DE19647301A1 - Mixture-preparation system for Otto-cycle engine - Google Patents

Abstract

The combustion chamber (12) in each cylinder (4) is enclosed between the piston (3) and a gable-shaped roof (18). A fuel-air mixture is delivered to it via a throttle-controlled intake containing a valve (17) and seat (23). An injector (13) in the intake wall discharges a jet (14) in the flow direction and the intake contains a bend (16) leading to the chamber roof, the mixture then flowing in a circle (T) inside the chamber. A gas controlled by valves (8) is blown into the bend on the inside via passages (6,7) dependent on operating conditions and acts on the mixture current. The gas current is caused to pulsate, and during starting and early warming up is mainly directed via one passage near the injector.

Description

The invention relates to a method for mixture preparation for an Otto engine according to the generic term of Claim 1 and an internal combustion engine to perform procedure.

It is known that in Otto internal combustion engines with äu Outer mixture formation through fuel injection in the Intake duct the preparation of a homogeneous mixture in the Combustion chamber can be promoted by the mixture flow from the intake duct in a roller-like flow, the so-called tumble flow, flows into the combustion chamber and brings about a fine distribution of the mixture. The Tumble flow is basically generated by that the suction channel through a tumble arch to a gie bel-shaped combustion chamber roof opens into the combustion chamber and Mixture inlet into the combustion chamber by lifting a Ven tilliedes from its valve seat in the combustion chamber roof with egg is released in a corresponding opening stroke. Here the mixture flow from the tumble arc into the Redirected combustion chamber and thereby the tumble flow works. It has proven its worth in the injector Combustion chamber opposite duct wall of the intake duct to be arranged so that the fuel at the entrance of the tum blebogens into the intake air stream in a spray is injected, which in the flow direction  is posed. Thus, atomization is early and Evaporation of the injected fuel in the intake airflow possible, which by employing a Throttle valve is intended as a control element.

In the low load range of the internal combustion engine is ever but the mixture flow delivered into the combustion chamber is only ge ring, which creates a tumble flow for mixture distribution weakly or not at all in the combustion chamber can. Another problem with the mixture preparation he gives itself in the starting phase of the internal combustion engine, whereby due to the upstream injector arrangement injected fuel is evaporated incompletely and partly on the cold channel wall in liquid form precipitates. JP 6-159075 therefore suggests one Otto internal combustion engine before, by blowing one continuous airflow into the intake duct the Ge Mixing in the combustion chamber is affected. The air stone Blow is on two in the flow direction of the Intake channel spaced locations in the tumble arch provided inner wall section. On each of these Places an injection duct opens into the intake duct, wel can optionally be released by a changeover valve, so that upstream of the throttle valve the intake air flow tapped partial flow by the respectively released Injection duct is blown into the intake duct. In the Cold start phase of the internal combustion engine is adjacent of the valve seat into the tumble arch injection channel released, with the blown airflow into the during the operational phase on the cold duct wall fuel on the valve lifted off the valve seat part spray and thus promote fuel evaporation different. Is the internal combustion engine after a certain one Operating time warmed up, so the  continuous air flow after the corresponding order switching of the changeover valve by the near the injector inlet duct opening into the tumble arch. The one through the air flow entering the intake duct urges the mixture flow flowing in the intake duct to the in the tumble arch outer channel wall and so favors with the formation of a tumble flow in the combustion chamber speaking of the valve lift and the geometry of the tumblebo gens.

However, it has been shown that early legs Flow of the mixture flow through air injection in one area close to the injector, especially in the low-load area the internal combustion engine with a low mixture mass flow, minimal impact on the generation of crops aspired tumble flow in the combustion chamber. The one the mixture flow directed by the outer wall of the tumble arc releases quickly from the system on the canal wall, so that a direct influence on the mixture preparation in Combustion chamber through air injection in the area near the injector is hardly possible. The turned on in the manner described blown air flow also leads to harmful formation turbulence in the mixture flow. Furthermore can measure the air injection in the valve seat area not ver during the starting phase of the internal combustion engine prevent that on the cold channel wall opposite the Injector by wetting the fuel with the spray beam of fuel film. That power stoffilm leads to the formation of too large fuel which do not drip before entering the combustion chamber can be evaporated more and in liquid form Create a homogeneous mixture in the combustion chamber. The result is over-greasing of the mixture formed in the combustion chamber and incomplete combustion, which increased  Pollutant emissions, especially unburned coal water causes hydrogen and carbon monoxide. By the blow like relocation of the blowing point due to the formwork device of the changeover valve during the warm-up phase of the Internal combustion engine is a satisfactory mixture Horse riding in the combustion chamber is not possible because of the changeover only produce an unsatisfactory tumble flow bar and increased damage immediately after switching emissions due to excessive fuel drop formation occur.

