DE102022115682A1 - COMBUSTION SYSTEM FOR AN AIR COMPRESSING ENGINE - Google Patents

Abstract

The invention relates to a combustion system for an air-compressing internal combustion engine with at least one reciprocating piston (1) with a rotationally symmetrical combustion bowl (3) which has a bowl base (4) with a cone-like elevation (5) and a surrounding bowl wall (6). to achieve high efficiency, it is provided thata. the internal combustion engine has a compression ratio (CR) of at least 17.5:1 and at most 25:1;b. the first bowl diameter (d1) is 48% to 62% of a maximum diameter (D) of the piston (1);c. the second trough diameter (d2) is 88% to 100% of the first trough diameter (d1);d. the third trough diameter (d3) is 120% to 190% of the first trough diameter (d1);e. the maximum trough depth (t1) is 22% to 35% of the first trough diameter (d1); f. the second section (6b) is arranged at a distance (t2) of between 7% and 16% of the first bowl diameter (d1) from the piston face (7);g. - a first tangent (T1) on the concave annular surface (8) with the piston end face (7) encloses a first angle (Φ) between 25° and 90°.

Description

The invention relates to a combustion system for an air-compressing internal combustion engine with at least one reciprocating piston with a combustion bowl that is essentially rotationally symmetrical to a piston axis and has a bowl bottom that has a maximum bowl depth, with a substantially cone-like or dome-like elevation and a circumferential bowl wall , wherein the trough wall has a substantially toroidal first section which adjoins the trough base and has a maximum inner first trough diameter, followed by a second section which forms a constriction and has a minimum inner second trough diameter which is smaller than the inner first trough diameter, and then a forms a third section forming a bowl edge region with a maximum third bowl diameter, wherein—viewed in a meridian section of the piston—the first section has a concave first wheel of curvature ius and the second section has a convex second radius of curvature, and wherein the third section forms at least one at least essentially concave annular surface which is directly or indirectly adjacent to the second section and is arranged inclined to a plane normal to the piston axis, the annular surface in particular starting at a turning point in a convex annular surface which is formed in the region of a piston end face. The invention also relates to an internal combustion engine with a combustion system of the type mentioned.

From the DE 10 2011 055 170 A1 a diesel engine piston with a combustion chamber is known, which has a profile surface projecting from its inner wall toward a central axis of the combustion chamber and having a protrusion on the inner wall extending a predetermined length from the inner wall. The projection divides injection fuel, which is injected and atomized onto the projection, into a fuel flow in an upper portion and a fuel flow in a lower portion of the combustion chamber. In this case, the combustion bowl has a core formed by a central elevation, which activates a twist, eddy or whirlpool that forms the flow in the combustion chamber. This improves the mixture of fuel and air flowing into the combustion chamber and the mixing ratio can be increased.

the DE 103 92 141 B4 describes a piston for an internal combustion engine that includes a combustion bowl with fuel routing structure for diverting at least a portion of fuel exiting the combustion bowl. The piston includes a sharp edge located on the outer surface of the piston adjacent the entrance to the combustion bowl and a rounded fuel receiving lip located within the combustion bowl.

Furthermore, the EP 2 708 714 A2 discloses a combustion chamber for a diesel engine having a combustion bowl which has a concave shape such that an injected fuel jet creates a swirl or squish flow for mixing with air.

the DE 10 2006 020 642 A1 describes a method for operating a direct-injection self-igniting internal combustion engine, which has pistons each with a piston recess formed into a piston recess, which merges into a substantially annular step space in the transition area to the piston. Injection jets from an injector are guided to the step chamber and deflected there in such a way that a first partial quantity of fuel is deflected in an axial direction and in a radial direction into the piston recess, that a second partial quantity of fuel is deflected in the axial direction and the radial direction via the piston head into the combustion chamber and that a third subset of fuel is deflected in a circumferential direction, with the respective third subsets of adjacent injection jets meeting in the circumferential direction and then being deflected inwards in the radial direction. The wall of the step space is formed by a cylindrical circumferential wall that is straight in the axial direction, by a flat bottom that is straight in the radial direction, and by a transition wall that is curved concavely. This should enable operation with reduced soot and smoke development. While it is suggested that the peripheral wall may be inclined to the axial direction from +10° to -30° and the bottom to the radial direction in a range of +30° to -40°, no explanation is given as to the purpose and effect submitted to this measure.

