DE10106887A1 - Direct-injection internal combustion engine with spark ignition and method for operating such an internal combustion engine - Google Patents

Abstract

The invention relates to a combustion chamber of a direct-injection gasoline engine with a spark plug 2 arranged in the cylinder center axis 1, an injector 3 arranged laterally in the combustion chamber, a piston 7, inlet channels, inlet valves 4, 4a, outlet valves 5, 5a and one offset to the cylinder center axis 1 arranged piston bowl 9 having piston crown 8, the mixture cloud being better absorbed in stratified charge operation due to the lateral displacement of the piston bowl 9 in accordance with the laterally offset injection jet 10. The essential part of the fuel is injected into the piston recess 9 and sufficient swirling of the fuel is achieved by a swirling movement.

Description

The invention relates to a direct injection spark-ignited Internal combustion engine with one in the range Cylinder center axis in the cylinder head arranged spark plug, an injector arranged laterally in the cylinder head, one Piston and one offset to the cylinder central axis in Piston plate arranged piston bowl and a method for internal mixture formation in a direct injection spark ignition internal combustion engine.

A direct injection engine usually has at least one two inlet and two outlet valves, one mostly in the middle arranged on the combustion chamber roof, one Fuel injector placed between the intake valves and is arranged inclined to the horizontal, and a piston equipped with a piston bowl, the so formed combustion chamber limited at the bottom.

The engine uses the stratified combustion process (the Fuel is in the compression phase in the combustion chamber introduced) for mixture formation or mixture management Piston bowl. This wets the piston crown Fuel instead. The evaporation time that the charge cloud in the Combustion chamber or available in the piston bowl is very short, so that a swirl flow is generated in the combustion chamber, which the evaporation process and the transport of the mixture cloud to the ignition location. In the stratified combustion process  care must be taken that the entire injected fuel as a stratified charge cloud on the Combustion participates and from the piston crown at the time of Ignition has largely evaporated.

Such a combustion chamber is already known from DE 197 35 863 A1 known. The combustion chamber shown here is also from limited a piston which has a piston recess. The The center of the piston recess is the axis of the cylinder staggered so that the more or less strong Swirl flowing into the cylinder or the combustion chamber Fresh air collected in the piston bowl, in the central area in the cylinder arranged spark plug and finally compressed is ignited. It is not described or provided that Piston bowl according to the fuel jet formation, d. H. corresponding to the resulting movement from the injection direction and swirl movement to train and arrange. The Swirl flow can only through the trough position explained here insufficient to get into the piston bowl, because the deflection of the Fuel jet due to the swirl flow causes some of the fuel is not in the area of the piston bowl arrives. There is no adequate evaporation of the Charge cloud and the fuel on the piston instead of.

The invention has for its object a combustion chamber provide with which an improved combustion of the supplied fuel-air mixture is achieved.

Another object of the invention is a method provide with which an improved combustion of the supplied fuel-air mixture is achieved.  

The object is achieved according to the invention by a device the features of claim 1 and a method with the Features of claims 21 or 22 solved. Further Refinements and advantages or improvements result from the subclaims.

The combustion chamber of a direct-injection spark-ignited Internal combustion engine has one in the range of Cylinder center axis spark plug arranged in the cylinder head, an injector arranged laterally in the cylinder head, one Piston, an exhaust valve, one offset to the cylinder center axis arranged in the piston crown and at least two Inlet channels, a in a first inlet channel swirl generating device is arranged. At a open position of the swirl generating device have the Channels a tumble flow with an integral Tumble count on which is at least 25% larger than an integral one Tumble number of a conventional filling channel is.

Due to the strong tumble flow, especially at high Speeds in full load operation cause a rapid blowout achieved at the same time low residual oxygen content in the exhaust gas. A low exhaust gas temperature is achieved, which is a better temperature protection for exhaust gas aftertreatment provides arranged exhaust gas cleaning system.

The fuel injection takes place in the direction of the Cylinder central axis such that the so-called "Geometric injector injection direction" and Direction of charge movement resulting fuel jet direction in the direction of the laterally offset piston recess. With the the so-called "geometric injector injection direction" is the Direction with which the fuel is missing Charge movement into the combustion chamber in the direction of the injector axis is injected. Due to the lateral offset of the piston bowl  becomes corresponding to that due to the swirling movement to the side offset injection jet better absorbed the mixture cloud, causing most of the fuel to enter the trough is injected. Adequate, through which Swirl movement and the tumble flow supported Evaporation of the fuel reached.