It is therefore an object of the invention to provide a method for Ge to create mixing, which is particularly in the low riglast range and in the starting phase of the internal combustion engine seems to have an effective influence on the mixture production device in the combustion chamber. It is still a task of the invention to provide an Otto engine len, which operate with the inventive method is cash.

This object is achieved in a method with the features of claim 1 and one Otto internal combustion engine with the features of claim 4 ge solves.

In the start-up phase or in the early warm-up phase of the Internal combustion engine is mainly by atomization exercise channel and its near the injector in the blow-in cut arranged injection opening in the intake duct a fluid stream is blown in and thereby in it Operating phase on the cold duct wall due to fuel wetting down torn fuel film and atomized in the mixture flow. The early removal of the Fuel film from the duct wall made possible by the Ab  there was complete evaporation from the valve seat atomized fuel drops before entering the Combustion chamber. With increasing operating time and therefore increasing The temperature of the internal combustion engine increases mender fluid mass flow through a tumble channel adj Beard of the valve seat blown into the intake duct. In the Normal operating phase of the internal combustion engine is as before blown through the tumble channel, the one wall section opposite the injector Fuel is evaporated by the temperature of the wall and therefore no additional atomization measures this point are required.

The air is blown into the valve seat area to create an egg ne has a direct influence on the combustion chamber the mixture flow to generate the desired tumor blowing flow in the combustion chamber. The fluid flow is before the Introduction into the injection channels pulsed, whereby a high with a low fluid mass flow Effectiveness of the injection due to the impulse-like legs flow is reached. One in the starting phase of the burning engine through the atomization channel and its on Blow opening in the area near the injector into the intake duct injected fluid stream tears down on the wall hit fuel film according to its pulse rate frequently and thus achieves fine atomization and rapid evaporation. Influencing the mixture flow mes to generate a tumble flow in the combustion chamber Injection of a fluid flow through the tumble channel and whose injection opening in the valve seat area is through the Pulsation of the fluid flow is particularly advantageous since great tumbling effect on the mixture flow only a small amount of air is added to the mixture flow becomes.  

The pulsation of the be to be blown into the intake duct tuned fluid flow is through a quick switch Tactile valve assembly which produces both the Tumbleka nal as well as the atomization channel and that ever Weil present operating point of the internal combustion engine controls accordingly. The upstream is advantageous Throttle valve in the intake duct to the intake air flow Partial stream tapped through a bypass channel is fed to the injection channels. The pressure drop upstream and downstream of the throttle valve drives the Air flow through the bypass duct and according to the on position of the timing valve arrangement through the injection channels for blowing into the tumble arch.

In an advantageous development of the invention, in a bypass duct arranged a changeover valve, which both the bypass channel and one at this point in dominated feed line leading to the bypass channel. By a corresponding circuit of the changeover valve is available as an alternative to the air flow through the feed line listed fluid ready for injection. Is the food line with an exhaust duct of the internal combustion engine bound, so is the exhaust gas into the Ansaugka nal the internal combustion engine traceable. By correspond Adequate switching of the changeover valve is in every loading driving point of the internal combustion engine the optimal exhaust gas feedback rate adjustable. In addition, is by a split injection of the entire exhaust gas flow to ver correspond to different places in the tumble arch de Setting the clock valve arrangement a mixture bil tion with high exhaust gas compatibility can be achieved.  

It is seen as advantageous that both the switching valve as well as the timing valve arrangement by a Kenn field control can be set optimally for the operating point. There at the control of the injection takes place such that in an optimal every operating point of the internal combustion engine Mixture preparation in the combustion chamber and, by controlling the Composition of the fluid flow to be blown, one each because optimal exhaust gas recirculation rate has been reached.