the CN 103 046 997 A shows a similar piston for a diesel internal combustion engine having a step room with an inclined crown and wall, the crown being at an angle between 8° and 12° with respect to a normal plane to the piston axis and the wall being between 80° with respect to the piston axis and inclined at 100°. As a result, in the area of the stepped chamber, a vortex of the injected fuel is created in the direction of the combustion chamber ceiling and then toward the piston axis.

From the documents CN 2010 74 556 Y , WO 2005/033496 A1 and CN 202 611 915 U are other similar pistons with step rooms for themselves igniting internal combustion engines are known, with the recess wall of the step chamber adjoining the front face of the piston being formed parallel to the piston axis. Fuel jets of the injected fuel hitting the step of the piston are also deflected in the direction of the combustion chamber ceiling and back to the piston axis or bowl axis.

The object of the invention is to provide a highly efficient combustion system for air-compressing internal combustion engines.

1. a. die Brennkraftmaschine ein Kompressionsverhältnis von mindestens 17,5:1 und maximal 25:1, vorzugsweise mindestens 20,1:1 und maximal 23,1:1, aufweist;
2. b. der erste Muldendurchmesser mindestens 48% und maximal 62%, vorzugsweise mindestens 50% und maximal 55%. eines maximalen Durchmessers des Kolbens beträgt;
3. c. der zweite Muldendurchmesser mindestens 88% und maximal 100%, vorzugsweise mindestens 90% und maximal 96%, des ersten Muldendurchmesser beträgt;
4. d. der dritte Muldendurchmesser mindestens 120% und maximal 190%, vorzugsweise mindestens 125% und maximal 150%, des ersten Muldendurchmesser beträgt;
5. e. die maximale Muldentiefe mindestens 22% und maximal 35%, vorzugsweise mindestens 25% und maximal 30%, des ersten Muldendurchmesser beträgt;
6. f. in einem Meridianschnitt betrachtet - ein Punkt des zweite Abschnitt mit minimalem inneren zweiten Muldendurchmesser in einem Abstand von einer Kolbenstirnfläche entfernt angeordnet ist, welcher mindestens 7% und maximal 16%, vorzugsweise mindestens 10% und maximal 13%, des ersten Muldendurchmesser beträgt;
7. g. im Meridianschnitt des Kolbens betrachtet - eine erste Tangente auf die konkave Ringfläche mit der Kolbenstirnfläche einen ersten Winkel von mindestens 25° und maximal 90°, vorzugsweise mindestens 40° und maximal 60°, einschließt, wobei
   1. i. im Falle einer sich mit der Kolbenstirnfläche schneidenden konkaven Ringfläche - die erste Tangente im Schnittpunkt der konkaven Ringfläche mit der Kolbenstirnfläche oder
   2. ii. - im Falle einer konkaven Ringfläche mit einer radial außerhalb anschließenden konvexen Ringfläche - in einem ersten Wendepunkt zwischen der konkaven Ringfläche und der konvexen Ringfläche
   definiert ist.