It is also advantageous that the piston recess on the from "Geometric injection direction" of the injector and the Swirl movement of the fuel-air mixture resulting Fuel jet direction is aligned.

The piston bowl consists of a first larger part, the essentially a first circular boundary wall has, and a second smaller part together, one second boundary wall of the second smaller part partially one formed towards the outside towards a cylinder wall Has bulge.

The bulge formed in the piston recess is intended to do this serve that the flow towards the first part of the Piston recess is guided. There the fuel cloud is going through a deflection wall led to the spark plug, the im essentially circular boundary wall of the piston bowl in first part of the piston bowl to achieve a precise Redirection and guidance of the mixture cloud is provided.

It is for engines with a cylinder bore of about 82 mm advantageous that the boundary wall of the first part of the Piston bowl a radius between 15 mm and 25 mm for Has the center of the first part of the piston bowl and the Boundary wall of the second part of the piston bowl including the bulge a radius between 8 mm and  15 mm to the center of the second part of the piston bowl having.

Furthermore, it is advantageous that in the area of the first Part of the piston bowl a radius between the piston bowl bottom and a piston bowl deflection wall between 5 mm and 12 mm. To the piston recess is designed such that the deflecting wall Height difference between trough bottom and trough edge from has at least 10 mm.

According to a further preferred embodiment of the solution according to the invention is an undercut in the Piston recess provided. The undercut becomes a Prevents the fuel cloud from escaping. Here it is important that the deflecting wall in the area of the spark plug is formed that the mixture cloud over the Piston contour is deflected towards the spark plug.

For this purpose, it is advantageous that the piston crown bottom in the area of the undercut of the piston bowl a bowl bottom radius has between 6 mm and 12 mm, and the undercut with the Piston crown surface an angle γ between 10 ° and 20 °, especially between 13 ° and 17 °.

It is also advantageous that the undercut of the Piston recess with respect to a fuel jet center in one of the Spark plug located opposite part of the piston recess is. Thus, the mixture cloud through the undercut again returned to the side of the spark plug. In the field of Spark plug or on the side of the spark plug is preferred no undercut provided for the mixture cloud can circulate freely.  

According to a further preferred embodiment of the Solution according to the invention provides that Inlet valve in the area of the piston bowl smaller than the other Inlet valve is formed. So there is space for Spark plug is available, and the spark plug can be made accordingly the center of the piston bowl can be arranged offset without it Collisions with the directly adjacent intake valve comes.

In the event that the fuel jet does not have the Piston recess may be sprayed away, according to one another preferred embodiment as high as possible Piston bowl wall provided. But this is through the Valve clearance limited, so that by reducing the Control time of the corresponding valve is sufficient Piston bowl wall height is reached. It is therefore special Importance for the present invention that an exhaust valve closes earlier than the other exhaust valve or timing is defined accordingly. In connection with the Training and arrangement according to the invention, it is advantageous that the piston crown has an exhaust valve pocket, so that adequate valve clearance with optimal Piston bowl wall height is guaranteed.

According to a further embodiment, the piston bowl is on aligned with a resulting fuel jet direction, which is a projection of the center of the fuel jet towards has the cylinder center axis. That is the case when it is out a geometric injector injection direction and Direction of charge movement resulting fuel jet direction shows in the direction of the cylinder central axis.

It is also according to another embodiment advantageous that two different inlet channels are provided are, with an inlet channel a strong charge movement and the  other inlet channel a slight charge movement in the cylinder generated. For the various operating points, such as stratified partial load, homogeneous partial load and full load different demands placed on the movement of cargo. In the stratified partial load, the swirl movement promotes the Evaporation of the fuel cloud and supports its transportation to the ignition site.

One is necessary for the formation of a stable stratified charge cloud Twist motion necessary with the tumble components depending on Operating point is superimposed. In the stratified partial load So is the inlet channel, which has a high tumble flow generated completely or partially via a flap locked or switched off. In the homogeneous part load or Depending on the map point, the charge air flows over a full load or both inlet channels in the combustion chamber. In the homogeneous Partial load and full load is especially for engines with one Cylinder bore of about 82 mm and a stroke of about 85 mm a speed of about 2700 revolutions per minute pronounced tumble flow in the combustion chamber necessary.

