4a . 4b per cylinder and without collecting space 5 for both intake systems 1 realizable. Also in 1 illustrated embodiment of the internal combustion engine with a manifold 5 and an inlet valve 4 for the cylinder 3 is of course also in combination with the intake system 1 according to 2 conceivable.

2 otherwise shows a similar structure as 1 with the two intake pipes 1a . 1b containing the sensors described above 17 . 19 , the hot air mass meter 20 , the vent lines 16 . 22 , the line element coming from the fuel tank regeneration 21 , the exhaust gas recirculation valve 10 and the two throttle devices 15 . 18 exhibit. Only on the intake 12 and the shut-off device connected to it 14 is in the embodiment according to 2 completely omitted.

The two throttling devices 15 . 18 in both embodiments both completely independent of each other and with a common shaft 24 and a common servo motor (not shown) are driven, depending on whether the focus of the requirements on a high variability or on a cost-effective series solution.

In an independently trained control of the throttle devices 15 and 18 In principle, it would also be conceivable to use the valve devices 23 to renounce, as by the two completely independently formed intake pipes 1a . 1b and the throttling devices included in each of them 15 . 18 also in the two headers 8th . 9 With respect to the pressure very different conditions could be created, which is a charge movement in the cylinder 3 could allow incoming air or the air-exhaust mixture.

In addition to the so-called external exhaust gas recirculation, which by the intake system described above 1 , in particular through the intake pipe 1b with his manifold 8th and its intake ports 7 , as well as through the exhaust gas recirculation valve 10 with associated exhaust gas recirculation line 11 becomes possible, can be in the operation of the internal combustion engine 2 also achieve a so-called "internal" exhaust gas recirculation. This means that via an adjustment of the camshaft (not shown), the control of the intake valves 4 As well as exhaust valves (not shown) is realized in the way that a small amount of exhaust gas in the respective cylinder 3 remains. This is the respective cylinder 3 prefilled with a certain amount of exhaust gas, so that even if only pure air is sucked in, a certain amount of exhaust gas is present in the cylinder during combustion. About this so-called internal exhaust gas recirculation, however, only a small amount of exhaust gas can be "returned", but this can be done very quickly and with high accuracy with respect to the amount of exhaust gas. Nevertheless, it was through the intake pipe 1b with the exhaust gas recirculation valve 10 and the exhaust gas recirculation line 11 realized an additional external exhaust gas recirculation, which by a large line cross section and a short line length, so a relatively small flow resistance for the recirculated Exhaust gas, a particularly high exhaust gas recirculation at low differential pressure makes possible.

When the actual exhaust gas recirculation rate is measured, eg indirectly via hot film air mass meter 20 and pressure sensor 19 in the intake system 1 determined, and alternatively a Lagehubregelung is used, can be achieved that changes in the exhaust back pressure, leaks caused by contamination diameter changes or tolerances that inevitably occur in the production of the intake manifold, the sensor and the control can be compensated. This gives an exhaust gas recirculation quantity control, which is the intake system 1 a high reproducibility of the exhaust gas recirculation rate allows. Due to the already mentioned possibility of minimizing the volume of the intake pipe 1b , that is the manifold 8th and the intake ports 7 , Can be a very high dynamics when switching from part-load operation with exhaust gas recirculation, the so-called stratified charge operation, and the full-load operation without exhaust gas recirculation, the so-called homogeneous operation realize. Of course, the possibility also plays a role, by electrically driven actuators, such as the exhaust gas recirculation valve 10 , the respective e-gas 15 . 18 , electrically driven valve device 23 and a camshaft actuator (not shown) to achieve a very high dynamic range. In particular, in the case of the camshaft adjuster for adjusting the camshaft, that is to say for controlling the exhaust gas recirculation quantity of the internal exhaust gas recirculation, this can allow very high dynamics, especially when switching from homogeneous operation to stratified charge operation.