According to the invention, this is done in that

1. a. the internal combustion engine has a compression ratio of at least 17.5:1 and no more than 25:1, preferably at least 20.1:1 and no more than 23.1:1;
2. b. the first trough diameter at least 48% and at most 62%, preferably at least 50% and at most 55%. a maximum diameter of the piston is;
3. c. the second trough diameter is at least 88% and a maximum of 100%, preferably at least 90% and a maximum of 96% of the first trough diameter;
4. i.e. the third trough diameter is at least 120% and a maximum of 190%, preferably at least 125% and a maximum of 150% of the first trough diameter;
5. e. the maximum trough depth is at least 22% and a maximum of 35%, preferably at least 25% and a maximum of 30% of the first trough diameter;
6. f. Viewed in a meridian section - a point of the second section with minimum internal second bowl diameter is located at a distance from a piston face which is at least 7% and no more than 16%, preferably at least 10% and no more than 13% of the first bowl diameter;
7. G. viewed in the meridian section of the piston - a first tangent on the concave annular surface with the piston end face includes a first angle of at least 25° and at most 90°, preferably at least 40° and at most 60°, wherein
   1. i. in the case of a concave annular surface intersecting with the piston face - the first tangent at the point of intersection of the concave annular surface with the piston face or
   2. ii. - in the case of a concave annular surface with a radially outward adjoining convex annular surface - in a first turning point between the concave annular surface and the convex annular surface
   is defined.

Surprisingly, it has been found that the effective efficiency of the internal combustion engine can be significantly increased through the combination of the features mentioned.

A meridian section of the piston is understood to be a section along the piston axis of the piston, which runs normal to the combustion bowl. The meridian section thus results in a meridian plane that is normal to the combustion bowl and is parallel to or coincident with the piston axis.

In one embodiment variant of the invention, it is provided that an injection device is arranged in the area of the piston axis in such a way that at least one fuel spray hits the second section in at least one stroke position of the piston and the fuel spray passes through the second section into a first spray part directed towards the first section and a second beam part directed towards the third section can be divided.

Extensive tests and calculations have shown that, in combination with the features mentioned above, stagnation zones on the bowl walls in the third section can be avoided if, in a meridian section of the piston located at top dead center, at least one jet axis of the injection device divides the piston bowl into a the lower area adjoining the bowl bottom of the piston and an upper area adjoining it in the direction of the combustion chamber ceiling, with the lower area covering about 54 to 62%, preferably 56%, and the upper area about 38 to 46%, preferably 44%, of the entire combustion chamber bowl amounts to.

Due to the fact that the inner second trough diameter is at least 88% and at most 100% of the first trough diameter, a pronounced division into two beam parts is achieved. For splitting up the fuel jet, it is favorable if--related to a largest diameter of the piston--the second radius of curvature is 0.02±50%.

The fuel jet is guided along the at least one annular surface in the direction of the cylinder wall, with direct contact with the cylinder wall being able to be avoided. This supports the maximum capture of available fresh gas charge for complete low-emission combustion. The fuel impulse generates a charge movement, which develops in the form of a rotation against the injection jet. This occurs both in the area between the piston and through the fire deck of the cylinder head formed combustion chamber ceiling and between the piston and bowl floor. The resulting rotating rollers are fanned even further by the fuel jets and thus enable an almost homogeneous fuel/air mixture. As a result, good and low-emission combustion can be achieved.

The injection device preferably has at least 7 and at most 12, in particular 8, injection openings.

einschließt, welcher zwischen insbesondere zwischen 70° und 80° beträgt. Dabei ist d2 der zweite Muldendurchmesser und t2 der Abstand des Punktes des zweiten Abschnittes mit dem zweiten Muldendurchmesser von der Kolbenstirnfläche.It is particularly advantageous if—viewed in a meridian section of the piston located at top dead center—at least one jet axis of the injection device forms a fuel spray cone angle with the piston axis $$\mathrm{a}={\text{tan}}^{-1}\left(\text{d2/}\left(2*\text{t2}\right)\right)\pm 3°-\text{preferably}\pm \text{1}\text{,5}°-$$

includes, which is between in particular between 70 ° and 80 °. In this case, d2 is the second bowl diameter and t2 is the distance from the point of the second section with the second bowl diameter to the front face of the piston.