Each cylinder of the internal combustion engine advantageously has two intake ducts opening side by side in the combustion chamber on. Through different control of the blowing processes there are differences in the tumble arches of the two intake channels pronounced tumble currents in the combustion chambers can be formed, with a swirl flow around the cylinder axis arises. With the generation of a swirl flow stands another means which can be influenced by the blowing for mixture preparation and improvement of the firing conditions ready.

Further features of the invention result from the Un claims and from the description of an execution example, which below with reference to the drawing is explained. Show it:

Fig. 1 shows a schematic illustration of a partially broken longitudinal section of a cylinder of a spark-ignition internal combustion engine with external mixture formation by injecting fuel into the intake passage,

Fig. 2 is a plan view of a cylinder,

Fig. 3, the magnification of the Einblasabschnittes adjacent the valve seat according to III in Fig. 1,

Fig. 4 shows an alternative embodiment of the detail accelerator as Fig. 3,

Fig. 5 is a perspective view of the mouth of the Tum blebogens into the combustion chamber according to V in Fig. 4.

In Fig. 1, a cylinder 4 of an Otto engine 1 is shown in a longitudinal section, in which a combustion chamber 2 is delimited by a piston 3 and a gable-shaped combustion chamber roof 18 . In the combustion chamber 2 open in a gable half of the combustion chamber roof 18 two consecutively arranged, mixture-supplying intake ducts 12 and in the other gable half of the combustion chamber roof 18 two exhaust gas channels 21 , which after combustion of the mixture in the combustion chamber 2 by an exhaust valve 20 for guiding the Exhaust gases can be released. Each intake duct 12 is bent in its end section with a tumble arch 16 to the combustion chamber roof 18 and can be released by lifting a Ven valve member 17 from its valve seat 23 in the combustion chamber roof 18 . Corresponding to the operating point of the internal combustion engine 1 controls a throttle valve 11 upon a release of the suction passage 12 to the intake air mass flow A. In the channel wall 15 of the intake passage 12 is opposite the combustion chamber 2 is disposed an injector 13, wel cher at the input of Tumblebogens 16 fuel in injects a spray 14 . The spray jet 14 is employed in the direction of flow of the intake air stream A.

In order to achieve an optimal mixture preparation in the combustion chamber with as homogeneous a distribution as possible, the aim is to introduce the mixture flow in a drum-shaped tumble flow T into the combustion chamber 2 . The tumble flow T is basically generated with a corresponding valve lift of the valve member 17 by the geometry of the tumble arc 16 and the flow energy of the mixture flow. In the low-load range of the internal combustion engine 1 with low speeds and low mixture mass flow, the generation of the tumble flow T is supported by blowing in a fluid flow in the region of the valve seat 23 in order to improve the mixing in the combustion chamber 2 . In the inner blowing section 25 , therefore, a tumble channel opens through blowing openings 24 into the suction channel 12 . The injection openings 24 are arranged in a circular arc in the internal injection section 25 parallel to a valve seat ring 22 which has the valve seat 23 . By blowing in a corresponding fluid mass flow through the tumble channel 6 , the desired tumble flow T for mixture preparation in the combustion chamber 2 can be generated at each operating point, particularly in the low load range of the internal combustion engine 1 . If the mixture flow supplied to the combustion chamber in each of the two intake ducts 12 is influenced differently in its flow direction by different injection control of the respective tumble ducts 6 , in addition to the generation of tumble flows T, influencing the mixture preparation by forming a swirl flow around the cylinder axis is possible.

In the inner blowing section 25 of the tumble arc 16 , near the injector 13 , another blowing channel opens, namely an atomizing channel 7 through blowing openings 26 into the suction channel 12 . The injection openings 26 are distributed annularly in a partial area of the channel wall of the injection section 25 . Both injection channels 6 , 7 are controlled by a fast-switching timing valve arrangement 8 , which feeds the injection channels with pulsating fluid flows, the proportions of which are dependent on the total available fluid flow of the operating point or the operating phase of the internal combustion engine 1 . During the start phase or the early warm-up phase of the internal combustion engine 1, the available for blowing fluid stream is mainly blown by the atomizing 7 in the intake duct 12th The emerging at this point through the blow holes 26 , pulsating fluid stream tears the fuel film in this operating phase on the cold channel wall due to fuel wetting down. The deposited fuel is torn into the interior of the intake duct 12 and atomized, which promotes complete evaporation and thus promotes the homogeneous mixture formation in the combustion chamber.

