Internal combustion engine having a top-down cooling concept

Abstract

The invention relates to an internal combustion engine having a top-down cooling concept, in particular with a plurality of cylinders (2), having a liquid-cooled cylinder head (1) with a first cooling chamber (81) adjoining a fire deck (10) and a second cooling chamber (82), which is separated from the first cooling chamber (83) by an intermediate deck, and which is predominantly further away from the fire deck (10) than the first cooling chamber (81), wherein the first cooling chamber (81) and the second cooling chamber (82) are flow-connected to one another in the region of the ignition device (6), with an intake port arrangement (30) on an intake side (3) and an exhaust port arrangement (40) on an exhaust side (4), having, per cylinder, two intake valves (312, 322), two exhaust valves (412, 422), an ignition device (6) opening centrally into a combustion chamber (5) and an injection device (7) opening laterally into the combustion chamber (5), which is arranged between a first intake port (31) and a second intake port (32) of the intake port arrangement (30). In order to enable sufficient cooling of the injection device (7), the first intake port (31) and the second intake port (32) of each cylinder (2) in the cylinder head (1) are routed separately starting from at least one lateral flange surface (33) of the cylinder head (1), and the injection device (7) is at least partially surrounded by a cooling chamber (85), which is flow-connected to the second cooling chamber (82) or is formed as part of the second cooling chamber (82).

Description

[0001] Internal combustion engine with a top-down cooling concept

[0002] The invention relates to an internal combustion engine with a top-down cooling concept, in particular with a plurality of cylinders, with a liquid-cooled cylinder head with a first cooling chamber bordering a fire deck and a second cooling chamber which is separated from the first cooling chamber by an intermediate deck and which is predominantly further away from the fire deck than the first cooling chamber, wherein the first cooling chamber and the second cooling chamber are fluidly connected to one another in the region of the ignition device, with an inlet duct arrangement on an inlet side and an outlet duct arrangement on an outlet side of the cylinder head, with two inlet valves per cylinder, two outlet valves, an ignition device opening centrally into a combustion chamber and an injection device opening laterally into the combustion chamber, which is arranged between a first inlet duct and a second inlet duct of the inlet duct arrangement.

[0003] A top-down cooling concept is a cooling concept in which the coolant first flows through the second cooling chamber further away from the fire deck and then through the first cooling chamber closer to the fire deck.

[0004] Such an internal combustion engine with two intake valves and two exhaust valves, a central ignition device, and a side injection device is known from AT 524 316 B1. An intake port leads to each intake valve, with the intake ports extending from a common main intake port within the cylinder head. A bore arrangement with several cooling bores is provided to cool the injection device located between the two intake ports.

[0005] US Pat. No. 5,983,843 A discloses a single-cylinder internal combustion engine with a laterally mounted injector. A bore arrangement with several cooling bores extending from one end face is provided for cooling the injector. This bore arrangement is less suitable for internal combustion engines with more than two cylinders.

[0006] EP 1 443 188 A2 describes a reciprocating piston internal combustion engine with at least one combustion chamber with direct gasoline injection, comprising a cylinder head having two intake gas exchange valves, two exhaust gas exchange valves, an ignition device arranged between the gas exchange valves, and a gasoline injection valve arranged between an intake and an exhaust gas exchange valve. The intake valve stems and the exhaust valve stems each define a plane that is aligned largely parallel to a longitudinal axis of the internal combustion engine. The longitudinal axis of the gasoline injection valve is aligned parallel to the cylinder axis.

[0007] WO 2007 / 125400 A2 discloses a spark-ignition internal combustion engine with a centrally arranged ignition device and an injection device arranged off-center in the roof-shaped combustion chamber ceiling between two exhaust valves.

[0008] In internal combustion engines of the type mentioned above, there is sometimes insufficient free space on the intake side in the area of ​​the injection device to ensure sufficient cooling of the injection device.

[0009] The object of the invention is to enable sufficient cooling of the injection device in an internal combustion engine of the type mentioned at the outset in a simple manner.

[0010] According to the invention, this object is achieved in an internal combustion engine of the type mentioned at the outset in that the first inlet channel and the second inlet channel of each cylinder are guided separately in the cylinder head starting from at least one lateral flange surface of the cylinder head, and in that the injection device is at least partially surrounded by a cooling chamber which is fluidly connected to the second cooling chamber or is formed as part of the second cooling chamber.

[0011] By routing the first intake port and the second intake port of each cylinder separately in the cylinder head, starting from at least one lateral flange surface of the cylinder head, sufficient space can be provided between the intake ports for the arrangement and cooling of the injection device. The cooling chamber that at least surrounds the injection device enables sufficient cooling of the injection device.