In addition, the intake system offers 1 as already mentioned, a minimization of the risk of contamination, since the vent lines 16 . 22 as well as the line element coming from the fuel tank regeneration 21 in kind in the intake system 1 be initiated that the case in the intake pipe 1b introduced gases and vapors, which have a very high oil content, not in the area of the exhaust gas recirculation valve 10 come into contact with the hot exhaust gas and so the pollution by a kind of carbonization in the area of the exhaust gas recirculation valve 10 can be prevented. Therefore, it is possible in the area of the exhaust gas recirculation valve 10 Also achieve a relatively high exhaust gas temperature ideal for combustion, without causing problems in the area of the exhaust gas recirculation valve due to pollution-related reasons 10 leads. Pollution of the intake pipe 1b By "carbonization" is minimized. In the intake air, which only draws in air 1a In contrast, there is a comparatively low temperature of the intake air, so that this intake pipe 1a or at least parts of it can be made of a corresponding material, which does not have too high temperature resistance, but on the other hand, allows advantages in terms of manufacturing and packaging. As the air intake pipe 1a does not come into contact with exhaust gas, there is no "carbon deposit" here.

Due to the corresponding structure of the intake system 1 with the intake pipe 1b and its connection to the exhaust gas recirculation valve 10 which are very close to the throttle device 18 or the e-gas 18 the intake pipe 1b is arranged, it can be achieved that it to a high uniform distribution, so to a very good mixing of air and exhaust gas in the intake manifold 1b comes. In addition, the possibility plays a role that the air flow through the e-gas 18 a corresponding movement can be given, which then, due to the turbulence generated thereby in the gas flow, to a very favorable mixing of the air with the tangential to the intake pipe 1b introduced exhaust gas leads. This can also be done on a very short distance of the intake manifold 1b realize, which in turn very favorable for the minimization of the volume of the intake manifold 1b and for the variability of the packaging.

In addition, results in the intake system 1 , in particular by the valve devices 23 , the possibility of generating a variable charge movement or a twist, as already described above. This makes it possible, the internal combustion engine 2 to operate with so-called wall-mounted combustion process. This makes it possible to achieve a very accurate and very fast adjustment of the degree of delivery to the speed, which makes sense especially for a naturally aspirated engine.

On the other hand, the direct injection engine can be separated by the separation into the air intake pipe 1a and the at least in the partial load range air-exhaust mixture leading intake pipe 1b a corresponding, targeted stratification of air and air-exhaust gas mixture in the cylinder 3 realize, which together with a corresponding injection and the geometric design of the piston surface in the cylinder 3 oscillating piston allows a very favorable combustion with high power delivery at relatively low pollutant content in the exhaust gases.

Both illustrated embodiments is based on the principle of the same principle of operation, with the design of the manifolds 8th . 9 or the intake ducts 6 . 7 and optionally the intake duct 12 With regard to their volumes and their lengths additional charging effects can be achieved, which are comparable to those of a pure resonance or Schaltsaugrohrs.

The description of the above construction with the two suction pipes refers to one flood of the internal combustion engine 2 , so that in multi-flow internal combustion engines 2 either from the headers 8th . 9 to the respective cylinders of the respective flood-leading intake ducts 6 . 7 . 12 may be formed repeatedly or in which, alternatively, for each of the existing floods, where appropriate, in turn, for some of the existing floods together, at least one of the described intake systems 1 can be present.

Claims (15)