With increasing operating time of the internal combustion engine, the clock valve arrangement 8 directs the blowing mass flow in increasing proportions through the tumble channel 6 . With a corresponding pulsation and quantity of the injected fluid flow, the development of the tumble flow T in the combustion chamber 2 can be optimally controlled at the operating point. In the higher load range of the internal combustion engine 1 with increasingly higher speeds, the injected fluid flow is increasingly reduced and the required tumble flow T through the mass flow of the mixture supply in the Ansaugka channel 12 and the tumble elbow 16 and the valve member 17 it produces. At high speeds of the internal combustion engine 1 , the injection through the tumble channel 6 is stopped in order not to increase the formation of the tumble flow T in the combustion chamber 2 to a harmful level, which would prevent the supply of the required amount of intake air A through the intake channel 12 . The curvature of the tumble arc 16 is carried out in such a way that a low basic tumble pulse is given to the mixture stream which is to be fed to the combustion chamber 2 due to the geometry of this low arc bleb. The required tumble flow T for good Ge mixture preparation is thus variable in the low load range of the internal combustion engine generated by the air injection in the tumble channel 6 adjacent to the valve seat 23 .

Another possibility for improving the mixture preparation in the combustion chamber 2 and the combustion conditions, in particular with regard to fuel consumption and pollutant emissions, is possible by controlling the composition of the fluid flow to be blown in. In this case, the blowing channels 6 , 7, on the one hand, an air flow can be fed for blowing, which upstream of the throttle valve 11, the intake air flow in the intake channel 12 is accessed and fed through a bypass channel 10 of the valve arrangement 8 to the valve line 8 .

The inlet air flow is pulsed by the clock valve arrangement 8 and rich in accordance with the respective vorlie operating conditions of the internal combustion engine 1 at part of the tumble channel 6 for injection in the valve seat and the atomization channel 7 for injection in the area close to the injector of the injection section 25 . The air flow tapped in front of the throttle valve 11 is driven upstream and downstream of the throttle valve 11 by the bypass duct 10 and the injection ducts 6 , 7 for blowing into the tumble elbow 16 by the pressure drop in the intake duct. As a result, at the start of the internal combustion engine 1 with the throttle valve 11 still closed, an injection pressure is immediately present in the dusting channel 7 . The Einla solution of the air flow already tapped in front of the throttle valve 11 through the atomization channel 7 and its blowing openings 26 directly atomize the fuel film formed at this point in the channel wall and thus prevent any liquid liquid from entering the combustion chamber 2 reliably. In the first Arbeitspie len of the cylinder 4 in the starting phase of the internal combustion engine 1 is ensured by the immediate atomization of the fuel film in the blowing section 25 for a complete, homogeneous mixture combustion and minimal pollutant emissions.

Between the timing valve arrangement 8 and the intake duct 12 , a changeover valve 9 is arranged in the bypass duct 10 , which controls both the bypass duct 10 and a feed line 19 which opens at this point. The Spei line 19 is connected in the embodiment with a common exhaust pipe of the exhaust channels 21 of all cylinders 4 of the internal combustion engine 1 . Gives the Umschaltven valve 9 the feed line 19 , exhaust gas from the internal combustion engine 1 is returned and comes in accordance with the setting of the timing valve arrangement 8 through the injection channels 6 , 7 for injection into the intake duct 12 . For each operating point of the internal combustion engine, an optimal exhaust gas recirculation rate can be controlled by a corresponding setting and switching sequence of the changeover valve 9 . The exhaust gas stream to be recirculated is from the Druckge cases from the exhaust tract to the intake tract of the internal combustion engine 1 through the feed line 19 , the bypass duct 10 and the injection ducts 6 , 7 for blowing into the tumble arc 16 . Advantageously, however, a mixture flow of air and fuel vapor can also be passed into the bypass duct 10 through the feed line 19 , whereby the mixture preparation in the combustion chamber 2 is improved, in particular in the starting phase of the internal combustion engine 1 .