In the context of the invention, it is further provided that the injection duration is at least 12° and at most 22°, preferably at least 14° and at most 20°, crank angle.

In order to generate a pronounced first vortex roller directed towards the bowl bottom, it is advantageous if - based on a largest diameter of the piston - the first radius of curvature is 0.06 ± 50% (i.e. 0.06 times the largest diameter of the piston). .

The piston is suitable for internal combustion engines with a swirling intake port structure, with a swirl number of the flow in the combustion chamber around the piston axis being at least 1, ie greater than 1, and at most 2. The intake structure means the shape and arrangement of the intake ports in the cylinder head, which are designed in such a way that when the air flows into the combustion chamber, a swirl with a swirl number between 1 and 2, i.e. greater than 1 and a maximum of 2, is generated.

• 1 einen Kolben einer erfindungsgemäßen Brennkraftmaschine in einem Meridianschnitt in einer ersten Ausführungsvariante;
• 2 die Kolbenmulde dieses Kolbens in einem Meridianschnitt;
• 3 diesen Kolben in einer Draufsicht;
• 4 eine Einlasskanalstruktur in einer Draufsicht und
• 5 eine Kolbenmulde eines Kolbens einer erfindungsgemäßen Brennkraftmaschine in einem Meridianschnitt in einer zweiten Ausführungsvariante;
• 6 einen Kolben einer erfindungsgemäßen Brennkraftmaschine in einem Meridianschnitt in einer dritten Ausführungsvariante
• 7a das Detail VII aus 2;
• 7b das Detail VII aus 2 in einer Ausführungsvariante;
• 8a das Detail VIII aus 5;
• 8b das Detail VIII aus 5 in einer Ausführungsvariante;
• 8c das Detail VIII aus 5 in einer weiteren Ausführungsvariante;
• 9a das Detail IX aus 1;
• 9b das Detail IX aus 1 in einer Ausführungsvariante und
• 10 das Detail X aus 4.

The invention is explained in more detail below using a non-restrictive exemplary embodiment shown in the figures. Show in it:

• 1 a piston of an internal combustion engine according to the invention in a meridian section in a first embodiment;
• 2 the piston bowl of this piston in a meridian section;
• 3 this piston in a plan view;
• 4 an intake port structure in a plan view and
• 5 a piston recess of a piston of an internal combustion engine according to the invention in a meridian section in a second embodiment variant;
• 6 a piston of an internal combustion engine according to the invention in a meridian section in a third embodiment
• 7a detail VII 2 ;
• 7b detail VII 2 in an embodiment variant;
• 8a the detail VIII out 5 ;
• 8b the detail VIII out 5 in an embodiment variant;
• 8c the detail VIII out 5 in a further embodiment variant;
• 9a detail IX 1 ;
• 9b detail IX 1 in one embodiment and
• 10 the detail X off 4 .

1 shows a piston 1 of an air-compressing internal combustion engine, not shown in detail. The piston 1 is particularly suitable for internal combustion engines with a swirl number of at least 1 and a maximum of 2, based on the piston axis 2, designed swirl-forming inlet port structure 20. An example of such an inlet structure 20 with a swirl-generating inlet port 21 and a filling port 22 is in 4 shown.

In the piston 1 a combustion chamber recess 3 designed rotationally symmetrical to the piston axis 2 is formed. Combustion bowl 3 of piston 1, which forms at least a large part of the combustion chamber, consists of a bowl base 4 with a cone-like central elevation 5 and a circumferential bowl wall 6. Beginning at bowl base 4, bowl wall 6 has a first section 6a and an adjoining second section 6b , as well as a third section adjoining the second section 6b at 6c, the third section 6c adjoining the piston end face 7 facing the cylinder head (not shown in more detail) and forming a bowl edge area 12. The second section 6b has the function of a spray divider for the fuel jets S.