Internal combustion engine ( 2 ), in particular direct-injection Otto internal combustion engine, with a plurality of cylinders ( 3 ), with an intake system ( 1 ) and with facilities ( 11 ) for exhaust gas recirculation, which with an exhaust gas recirculation valve ( 10 ) relative to the intake system ( 1 ) are shut off, wherein the intake system ( 1 ) at least two independently formed intake pipes ( 1a . 1b ), via which in each case air can be sucked in and which in each case with the at least one cylinder ( 3 ), one of the intake pipes ( 1b ) a connection with the exhaust gas recirculation valve ( 10 ), while through the other intake pipe ( 1a ) only air can be sucked in, whereby the two intake pipes ( 1a . 1b ) at least one throttle device ( 15 . 18 ) for influencing one of the two intake pipes ( 1a . 1b ) have flow through the volume, and wherein the two intake pipes ( 1a . 1b ) each a collecting pipe ( 8th . 9 ) and for each of the cylinders at least one respective manifold ( 8th . 9 ) with the cylinder connecting intake duct ( 6 . 7 . 12 ) exhibit. Internal combustion engine according to claim 1, characterized in that the volumes of both intake pipes ( 1a . 1b ) are formed independently of each other. Internal combustion engine according to claim 1, characterized in that the air sucking intake pipe ( 1a ) for each cylinder ( 3 ) one compound each ( 12 '' ) via shut-off devices ( 14 ) with the exhaust gas recirculation valve ( 10 ) connected intake pipe ( 1b ) having. Internal combustion engine according to one of claims 1 to 3, characterized in that the air sucking intake pipe ( 1a ) for each cylinder ( 3 ) a valve device ( 23 ) having. Internal combustion engine according to claim 4, characterized in that each of the intake pipe ( 1a ) to the respective cylinder ( 3 ) extending intake duct ( 6 ) the valve device ( 23 ) in the region of the cylinder ( 3 ) having. Internal combustion engine according to claim 5, characterized in that the intake ducts ( 6 . 7 ) of the two intake pipes ( 1a . 1b ) each have a connection via at least one inlet valve ( 4 . 4a . 4b ) with the cylinder ( 3 ) exhibit. Internal combustion engine according to claim 5, characterized in that in the flow direction of the sucked gas streams in each case in the region in front of the cylinder ( 3 ) a collection room ( 5 ) is arranged, wherein the collecting space ( 5 ) with the at least one inlet valve ( 4 ) of the cylinder ( 3 ), wherein the respective intake ducts ( 6 . 7 ) of the two intake pipes ( 1a . 1b ) into the collection room ( 5 ). Internal combustion engine according to one of claims 1 to 7, characterized in that in each of the two intake pipes ( 1a . 1b ) in the flow direction of the respective gas streams after the throttle devices ( 15 . 18 ) at least one pressure sensor ( 17 . 19 ) is arranged. Internal combustion engine according to one of claims 1 to 8, characterized in that the with the exhaust gas recirculation valve ( 10 ) associated intake pipe ( 1b ) has a significantly smaller volume than the air sucking intake pipe ( 1a ). Internal combustion engine according to one of claims 1 to 9, characterized in that the with the exhaust gas recirculation valve ( 10 ) associated intake pipe ( 1b ) An institution ( 20 ) for detecting the volume of the sucked gas, which in the flow direction of the sucked gas before the connection with the exhaust gas recirculation valve ( 10 ) is arranged. Internal combustion engine according to one of claims 1 to 10, characterized in that each of the two intake pipes ( 1a . 1b ) a connection (vent lines 16 . 22 ) with at least one vent opening of a crankcase of the internal combustion engine ( 2 ), wherein the compound ( 16 ) of the vent opening with the air intake pipe ( 1a ) in the flow direction of the in this intake pipe ( 1a ) flowing air in front of the throttle device ( 15 ), and wherein the compound ( 22 ) of the vent with the exhaust gas recirculation valve ( 10 ) connected intake pipe ( 1b ) in the respective intake ducts ( 7 ) is arranged. Internal combustion engine according to claim 11, characterized in that the connection ( 22 ) of the vent opening with the respective intake channels ( 7 ) of the exhaust gas recirculation valve ( 10 ) connected intake pipe ( 1b ) in the flow direction of the sucked gases in an area immediacy bar in front of the cylinder ( 3 ) is arranged. Internal combustion engine according to one of claims 1 to 12, characterized in that the connection of the exhaust gas recirculation valve ( 10 ) with the intake pipe ( 1b ) in a close to the throttle device ( 18 ) of the intake pipe ( 1b ) lying area is arranged. Internal combustion engine according to one of claims 1 to 13, characterized in that the connection of the exhaust gas recirculation valve ( 10 ) with the intake pipe ( 1b ) tangentially to the intake pipe ( 1b ) he follows. Internal combustion engine according to one of claims 1 to 14, characterized in that the throttle devices ( 15 . 18 ) of the two intake pipes ( 1a . 1b ) by means of a common wave ( 24 ) are drivable.