The setting of both the clock valve arrangement 8 and the setting of the changeover valve 9 is carried out in dependence on the respective operating point of the internal combustion engine 1 by means of a map control 5 . The mixture preparation in the combustion chamber 2 can be optimized by the map control 5 under all operating conditions, that is to say at every operating point and in every operating phase of the internal combustion engine 1 , by appropriately controlling the blowing processes. Due to the always optimal influencing of the flow direction of the mixture flow in the intake duct 12 , a high exhaust gas compatibility during mixture formation is also achievable at every operating point and the maximum possible exhaust gas quantity can thus be traced. The map control 5 operates in dependence on the speed and the load state of the internal combustion engine 1 . The available due to a Druckgefäl les to the blowing section 25 A blow amount is distributed by the map control 5 by corre sponding control of the clock valve assembly 8 and the switching valve 9 in a dependent on the operating time of the internal combustion engine 1 gradation on the Einblaska channels 6 , 7 . At the start of the internal combustion engine 1 , the entire fluid flow available for injection is blown through the atomization channel 7 in the region of the injection section 25 near the injector for atomization of the fuel film applied to the channel wall. With increasing operating time, the available fluid flow is blown in ever increasing proportions through the tumble channel 6 to influence the generation of the tumble flow T in the combustion chamber 2 into the tumble arc 16 near the valve seat 23 , as already described in the higher load range of the internal combustion engine 1 at high speeds the injection mass flow for tumble generation is reduced or blocked.

In Fig. 2 is a plan view of a cylinder 4 of an internal combustion engine, in the combustion chamber 2 two intake channels 12 , 12 'open, which open in a symmetrical arrangement side by side in one half of the giebelförmi gene roof of the combustion chamber. Each intake duct 12 , 12 'supplies the combustion chamber with a mixture whose inflow direction for generating the tumble flow can be influenced by targeted blowing of a fluid flow. The fluid flow intended for a blow is brought up by a tumble channel 6 in the channel wall 15 adjacent to the suction channels 12 , 12 'and a driving pressure gradient. The injection takes place at each Ansaugka channel through inlet openings 24 which are arranged in the arcuate end section of each suction channel adjacent to the respective valve seat in the inner blowing section of the (see FIG. 1) tumble arc evenly beabstan det from the valve seat. The injection openings 24 are fluidically connected to the tumble channel 6, each with an injection bore 29 passing through the channel wall 15 . Via a feed bore 28 in an outer wall 30 delimiting the tumble channel 6 , the tumble channel 6 is supplied with a fluid flow intended for blowing in depending on the speed of a clock valve arrangement. By appropriate choice of the fluid flow through the tumble channel 6 and a corresponding setting of the clock valve arrangement of an intake duct 12 , the mixture flows of both intake ducts 12 , 12 'can be let into the combustion chamber 2 with different flow patterns, whereby a swirl flow in the circumferential direction of the combustion chamber 2 can be generated to improve the mixture preparation. It is also possible to generate a swirl flow through different blowing processes in both intake ducts 12 , 12 ', provided that both intake ducts 12 , 12 ' are each assigned a timing valve arrangement and a piping system serving the Einla solution.

In Fig. 3 is shown in a section according to III in Fig. 1, the inside of the tumble arch inlet section 25 neigh bears the valve seat 23 . The valve seat 23 , against which a valve member for closing the intake duct can be brought into contact, is formed in a valve seat ring 22 , which can be inserted into the combustion chamber roof. In the channel wall 15 , a fluid-carrying tumble channel 6 is formed, which is fluidly connected to the suction channel via blow-in bores 29 and associated blow-in openings 24 adjacent to the valve seat ring 22 . A pulsating fluid flow blown through the injection bores 24 into the intake duct supports the detachment of the mixture flow from the duct wall 15 which is curved inwards in the injection section 25 and thus generates a roller-like tumble flow when it enters the combustion chamber. The Einblasbohrungen 29 and thus the insufflation ports 24 in the exemplary embodiment have a favorable diameter d of 2 mm, wherein the injection openings 24 are arranged with a distance to each other of about 4 mm. The outer wall 30 delimiting the tumble channel 6 is penetrated by bores which lie opposite the blow-in bores 29 in the tumble channel 6 in the respective overlap. These bores are used in the manufacture of the blowing bores 29 to introduce a tool which penetrates the outer wall 30 from the outside. For fluidic sealing of the tumble channel 6 , each bore in the outer wall 30 is closed by a plug 27 , which is preferably made of aluminum.

The injection openings 24 can also be formed in the valve seat ring 22 , whereby the influencing of the mixture flow in the intake duct to generate a tumble flow in the combustion chamber can be carried out particularly close to the valve seat 23 .