In the first section 6a, the cavity wall 6 is designed at least partially in the shape of a circular torus, with--viewed in a meridian section of the piston 1--the concave first radius of curvature R1 of the first Section 6a is about 0.06 ± 50% of the largest diameter D of the piston 1. In the region of the first section 6a, the combustion bowl 3 has an inner first diameter d1 which is at least 48% and at most 62% of the maximum diameter D of the piston 1. In the area of the second section 6b, the trough wall 6 is drawn in and overhangs, the inner second trough diameter d2 measured in the area of the second section 6b being at least 88% and at most about 100% of the inner first trough diameter d1. In relation to the maximum piston diameter D, the inner first recess diameter d1 is therefore approximately 0.42 to 0.62.

The third section 6c of the trough wall 6 has at least one concave annular surface 8 with a third radius of curvature R3, which in FIG 1 illustrated embodiment directly, so running and seamlessly, adjoins the second radius of curvature R2 of the second section 6b and ends in the piston end face 7. The line of intersection between the concave annular surface 8 and the piston face 7 points in the in 1 and 2 The first exemplary embodiment illustrated has a diameter d3 which is at least approximately 120% and at most 190% of the first bowl diameter d1 of the piston 1 . Im in the 1 Viewed from the meridian section of the piston 1 shown, a first tangent T1 on the concave annular surface 8 in the region of the piston end face 7 spans a first angle Φ between approximately 25° and 90° with a normal plane ε on the piston axis 2 . Experiments have shown that the best results can be achieved when the third radius of curvature R3 of the concave annular surface 8 is at most about 50% of the diameter D of the piston 1.

In the in the 1 and 2 Considering the meridian sections of the piston 1 shown, the bowl wall 6 is convexly curved in the second section 6b and has a second radius of curvature R2 of approximately 0.02±50% times the largest diameter D of the piston 1. The trough wall 6 runs between the first section 6a and the second section 6b, it also being possible for a straight section to be formed between the first radius of curvature R1 and the second radius of curvature R2. As an alternative to this, the first radius of curvature R1 can transition directly into the second radius of curvature R2 via a second turning point W2. A second tangent T2 through the second turning point W2 in the transition between the first section 6a and the second section 6b spans a second angle β of approximately 35° to 45° with the normal plane ε on the piston axis 2 .

In the exemplary embodiment shown, the maximum depression depth 13 is at least 22% and at most 35% of the first depression diameter d1.

The minimum depression depth t3 measured in the area of the central elevation 5 is approximately 4% to 8%, in particular 6%, of the maximum diameter D of the piston 1. A distance t2 of the second section 6b measured away from the piston end face 7 in the direction of the piston axis 2 is at least 7% and at most 16% of the first trough diameter d1. The conical elevation 5 spans a third angle δ of approximately 20° to 40° with the piston axis 2--approximately 30° in the example. The elevation 5 has a central radius of curvature RZ, which is approximately 6% of the largest diameter D of the piston 1, for example.

As in 1 and 2 indicated, fuel is injected via an injection device 10 arranged centrally in the cylinder, the fuel impinging on the second section 6b of the cavity wall 6 in at least one stroke position of the piston 1 . The jet axes Sa of the fuel jet span a fuel spray cone angle α of at least 70° and at most 80° with the piston axis 2 .

The geometry of the piston 1 and the direction of injection of the injection device 10 are coordinated in such a way that - viewed in a meridian section of the piston 1 located at top dead center TDC - at least one jet axis Sa of an injection jet of the injection device 10, which points to the point P of the second section 6b meets the minimum inner second bowl diameter d2, the combustion chamber bowl 3 is divided into a lower area 3a and an upper area 3b, with the lower area 3a being about 54% to 62%, preferably 56%, and the upper area 3b being about 38% to 46%. , preferably 44%, of the entire area of the combustion bowl 3 ( 1 , 2 ).