For remaining fuel droplets on the injector entrainment is a first on the cylinder head in the injector area Swirl inlet provided with a small squeeze area. In order to drops of fuel adhering to the injector after Injection removed by the cylinder flow. Thereby becomes the one with increasing operating time Coking minimized.

According to the first swirl inlet in the cylinder head is one Deepening towards one in the combustion chamber current charge swirl is lowered to the injector, with a small squeeze area formed near the injector is to direct the flow into the piston bowl.  

In addition, according to a further embodiment, the Assigned a second swirl inlet in the piston crown, the second swirl inlet in the piston crown as one Recess is formed outside the piston bowl in such a way that a flow directed by this depression towards the second part of the piston bowl is directed. With that the Swirl flow optimally continued into the piston bowl, whereby the mixture preparation is improved.

According to the invention, the inlet valves are spaced apart arranged near the edge of the combustion chamber, so that a smallest The distance between the two inlet valve circumferences is at least 9 mm especially for engines with a cylinder bore of about 82 mm and a stroke of about 85 mm. This is supposed to a low wetting of the intake valves with fuel Suction stroke injection take place. This arrangement is about in addition, good cooling of the injector via appropriate Allow cooling water channels, thereby coking the injector is avoided.

According to the invention, the direction of injection of the injector is to a cylinder head parting surface an inclination of 35 ° to 50 ° have a beam cone angle at a distance of 10 mm to the fuel outlet opening of at least 60 ° Environmental conditions.

According to a preferred embodiment of the invention Solution is finally provided that the piston crown bottom has an inclination to the cylinder head parting surface. this leads to for better, targeted guidance of the mixture in the direction the spark plug.  

According to the invention, the charge movement - seen from above - a twist with a counterclockwise direction, and the Fuel jet, viewed from the injector, one Swirl motion with a counterclockwise direction, the charge movement - seen from above - with a twist may have a clockwise direction if the Fuel jet, viewed from the injector, one Twist movement in a clockwise direction having.

The invention provides a method for mixture formation, in a charge movement with a swirl in an inlet channel is produced. The swirl of the supplied air volume points - from Viewed above - a counter-clockwise rotation on. A quantity of fuel is added to the quantity of air supplied a swirl movement injected, the swirl - from the injector viewed from -, d. H. in the spray direction, also one Counterclockwise.

By generating the swirl flow in interaction with the Tumble basic flow in the combustion chamber is in stratified charge mode the evaporation of the injected fuel despite the short Evaporation time that the charge cloud in the combustion chamber Is available, accelerated and the transportation of Mixture cloud supported to the ignition location.

It is also conceivable that a swirl in an inlet duct is formed so that the charge movement with a swirl in a clockwise direction when viewed from above if the amount of fuel is injected such that the fuel jet downstream, d. H. from the injector considered a swirl movement with a direction in the Clockwise.  

In stratified charge mode is a targeted overlay a tumble flow and a swirling movement make sense Management of the fuel brought into the combustion chamber reached. There is an interaction between the one Swirl injected fuel and the swirl assisted and with a tumbling cylinder flow instead. The The resulting mixture cloud is caused by the cloud in the piston crown arranged swirl inlet to the piston bowl and thereby by the swirl flow rotating around the cylinder axis is promoted.

The accelerated evaporation achieved is advantageous of fuel. Through the arranged on the cylinder head Swirl inlet ensures that there are no fuel residues stick to the outlet opening of the injector in the form of droplets remain, which can lead to coking of the injector.

The two inlet channels are depending on the engine load generates different cargo movements, which adds up to the sum of the velocity vectors from the swirl flow of the Injection jet and the internal flow of the cylinder Operating point is adjusted so that a targeted Transport of the charge cloud to the center of the ignition takes place.

Further advantages and details of the invention are in the Claims and explained in the description and in the Figures shown. Show it:

Fig. 1 is a sectional view of a cylinder head of a direct injection gasoline engine according to the invention,

Fig. 2 is a schematic plan view of a piston according to the invention with an offset piston recess

Fig. 3 is a schematic representation of a cylinder head side combustion chamber according to the invention with a swirl inlet,

Fig. 4 is a plan view of a piston according to the invention,

Fig. 5 is a sectional view of the piston according to the invention of Fig. 4 taken along line VV,

Fig. 6 is a sectional view of another embodiment of the piston of Fig. 4 taken along line VI-VI,

Fig. 7 is a plan view of the cylinder head-side combustion chamber with the first swirl inlet, and

Fig. 8 is a schematic diagram of a method according to the invention.