In FIG. 4, an alternative embodiment of an inner in Tumblebogen Einblasabschnittes 25 is shown. Here, the Tumblekanal is brought 6 in the channel wall 15 near to the valve seat ring 22 and is supplied with a blowout to a particular fluid flow will be described through a bore 28 as to FIG. 1,. The bore 28 is provided with a thread into which a line part for connection to the clock valve arrangement ( FIG. 1) can be screwed. The injection holes 24 are rectangular and ge in the circumferential direction of the tumble sheet stretches, so that a large-scale entry of the fluid flow to be blown into the tumble sheet is possible. The fluid flow is parallel to the valve seat ring 22 ge directed to the opposite outer wall of the Tumblebo gene and directly affects the generation of a tumble flow in the combustion chamber when the mixture flow occurs.

In Fig. 5 in the view according to arrow V in Fig. 4, the arrangement of the rectangular injection openings 24 parallel to the valve seat ring 22 in the inner circular arc section of the channel wall 15 of the tumble arc is shown. The effect of the pulsating fluid flow during the injection is enhanced by the rectangular configuration of the inlet openings 24 , since a large-area entry near the valve seat ring 22 for optimal influencing of the mixture flow guided in the intake duct is possible with each injection pulse. The injection openings 24 are therefore, if possible, stretched in the circumferential direction of the intake duct with a large length l and a small width b and are arranged at a small distance h from the valve seat ring 22 . In the advantageous embodiment of the injection openings 24 shown , the length l is approximately 3 mm with a respective width b of 1 mm. The injection openings 24 are arranged at a distance a of 0.8 mm from one another and are each arranged at a distance h from the valve seat ring 22 , which is 1.5 mm.

The arrangement in the circumferential direction of the intake duct can also be advantageous for the injection openings of the atomization duct in the region of the injection section near the injector ( FIG. 1). The injection openings of the atomization channel are distributed over the entire circumference of the intake duct, so that a section of the intake duct knocked down and atomized on the duct wall is torn open and atomized during injection in each circumference of the intake duct. In addition, in the annular arrangement of the injection openings of the atomization channel, a very high volume flow can be blown in, so that in certain operating points of the internal combustion engine with a corresponding setting of the changeover valve ( FIG. 1), large quantities of exhaust gas are traceable.

Claims (15)