[0012] In one embodiment of the invention, the cooling chamber is connected to a cooling jacket of a cylinder block adjacent to the cylinder head via at least one connecting channel arranged in the fire deck on the intake side. This allows the injection device to be cooled directly with the coolant coming from the cylinder block.

[0013] Preferably, at least one first cylinder head bolt is arranged between the first intake port and the injection device, and / or at least one second cylinder head bolt is arranged between the second intake port and the injection device. The intake ports are thus each routed between two cylinder head bolts, with the intake ports extending in a curve around the cylinder head bolts adjacent to the intake device. This allows sufficient installation space to accommodate cooling channels and cooling chambers for cooling the injection device.

[0014] In one embodiment of the invention, at least two adjacent intake ports of two adjacent cylinders extend from a common flange surface. These at least two intake ports of adjacent cylinders are advantageously arranged directly on both sides of a transverse engine plane extending between two adjacent cylinders. Thus, the first intake port and the second intake port of each cylinder are spaced apart as far as possible, with the maximum distance between the two intake ports approximately corresponding to the cylinder bore diameter.

[0015] In this case, at least one third cylinder head screw can be arranged in the region of at least one transverse engine plane between two adjacent cylinders, wherein the third cylinder head screw preferably has a smaller distance from a longitudinal engine plane spanned by the cylinder axes than the first cylinder head screw and / or the second cylinder head screw.

[0016] One embodiment of the invention provides that the first cooling chamber has at least one first cooling channel arranged between the first inlet channel and the injection device, and at least one second cooling channel arranged between the second inlet channel and the injection device, wherein the first cooling channel and / or the second cooling channel is / are preferably cast. The first and second cooling channels at least partially surround the injection device and extend from a third web channel, which runs close to the fire deck in the region of the intake valve seats between the two intake channels.

[0017] The intake valves and / or exhaust valves are advantageously arranged essentially parallel to the cylinder axis - with a maximum deviation of ±5°.

[0018] Preferably, the distance between the orifice of the injection device and the cylinder axis is 35% to 45% of the cylinder bore diameter. This ensures that the fuel is optimally injected into the – preferably cylindrical – intake flow.

[0019] A pronounced tumble charge movement can be initiated in the combustion chamber if at least one of the intake ports – preferably both intake ports – is / are designed to generate tumble. To support the tumble charge movement, it is further advantageous if at least one, preferably asymmetrical, chamfer is incorporated into the fire deck of the cylinder head on the side of at least one intake valve seat facing the exhaust side.

[0020] To initiate a symmetrical intake tumble flow, it is advantageous if the first intake port and the second intake port of at least one cylinder are designed symmetrically to a transverse engine plane containing the cylinder axis. Advantageously, the longitudinal axis of the injection device is arranged in a transverse engine plane containing the cylinder axis.

[0021] In a further embodiment of the invention, it is provided that at least one outlet channel borders on the first cooling chamber and on the second cooling chamber, wherein the second cooling chamber is arranged at least partially - preferably completely - on a side of the outlet channel facing away from the first cooling chamber.

[0022] Advantageously, the first cooling chamber in the region of the ignition device is fluidly connected to the second cooling chamber via at least one connecting channel arranged on the outlet side and / or inlet side, wherein the connecting channel is preferably a cast channel.

[0023] Preferably, the first cooling chamber in the region of the ignition device is fluidly connected to the second cooling chamber via at least one connecting channel, preferably arranged on the exhaust side, wherein the connecting channel is preferably a cast channel. The coolant flows directly from the cylinder block into the second cooling chamber—preferably in the region of the injection device—and flows into the first cooling chamber near the fire deck via the at least one connecting channel in the region of the ignition device.

[0024] Within the scope of the invention, it is further provided that an ignition device sleeve for receiving the ignition device is arranged in the cylinder head, wherein the ignition device sleeve is preferably designed wet and directly borders on the first cooling chamber and / or the second cooling chamber.

[0025] Furthermore, for good cooling of the injection device, it is advantageous if an injector sleeve is arranged in the cylinder head to accommodate the injection device, wherein the injector sleeve is preferably designed wet and directly borders on the cooling chamber and / or the second cooling space.