In Fig. 1, a cylinder head 12 is shown a direct-injection spark-ignition internal combustion engine. The cylinder head 12 comprises an injector 3 , a spark plug 2 , and inlet and outlet channels for the working medium of the engine, which are not described in more detail.

The cylinder head 12 is arranged on a so-called cylinder head parting surface 17 in a manner not shown on an engine block. In the engine block, cylindrical bores (cylinders) are provided, in which combustion or working spaces for the working medium of the engine are formed, which in turn are closed off from the cylinder head 12 . Pistons 7 are guided in the cylinders and limit the combustion chambers formed in the cylinders downwards. The proposed engine has a combustion chamber volume of approximately 0.5 l per cylinder.

The injector 3 is arranged in the cylinder head 12 inclined to the cylinder head parting surface 17 such that the direction of injection of the injector 3 to the cylinder head parting surface 17 has an inclination of 35 ° to 50 °. The injector 3 injects the fuel into the combustion chamber in such a way that a jet cone angle α is present at a distance of approximately 10 mm from a fuel outlet opening 3 a of at least 60 ° under ambient conditions.

FIG. 2 shows a piston crown 8 of the direct-injection spark-ignition internal combustion engine, which has a piston recess 9 . The piston crown 8 is part of a piston 7 , which is arranged coaxially to a cylinder central axis 1 according to FIG. 1.

The piston bowl 9 consists of a first larger part 9 a and a second smaller part 9 b, the second part 9 b being designed as a bulge. The fuel injection takes place in the direction of the cylinder center axis 1 such that the fuel jet direction 18 resulting from a so-called “geometric injector spray direction” 18 a and the direction of charge movement points in the direction of the laterally offset piston recess 9 .

Referring to FIG. 3, on one side between the intake valves 4, 4 are arranged a the injector 3 at the combustion chamber edge in the cylinder head area obliquely such that the cylinder head joint face 17 is an angle of 35 ° included to 50 ° between the injector 3 and. Through the inlet valves 4 and 4 a fresh air flows into the combustion chamber, the ignition location being on or in the immediate vicinity of the cylinder center axis 1 . The inlet channels, not shown, are designed according to the invention in such a way that either a tumble flow alone or a tumble flow combined with a swirl flow results.

Fig. 3 illustrates an arrangement according to the invention of a first swirl inlet 13 on the cylinder head 12 near the injector 3 , which serves to design the flow conditions at the injector in such a way that no fuel droplets adhere to the fuel outlet opening after the injection of the fuel, as a result of which the operating time increases starting fuel injector coking is minimized.

A second swirl inlet 13 a is formed according to FIG. 2 on the piston crown 8 as a concave flattening in the edge region of the piston 7 on the side of the piston crown 8 opposite the piston recess 9 and in the region of the injector 3 , which opens tangentially into the piston recess.

Due to the fresh air supplied to the combustion chamber (intake ducts are not shown), a swirl flow occurs which is conducted to the piston bowl 9 in the area of a cylinder wall (not shown) or in the edge area of the piston 7 along the second swirl inlet 13 a according to FIG. 2.

The piston bowl 9 is arranged offset in relation to the cylinder center axis 1 in such a way that the injected fuel jet 10 has an injection direction superimposed or resulting from the swirl flow direction and fuel injection direction, which lies in the region of the piston bowl center.

Due to the lateral offset of the piston recess 9 and corresponding to the laterally offset injection jet 10 , the mixture cloud is better absorbed into the piston recess 9 . In this case, the essential part of the fuel is injected into the piston recess 9 , so that sufficient swirl of the fuel is achieved by the swirl movement and the tumble flow.

The bulge formed in the piston recess 9 serves to ensure that the flow through the second swirl inlet 13 a is continued in the direction of the larger part 9 a of the piston recess 9 . The swirl flow can thus better enter the laterally offset trough, which accelerates the evaporation of the charge cloud and the fuel on the piston. In addition, transport of the charge cloud is increased by the swirl flow to the ignition site.

For this purpose, it is advantageous that according to Fig. 4 c a boundary wall 9 of the first part 9a of the piston cavity 9 mm having a radius R1 between 15 and 25 mm and having a boundary wall 9 c of the second part 9b of the piston cavity 9 including the bulge has a radius R2 has between 8 mm and 15 mm.