1. Method for mixture preparation for an Otto internal combustion engine ( 1 ), in the cylinders ( 4 ) of a piston ( 3 ) and a gable-shaped combustion chamber roof ( 18 ) a combustion chamber ( 2 ) is delimited by at least one intake channel ( 12 ) a fuel / air mixture is supplied by a Ven valve member ( 17 ) of an intake valve from its Ven valve seat ( 23 ) in the combustion chamber roof ( 18 ) and depending on the employment of a throttle valve ( 11 ) an intake air flow (A) flows through the intake duct ( 12 ) into which an injector ( 13 ) arranged in a duct wall ( 15 ) facing away from the combustion chamber ( 2 ) injects fuel in a spray jet ( 14 ) set in the direction of flow and the mixture flow through a tumble arch ( 16 ) to the combustion chamber roof ( 18 ) and then subsequently in a roller-like tumble flow (T) flows into the combustion chamber ( 2 ), with one another in an inward blowing section ( 25 ) in the tumble arc ( 16 ) it is spaced apart by at least one blowing opening ( 24 , 26 ) of blowing channels ( 6 , 7 ), a fluid stream acting on the mixture flow in the tumble arc ( 16 ) is blown, which of a valve arrangement ( 8 ) depending on the operating phase of the Internal combustion engine ( 1 ) is fed to the injection channels ( 6 , 7 ), characterized in that the fluid flow is set in pulsation and in the start phase or in the early warm-up phase of the internal combustion engine ( 1 ) predominantly through an atomization channel ( 7 ) near the injector ( 13 ) and with increasing operating time during the warm-up phase steadily increasing in the normal operating phase of the internal combustion engine ( 1 ) through a tum blekanal ( 6 ) adjacent to the valve seat ( 23 ) in the intake duct ( 12 ) is blown. 2. The method according to claim 1, characterized in that an upstream of the throttle valve ( 11 ) in the intake channel ( 12 ) tapped air flow into the Tumblebo gene ( 16 ) is blown. 3. The method according to claim 1, characterized in that a from an exhaust duct ( 21 ) of the internal combustion engine ( 1 ) recirculated exhaust gas stream in the tumble arc ( 16 ) is blown. 4. Otto internal combustion engine for carrying out the process, in the cylinders ( 4 ) of a piston ( 3 ) and a gable-shaped combustion chamber roof ( 18 ) a combustion chamber ( 2 ) is limited, in which at least one controlled by an intake valve and by lifting a valve member ( 17 ) from its valve seat ( 23 ) in the combustion chamber roof ( 18 ) releasable intake channel ( 12 ) which, depending on the position of a throttle valve ( 11 ) through which an intake air flow (A) can flow and in which one in an injector ( 13 ) arranged in the channel ( 15 ) facing away from the combustion chamber ( 2 ), fuel can be injected in a spray jet ( 14 ) set in the direction of flow and the mixture flow through a tumble arc ( 16 ) to the combustion chamber roof ( 18 ) to form a roller-like tumble flow (T) in the combustion chamber ( 2 ) can be inlet, wherein in the tumble arch ( 16 ) in an internal Einblasab section ( 25 ) spaced apart blowing channels ( 6 , 7 ) each open through at least one injection opening ( 24 , 26 ) through which a fluid flow can be conducted by a valve arrangement ( 8 ) depending on the operating phase of the internal combustion engine ( 1 ) and with effect on the mixture flow in the tumble arc ( 16 ) is inflatable, characterized in that the valve arrangement ( 8 ) is a fast-switching cycle valve arrangement ( 8 ). 5. Internal combustion engine according to claim 4, characterized in that a bypass duct ( 10 ) branches upstream of the throttle valve ( 11 ) from the intake duct ( 12 ) and from the timing valve arrangement ( 8 ) fluidically connected to the injection ducts ( 6 , 7 ). 6. Internal combustion engine according to claim 5, characterized in that in the bypass channel ( 10 ) a switching valve ( 9 ) is arranged, which controls the merging of the by-pass channel ( 10 ) and a fluid-carrying feed line, depending on the position of the switching valve ( 9 ) the feed line ( 19 ) can be released. 7. Internal combustion engine according to claim 3 and 6, characterized in that the feed line ( 19 ) is fluidly connected to a gas channel ( 21 ) from the internal combustion engine ( 1 ). 8. Internal combustion engine according to one of claims 4 to 7, characterized in that both the changeover valve ( 9 ) and the clock valve arrangement ( 8 ) by a map control ( 5 ) can be adjusted to the optimum operating point. 9. Internal combustion engine according to one of claims 4 to 8, characterized in that the atomization channel ( 7 ) with a plurality of injection openings ( 26 ) in the channel wall ( 15 ) opens into the intake channel ( 12 ). 10. Internal combustion engine according to claim 9, characterized in that the injection openings ( 26 ) of the atomization channel ( 7 ) are arranged on a surface in the injection section ( 25 ), which is preferably circular or annular. 11. Internal combustion engine according to one of claims 5 to 10, characterized in that the tumble channel ( 6 ) with a plurality of Einblasöffnun gene ( 24 ) opens into the intake duct ( 12 ) which sits in a radial arc section parallel to the valve ( 23 ) in the blowing section ( 25 ) of the tumble arch ( 16 ) are arranged. 12. Internal combustion engine according to claim 11, characterized in that the injection openings ( 24 ) of the tumble channel ( 6 ) in a valve seat ( 23 ) having, in the combustion chamber roof ( 18 ) insertable valve seat ring ( 22 ) are formed. 13. Internal combustion engine according to claim 11 or 12, characterized in that the injection openings ( 24 ) of the tumble channel are designed with a round cross-section. 14. Internal combustion engine according to claim 11 or 12, characterized in that the injection openings ( 24 ) of the tumble channel ( 6 ) with rectangular, in the circumferential direction of the Ansaugka channel ( 12 ) are elongated cross-section. 15. Internal combustion engine according to one of the preceding claims, characterized in that each cylinder ( 4 ) of the internal combustion engine ( 1 ) has two side by side in the same gable half of the combustion chamber roof ( 18 ) in the combustion chamber ( 2 ) opening suction channels ( 12 , 12 ').