[0026] The invention is explained in more detail below with reference to the non-limiting exemplary embodiment shown in the figures. Therein: Fig. 1 shows a cylinder head of an internal combustion engine according to the invention in a section along line II in Fig. 5;

[0027] Fig. 2 shows the cylinder head from Fig. 1 in a detailed view;

[0028] Fig. 3 the intake ports of the cylinder head in an axonometric core representation;

[0029] Fig. 4 shows the cylinder head in section along the line IV - IV in Fig. 6;

[0030] Fig. 5 shows the cylinder head in a section along the line V - V in Fig. 4;

[0031] Fig. 6 shows the cylinder head in a section along the line VI - VI in Fig. 2;

[0032] Fig. 7 the cylinder head in a combustion chamber side view;

[0033] Fig. 8 shows a piston recess of a piston of the internal combustion engine in an axonometric representation;

[0034] Fig. 9 shows the piston recess in a section along the line IX-IX in Fig. 8;

[0035] Fig. 10 shows the piston recess in a section along the line XX in Fig. 8; and

[0036] Fig. 11 the piston recess in a section along the line XI-XI in Fig. 8.

[0037] The cylinder head 1 of a multi-cylinder internal combustion engine shown in Figs. 1 to 7 has, for each cylinder 2, an inlet port arrangement 30 arranged on an inlet side 3 and an outlet port arrangement 40 arranged on an outlet side 4. The inlet-side longitudinal side wall 13 of the cylinder head 1 runs in the longitudinal direction of the internal combustion engine and is oriented, for example, parallel to the engine longitudinal plane 12. The tumble-generating inlet port arrangement 30 has a first inlet port 31 with a first inlet valve seat 311 for a first inlet valve 312 and a second inlet port 32 with a second inlet valve seat 321 for a second inlet valve 322. The two inlet channels 31, 32 originate from the inlet side 3 of the cylinder head 1 and are each guided completely separately between a flange surface 33 on the inlet side 3 and the inlet valve seats 311, 312 (Fig. 2, Fig. 7).

[0038] In the cylinder head 1 shown, at least one cylinder 2 is assigned eight cylinder head bolts 15, which - viewed in plan view - can be arranged, for example, in the shape of a regular octagon and have the same radial distance from the cylinder axis 2a. The cylinder head bolts 15 arranged in the region of the engine transverse plane 111 between two adjacent cylinders 2 are assigned to both adjacent cylinders 2. At least one first cylinder head bolt 151 is arranged between the first inlet port 31 and the injection device 7, and at least one second cylinder head bolt 152 is arranged between the second inlet port 32 and the injection device 7. In the region of an engine transverse plane 111 between two cylinders 2, at least one third cylinder head bolt 153 is arranged between two adjacent inlet ports 31, 32 belonging to different cylinders 2.The third cylinder head screw 153 has a smaller distance b from a longitudinal engine plane 12 defined by the cylinder axes 2a than the first cylinder head screw 151 or the second cylinder head screw 152, whose distances from the longitudinal engine plane are each designated by c (Fig. 2).

[0039] The intake ports 31, 32 are thus each routed between two cylinder head bolts 151, 152, with the intake ports 31, 32 extending in an arc around the cylinder head bolts 151, 152 adjacent to the intake device 7. This allows sufficient installation space to accommodate cooling channels and cooling chambers for cooling the injection device 7.

[0040] The intake ports 31, 32 are designed to generate a cylindrical charge movement in the combustion chamber 5. The valve axes of the first intake valve 312 and the second intake valve 322 are designated by reference numerals 312a, 322a (Fig. 2, Fig. 3, Fig. 7).

[0041] In at least one cylinder 2, the first inlet port 31 and the second inlet port 32 are arranged as far apart from each other as possible, wherein, for example, the maximum distance A between the two inlet ports 31, 32 corresponds approximately to the bore diameter D of the cylinder 2 (Fig. 2).

[0042] The exhaust port arrangement 40 has a first exhaust port 41 with a first exhaust valve seat 411 for a first exhaust valve 412 and a second exhaust port 42 with a second exhaust valve seat 421 for a second exhaust valve 422. The two exhaust ports 41, 42 open into a common main exhaust port 45 per cylinder 2. The valve axes of the first exhaust valve 412 and the second exhaust valve 422 are indicated by reference numerals 412a, 422a (Fig. 2, Fig. 7).