In the 5 The second embodiment variant shown differs from that in 1 and 2 illustrated first embodiment in that between the concave annular surface 8 and the piston end surface 7 a convex annular surface 9 is formed with a fourth radius of curvature R4, which is, for example, about 0.02 ± 50% times the largest diameter D of the piston 1, and in particular substantially corresponds to the second radius of curvature R2. A second turning point W2 is formed between the concave annular surface 8 and the convex annular surface 9a ( 10 ). The first tangent T1 through the first turning point W1 between the concave annular surface 8 and the convex annular surface 9 spans a first angle Φ between approximately 25° and 90°, in particular 60°, with the normal plane ε on the piston axis 2 .

At the in 6 In the third embodiment variant shown, the third section 6c has a conical annular surface 9b between the second section 6b and the concave annular surface 8, which spans a fourth angle φ between approximately 10° and 40°, for example 20°, with the normal plane ε.

The swirl-supported combustion system according to the invention for compression-ignited or air-compressing internal combustion engines with a defined swirl level with a swirl number between 1 and 2 combines a high compression ratio CR with a short injection duration, which leads to increased thermodynamic efficiency and thus to higher effective efficiency (BTE=Break Thermal Efficiency ) leads. The compression ratio CR should be between 17.5:1 and 25:1, in particular between 20:1 and 23:1, while the injection duration should be in a crank angle range CA of 12° to 22°, particularly preferably 14° to 20° .

The combustion system can be defined by the cylinder bore diameter or the maximum piston diameter D, the first bowl diameter d1, the second bowl diameter d2, the third bowl diameter d3, the maximum bowl depth t1 that defines the depth of the combustion chamber, the depth of the spray divider 11 that is defined by the distance t2 from the piston end face 7 at the point P of the second section 6b with minimum inner second bowl diameter d2, the first angle Φ between the bowl edge region 12 and the piston face 7 and the fuel spray cone angle α, as in FIGS 1 until 6 is shown.

The main features of the combustion system can be reduced by the spray divider 11, which divides the fuel jets S into a first jet part S1 and a second jet part S2, an enlarged third bowl diameter d3 in the area of the bowl edge area 12, which is located above the spray divider 11, around the fuel in the direction of the cylinder head and liner, and describe the area below the spray divider 11, which directs the fuel to the center of the combustion bowl 3 (see 2 and 6 ).

In order to achieve a high compression ratio CR with sufficient bowl depth t1, a narrow piston bowl design is required. The first depression diameter d1 should be in a range between 48% and 62%, in particular 50% and 55%, based on the maximum piston diameter D.

With the short injection duration and small volume of the combustion chamber due to the high compression ratio CR, this combustion bowl 3 improves the mixing of the fuel with the charge air for improved combustion efficiency.

The spray distributor 11 divides the injected fuel jets S into two jet parts S1, S2 and supports the spread of fuel to the desired locations during the very short injection duration. It is characterized by the ratio of the second bowl diameter d2 to the first bowl diameter d1, which defines the splitting and deflection of the beam, which is between 88% and 100%, preferably 90% to 96%, and the distance t2 of the beam splitter 11 from the piston end face 7, which is between 7 % and 16%, preferably between 8% and 13% of the first trough diameter d1, as in FIGS 7a and 7b for differently overhanging spray manifolds 11 is illustrated.

The increased third bowl diameter d3 gives the possibility to direct the vaporized fuel towards the cylinder head fire deck and the cylinder liner for better mixing with the charge air from this area, resulting in improved combustion efficiency, as the examples in , and demonstrate. The third trough diameter d3 should be in a range from 120% to 190%, preferably in a range from 125% to 150% relative to the first trough diameter d1. In the area of the piston end face 7, the bowl edge area 12 has a first angle Φ to a normal plane ε on the piston axis 2, which influences the propagation direction of the fuel. According to the invention, this first angle Φ is in a range between 25° and 90°, preferably 40° to 60°.