According to FIG. 4, the piston head 8, two exhaust valve bags 19 for a sufficient valve clearance when the fuel spray 10 may not be injected via the piston recess 9 across a very high, and the piston recess wall is provided.

FIG. 5 shows the cross section VV from FIG. 4. In addition to a connecting rod eye 6, the piston 7 has three circumferential grooves 20 for piston rings (not shown). Referring to FIG. 5, the fuel cloud is led by a baffle 9 e to the spark plug 2, wherein by the essentially circular boundary wall 9 of the piston cavity c in the first part 9 a precise deflection is achieved.

According to a further embodiment according to FIG. 6, the piston recess 9 has an undercut 9 g, which is provided in the region of a piston recess part 9 j according to FIG. 2. The piston recess part 9 j is the part of the piston recess 9 which is arranged on the right (according to FIG. 2) with respect to a fuel jet center 1 with respect to the spark plug 2 . The undercut 9 g is crescent-shaped in the view from above (according to FIG. 2).

The piston crown 8 is delimited on the left side according to FIG. 6 by two radii R3 and R4 and on the right side by a bead 21 and the swirl inlet 13 a arranged behind it. A continuous transition is provided between the bead 21 and the swirl inlet 13 a, which includes an angle β between 150 ° and 160 ° with the piston crown surface 8 b or with the horizontal.

The piston recess 9 is delimited on the right side by a radius R5, starting from the bead 21 . Starting from this radius, the piston recess 9 or a side surface of the piston recess 9 extends into the interior of the piston towards the connecting rod eye 6 . The trough bottom 9 d, which runs almost horizontally or parallel to the piston head 8 , is formed from this side surface over two trough bottom radii 9 h. This results in an approximately oval cross-sectional shape of the piston recess 9 .

The undercut 9 g is arranged on the left-hand side opposite R5 in such a way that it prevents the fuel mixture located in the piston recess 9 from escaping from the piston recess. The trough area in the vicinity of the spark plug 2 is undercut-free, so that the stratified charge cloud is deflected as freely as possible via the piston contour to the spark plug. In addition, the undercut 9 g of the piston recess 9 according to FIG. 6 with a perpendicular 9 k to the piston crown surface 8 b forms an angle γ between 10 ° and 20 °, in particular between 13 ° and 17 °.

The undercut 9 g is followed by a further section of the horizontally running part 8 b of the piston head 8 or connects the undercut 9 g with the radius R4 mentioned above.

Fig. 7 shows an enlarged view of the first swirl inlet 13 and the squish fourteenth The first swirl inlet 13 represents a depression formed in the cylinder head, which lowers in the direction of the swirl flow direction in the combustion chamber toward the injector in such a way that the surface around the injector coincides flush with the edge of the injector. A small squeeze area 14 is formed near the injector in the direction of the charge movement swirl so that the removed fuel residues on the injector are transported from the combustion chamber roof to the center of the combustion chamber.

The inlet valves 4 and 4 a are arranged in the cylinder head 12 towards the combustion chamber edge 15 in such a way that a minimum distance 16 between the two inlet valve circumferences is at least 9 mm.

Fig. 8, the direction of charge movement illustrated in the combustion chamber of the gasoline engine according to the invention. The fresh air mass introduced into the combustion chamber has a swirl direction 22 with a counterclockwise direction, the fuel being injected in such a way that the fuel jet 10 , observed from the injector 3 , ie in the spray direction, has a swirl movement 23 with a counterclockwise direction. This can also be done in the opposite direction. That is, the fresh air mass introduced through the first inlet valve has a swirl direction 22 with a clockwise direction, the fuel quantity being injected in such a way that the fuel jet 10 has a swirl movement with a clockwise direction 23 in the spraying direction.

The gasoline engine is operated according to the invention at partial load in stratified charge operation, a swirl flow being generated in the inlet duct, which is variably adjustable by means of a swirl flap, so that the fresh gas partly or completely reaches the combustion chamber via the first inlet duct. If the engine is running at partial load or full load in homogeneous operation, the fresh gas is introduced into the combustion chamber via both inlet channels, the swirl-generating device being controlled depending on the load and speed in such a way that sufficient tubulence or charge movement is generated in the combustion chamber. This leads to the fact that both in stratified charge mode and in homogeneous mode in the ignition area there is an ignitable mixture (λ ≈ 1) in all load areas, in which the best ignition conditions are present, so that reliable ignition is ensured and the spark plug 2 is avoided.