The elevation 5, which can be cone-shaped or slightly dome-shaped, enables better fuel spread and mixing with the air charge towards the center of the combustion chamber recesses 3. 9a shows an embodiment with a simple conical elevation 5 and 9b an embodiment variant with a dome-shaped elevation 5. The mixing process in the lower region 3a of the piston bowl 3 is mainly influenced by the ratio of the second bowl diameter d2 to the first bowl diameter d1, which defines the splitting and deflection of the jet described above.

In order to achieve high combustion efficiency, the ratio of the maximum depression depth t1 to the first depression diameter d1 should be between 22% and 35%, preferably 24% to 32%.

mit einem Einstellbereich von ±3° - vorzugsweise ±1,5° - zur Optimierung auf dem Prüfstand anhand anwendungsspezifischer Randbedingungen verknüpft.Adapting the fuel spray cone angle α to the shape of the piston bowl 3 is essential for high combustion efficiency. Since the combustion system described combines short injection durations near top dead center with almost no vertical movement of the piston, the splitting effect of the fuel spray S through the spray distributor 11 must be ensured. To ensure high effective efficiency, half the fuel spray cone angle α with the bowl geometry is above the formula $$\mathrm{\alpha =}{\text{tan}}^{-1}\left(\text{d2/}\left(\text{2*t2}\right)\right)$$

with an adjustment range of ±3° - preferably ±1.5° - for optimization on the test bench based on application-specific boundary conditions.

The combustion system according to the invention includes a swirl support in the intake ports for optimal use of the trapped air charge and the air/fuel mixture. The spray hole number associated with the high fuel injection rate (short injection duration) is optimally matched to the induced swirl level and completes the combustion system configuration for maximum utilization of the trapped air charge and mixing with the injected fuel.

3 shows an example of an injector 10 with eight injection ports. It is shown that the fuel jet S splits in all directions at the jet splitter 11, so that two fuel jets S approach one another. In order to achieve high combustion efficiency, interaction of each adjacent fuel jet S must be prevented. Since the twist movement DR influences this effect, the number of injection openings of the injection device 10 must be adjusted accordingly in a range between 7 and 12. The higher the swirl movement of the charge air, the smaller the number of adapted fuel jets S and the injection openings of the injection device 10.

QUOTES INCLUDED IN DESCRIPTION

This list of the documents cited by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent Literature Cited

• DE 102011055170 A1 [0002]
• DE 10392141 B4 [0003]
• EP 2708714 A2 [0004]
• DE 102006020642 A1 [0005]
• CN 103046997A [0006]
• CN201074556Y[0007]
• WO 2005033496 A1 [0007]
• CN202611915U[0007]

Claims (10)