LIST OF REFERENCE NUMBERS

1

Cylinder center axis

2

spark plug

3

injector

3

a Fuel outlet opening

4

intake valve

4

a inlet valve

5

outlet valve

5

a exhaust valve

6

connecting rod

7

piston

8th

piston crown

8th

b piston crown surface

9

piston bowl

9

a larger part of the piston bowl

9

b smaller part of the piston bowl

9

c boundary wall

9

d Piston bowl bottom

9

e baffle

9

f trough edge

9

g undercut

9

h Trough bottom radius

9

j Part of the piston recess opposite the spark plug

9

k Vertical to the piston crown surface

10

Fuel jet

11

Fuel jet center

12

cylinder head

13

First spin entry

13

a Second swirl inlet

14

squish

15

Combustion chamber edge

16

Smallest distance

17

Cylinder head interface

18

Resulting fuel jet direction

18

a Geometric fuel jet direction

19

Auslaßventiltasche

20

circumferential groove

21

bead

22

Fresh air twist direction of rotation

23

Fuel swirl direction of rotation

Claims (23)

1. Combustion chamber of a direct-injection spark-ignition internal combustion engine
a spark plug ( 2 ) arranged approximately in the area of the cylinder central axis ( 1 ) in the cylinder head,
an injector ( 3 ) arranged laterally in the cylinder head,
a piston ( 7 ),
an outlet valve ( 5 , 5 a),
a piston recess ( 9 ) arranged in the piston head ( 8 ) offset to the cylinder center axis ( 1 ),
at least two inlet channels ( 4 , 4 a),
wherein a swirl generating device is arranged in a first inlet channel ( 4 ), and
in both inlet channels ( 4 a) there is a basic tumble flow with an integral tumble number which is at least 25% larger than an integral tumble number of a conventional filling channel. 2. Combustion chamber according to claim 1, characterized in that the piston bowl ( 9 ) from a first larger part ( 9 a), which essentially has a first circular boundary wall ( 9 c), and a second smaller part ( 9 b) is composed , wherein a second boundary wall ( 9 c) of the second smaller part partially has a bulge formed on the outside towards a cylinder wall. 3. Combustion chamber according to claim 1 or 2, characterized in that the boundary wall ( 9 c) of the first part ( 9 a) of the piston bowl has a radius between 15 mm and 25 mm and the boundary wall ( 9 c) of the second part ( 9 b ) the piston bowl including the bulge has a radius between 8 mm and 15 mm. 4. Combustion chamber according to one of the preceding claims, characterized in that in the region of the first part ( 9 a) of the piston bowl, a radius between a piston bowl bottom ( 9 d) and a piston bowl deflecting wall ( 9 e) is between 5 mm and 12 mm. 5. Combustion chamber according to one of the preceding claims, characterized in that the piston bowl ( 9 ) is designed such that a deflection wall ( 9 e) with a height of at least 10 mm between the bowl bottom ( 9 d) and bowl edge ( 9 f) is present. 6. Combustion chamber according to one of the preceding claims, characterized in that the piston recess ( 9 ) has an undercut ( 9 g). 7. Combustion chamber according to one of the preceding claims, characterized in that in the region of the undercut ( 9 g) of the piston bowl ( 9 ) the piston bowl bottom ( 9 d) has a bowl bottom radius ( 9 h) between 6 mm and 12 mm. 8. Combustion chamber according to one of the preceding claims, characterized in that the undercut ( 9 g) of the piston bowl ( 9 ) with a perpendicular 9 k to the piston crown surface ( 8 b) an angle γ between 10 ° and 20 °, in particular between 13 ° and 17 °, includes. 9. Combustion chamber according to one of the preceding claims, characterized in that the undercut ( 9 g) of the piston bowl ( 9 ) in relation to a fuel jet center ( 11 ) preferably in one of the spark plug ( 2 ) opposite part ( 9 j) of the piston bowl ( 9 ) is arranged. 10. Combustion chamber according to one of the preceding claims, characterized in that the piston recess ( 9 ) is aligned with the fuel jet direction resulting from an injection direction of the injector ( 3 ) and a swirl movement of the fuel-air mixture. 11. Combustion chamber according to one of the preceding claims, characterized in that the inlet valve ( 4 ) in the region of the piston recess ( 6 ) is smaller than the other inlet valve ( 4 a). 12. combustion chamber according to one of the preceding claims, characterized, that at least one exhaust valve closes earlier than the other Exhaust valve.   