Combustion system for an air-compressing internal combustion engine with at least one reciprocating piston (1) with a combustion chamber bowl (3) that is essentially rotationally symmetrical to a piston axis (2) and has a bowl base (4) that has a maximum bowl depth (t1), with a has a substantially cone-like or dome-like elevation (5) and a peripheral trough wall (6), the trough wall (6) adjoining the trough base (4), a substantially toroidal first section (6a) with a maximum inner first trough diameter (d1) , followed by a second section (6b), preferably forming a constriction, with a minimum inner second trough diameter (d2) which is smaller than or equal to the inner first trough diameter (d1), and then a third section forming a trough edge region (12). Section (6c) with a maximum third trough diameter (d3) forms, where - in a meridian section of the piston (1) considered - the first section (6a) has a concave first radius of curvature (R1) and the second section (6b) has a convex second radius of curvature (R2), and wherein the third section (6c) has at least one attached to the second section (6b) directly or indirectly adjoining and inclined to a normal plane (ε) to the piston axis (2), at least essentially concave annular surface (8), wherein in particular the concave annular surface (8) from a first turning point (W1) into a convex Ring surface (9a) which is formed in the area of a piston end face (7), characterized in that a. the internal combustion engine has a compression ratio (CR) of at least 17.5:1 and no more than 25:1, preferably at least 20.1:1 and no more than 23.1:1; b. the first depression diameter (d1) is at least 48% and at most 62%, preferably at least 50% and at most 55%, of a maximum diameter (D) of the piston (1); c. the second trough diameter (d2) is at least 88% and at most 100%, preferably at least 90% and at most 96%, of the first trough diameter (d1); i.e. the third trough diameter (d3) is at least 120% and at most 190%, preferably at least 125% and at most 150%, of the first trough diameter (d1); e. the maximum trough depth (t1) is at least 22% and at most 35%, preferably at least 25% and at most 30%, of the first trough diameter (d1); f. viewed in a meridian section of the piston (1) - a point (P) of the second section (6b) with the minimum inner second bowl diameter (d2) is arranged at a distance (t2) from a piston end face (7) which is at least 7% and at most 16%, preferably at least 10% and at most 13%, of the first trough diameter (d1); G. viewed in the meridian section of the piston (1) - a first tangent (T1) on the concave annular surface (8) with the piston end face (7) a first angle (Φ) of at least 25° and at most 90°, preferably at least 40° and at most 60 °, where i. - in the case of a concave annular surface (8) intersecting with the piston end surface - the first tangent (T1) at the point of intersection of the concave annular surface (8) with the piston end surface (7), or ii. - in the case of a concave annular surface (8) with a radially outward adjoining convex annular surface (9a) - is defined in a first turning point (W1) between the concave annular surface (8) and the convex annular surface (9a). combustion system Claims 1 , characterized in that in the area of the piston axis (2) an injection device (10) is arranged in such a way that at least one fuel jet (S) hits the second section (6b) in at least one stroke position of the piston (1) and the fuel jet (S ) can be divided by the second section (6b) into a first beam part (S1) directed towards the first section (6a) and a second beam part (S2) directed towards the third section (6c). combustion system claim 2 , characterized in that - viewed in a meridian section of the piston (1) located at top dead center - at least one jet axis (Sa) of the injection device (10) extends the piston bowl (3) into a cavity bottom (4) of the piston (1) adjoining lower area (3a) and an upper area (3b) adjoining it in the direction of the combustion chamber ceiling, the lower area (3a) being about 54 to 62%, preferably 56%, and the upper area (3b) being about 38 to 46%, preferably 44% of the entire combustion bowl (3). combustion system claim 2 or 3 , characterized in that the injection device (10) has at least 7 and a maximum of 12, preferably 8, injection openings. Combustion system according to one of claims 2 until 4 , characterized in that - viewed in a meridian section of the piston (1) located at top dead center - at least one jet axis (Sa) of the injection device (10) forms a fuel spray cone angle with the piston axis (2). $$\mathrm{a}={\text{tan}}^{-1}\left(\text{d2/}\left(2*\text{t2}\right)\right)\pm 3°-\text{preferably}\pm \text{1}\text{,5}°-$$

includes, where d2 is the second bowl diameter and t2 is the distance of the point (P) of the second section (6b) with the second bowl diameter (d2) from the piston face (7). Combustion system according to one of claims 2 until 4 , characterized in that the fuel spray cone angle (α) is between 70° and 80°. Combustion system according to one of claims 2 until 6 , characterized in that the injection duration is at least 12° and at most 22°, preferably at least 14° and at most 20°, crank angle (CA). Combustion system according to one of Claims 1 until 7 , characterized in that the internal combustion engine has an intake port structure which is designed to generate a flow in the combustion chamber with a swirl rate about the piston axis (2) of at least 1, preferably a maximum of 2. Combustion system according to one of Claims 1 until 8th , characterized in that - based on a largest diameter (D) of the piston (1) - the first radius of curvature (R1) is 0.06 ± 50% and/or the second radius of curvature (R2) is 0.02 ± 50%. Internal combustion engine with a combustion system according to any one of Claims 1 until 9 .

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