13. Combustion chamber according to the preceding claims, characterized in that the cylinder head ( 12 ) has a first swirl inlet ( 13 ) in the injector area with a small squeeze area ( 14 ). 14. Combustion chamber according to the preceding claims, characterized in that the first swirl inlet ( 13 ) in the cylinder head ( 12 ) is a depression which lowers in the direction of a charge movement swirl located in the combustion chamber up to the injector ( 3 ), the small squeeze area ( 14 ) is formed near the injector ( 3 ) in the direction of the charge movement swirl. 15. Combustion chamber according to one of the preceding claims, characterized in that the piston bowl ( 9 ) is assigned a second swirl inlet ( 13 a) in the piston crown ( 8 ). 16, the combustion chamber according to the preceding claims, characterized in that the second swirl inlet (8 a) in the piston head (8) is formed as a recess outside the piston cavity (9) such that a steered by this recess flow in the direction of the second part ( 9 b) the piston bowl is directed. 17. Combustion chamber according to one of the preceding claims, characterized in that the inlet valves ( 4 , 4 a) are arranged apart from one another towards the combustion chamber edge ( 15 ) in such a way that the smallest distance ( 16 ) between the two inlet valve circumferences is at least 9 mm. 18. Combustion chamber according to one of the preceding claims, characterized in that a direction of injection of the injector to a cylinder head parting surface ( 17 ) has an inclination of 35 ° to 50 °, a beam cone angle (α) at a distance of about 10 mm from a fuel outlet opening ( 3 a) of at least 60 ° at ambient conditions. 19. Combustion chamber according to one of the preceding claims, characterized in that the piston bowl bottom ( 9 d) has an inclination to the cylinder head separating surface ( 17 ). 20. Combustion chamber according to one of the preceding claims, characterized in that the charge movement has a swirl with a direction ( 22 ), seen from above, counterclockwise, and the fuel jet ( 10 ) a swirl movement with a direction ( 23 ) from the injector seen, has a counterclockwise direction, or the charge movement has a swirl with a direction ( 22 ) with the clockwise direction, and the fuel jet has a swirl movement with a direction ( 23 ) with the clockwise direction. 21. A method for mixture formation in a direct injection spark-ignition internal combustion engine, in particular according to claim 1
a spark plug ( 2 ) arranged approximately in the area of the cylinder central axis ( 1 ) in the cylinder head,
an injector ( 3 ) arranged laterally in the cylinder head,
a piston ( 7 ),
an outlet valve ( 5 , 5 a),
a piston recess ( 9 ) arranged in the piston head ( 8 ) offset to the cylinder center axis ( 1 ),
at least two inlet channels ( 4 , 4 a),
characterized,
that in a first inlet channel ( 4 ) a swirl is formed with a charge movement in a direction ( 22 ) counterclockwise, and an amount of fuel is injected such that the fuel jet ( 10 ) in the spray direction with a swirl movement in a direction ( 23 ) against clockwise. 22. A method for mixture formation in a direct injection spark-ignition internal combustion engine, in particular according to claim 1
a spark plug ( 2 ) arranged approximately in the area of the cylinder central axis ( 1 ) in the cylinder head,
an injector ( 3 ) arranged laterally in the cylinder head,
a piston ( 7 ),
an outlet valve ( 5 , 5 a),
a piston recess ( 9 ) arranged in the piston head ( 8 ) offset to the cylinder center axis ( 1 ),
at least two inlet channels ( 4 , 4 a),
characterized,
that in the first inlet channel ( 4 ) a swirl is formed with a charge movement in a clockwise direction ( 22 ), and an amount of fuel is injected such that the fuel jet ( 10 ) is formed in the spray direction with a swirl movement in a clockwise direction ( 23 ) becomes. 23. Method for mixture formation in an internal combustion engine according to claim 21 or 22, characterized, that at partial load in stratified charge a fresh gas flow is variably adjusted in the inlet duct so that the fresh gas partially or completely via the first inlet channel in the Combustion chamber arrives, and in homogeneous operation at part load or At full load the fresh gas takes place via both inlet channels, whereby the swirl-generating device depending on load and speed is controlled in such a way that sufficient tubulence or There is charge movement in the combustion chamber.