[0043] In the region of the cylinder axis 2a of the cylinder 2, an ignition device 6 opening into the combustion chamber 5 is centrally arranged, wherein the ignition device 6 is received by an ignition device sleeve 60 arranged in the cylinder head 1. The eccentricity of the longitudinal axis 6a of the ignition device 6 to the cylinder axis 2a is a maximum of 2-3 mm or a maximum of 2% of the bore diameter D (Fig. 7). Between the two inlet ports 31, 32, an injection device 7 for direct fuel injection into the combustion chamber 5 is arranged at a first distance a from the cylinder axis 2a, wherein the first distance a between the opening 71 of the injection device 7 and the cylinder axis 2a is approximately 35% to 45% of the bore diameter D of the cylinder 2. The first distance a is here greater than the second distance b measured between the valve axis 312a, 322a of the intake valve 312, 322 and the cylinder axis 2a.In the exemplary embodiment, the injection device 7 is arranged in an injector sleeve 70 that is firmly connected to the cylinder head 1 (Fig. 7). Alternatively, the injection device 7 can also be arranged directly in the cylinder head 1—i.e., without an injector sleeve 70.

[0044] The combustion chamber ceiling 14 of the cylinder head 1, formed by the fire deck 10, is essentially flat, in particular planar, and perpendicular to the cylinder axis 2a—i.e., not "roof-shaped." The valve axes 312a, 322a; 412a, 422a of the intake valves 312, 322 and the exhaust valves 412, 422 are inclined relative to the cylinder axis 2a by an angle of at most 5° and are preferably parallel to the cylinder axis 2a. The longitudinal axis 7a of the injection device 7 is inclined relative to the cylinder axis 2a by a first angle α of 45°.

[0045] The liquid-cooled cylinder head 1 has a cooling chamber arrangement 8 designed particularly for top-down cooling concepts, comprising a first cooling chamber 81 and a second cooling chamber 82, wherein the second cooling chamber 82 is arranged above the first cooling chamber 81, farther from the fire deck. An intermediate deck 16 of the cylinder head is formed between the first cooling chamber 81 and the second cooling chamber 82, separating the two cooling chambers 81, 82 from each other. The first cooling chamber 81 is arranged below the outlet channels 41, 42 adjacent to the fire deck 10—that is, between the outlet channels 41, 42 and the fire deck 10. The first cooling chamber 81 has an inner annular channel 811 formed circumferentially around the ignition device 6 between the ignition device 6 and the inlet channels 31, 32 and the outlet channels 41, 42 and a circumferentially formed outer annular channel 812 in the region of the cylinder rim 20 (Fig. 4).In top-down cooling concepts, the coolant first flows through the second cooling chamber 82, which is further away from the fire deck, and only then through the first cooling chamber 81, which is closer to the fire deck.

[0046] The inner annular channel 811 is fluidly connected on the exhaust side 4 to the outer annular channel 812 via a cast first web channel 813, which is arranged between the exhaust valve seats 411, 421 of the exhaust valves 412, 422 in the region of a transverse engine plane 11 running through the cylinder axis 2a. Furthermore, the inner annular channel 811 is fluidly connected to the outer annular channel 812 in the region of a longitudinal engine plane 12 containing the cylinder axis 2a via cast second web channels 814, wherein the second web channels 814 are each arranged between an exhaust valve seat 411, 421 and an intake valve seat 311, 321. Furthermore, a third web channel 815 is arranged between the inlet valve seats 311, 321 in the region of the engine transverse plane 11, which third web channel is divided into a first cooling channel 816 and a second cooling channel 817 and connects the inner ring channel 811 to the outer ring channel 812 via these cooling channels 816, 817.The cooling channels 816, 817 surround the injection device 7 on both sides of the engine transverse plane 11 and serve in particular to cool the area of ​​the mouth 71 of the injection device 7.

[0047] The third web channel 815 and the cooling channels 816, 817 are cast and extend substantially radially with respect to the cylinder axis 2a in a plane normal to the cylinder axis 2a, with the first cooling channel 816 being arranged between the first inlet channel 31 and the injection device 7, and the second cooling channel 817 being arranged between the second inlet channel 32 and the injection device 7. The cooling channels 816, 817 each extend approximately centrally between the inlet channels 31, 32 and the injection device 7 and are thus approximately equidistant from the inlet channels 31, 32 and the injection device 7 (Fig. 4).

[0048] Viewed in plan view, the first cooling channel 816 and the second cooling channel 817 form an angle ß between approximately 20° and 45°, preferably approximately 30° ± 5°. The first cooling channel 816 and the second cooling channel 817 are arranged symmetrically to the transverse engine plane 11 containing the cylinder axis 2a and the longitudinal axis 7a of the injection device 7 (Fig. 4).

[0049] Above the outlet channels 41, 42—that is, on the side of the outlet channels 41, 42 facing away from the first cooling chamber 81—is the second cooling chamber 82, which is fluidly connected to the inner annular channel 811 of the first cooling chamber 81 via a cast connecting channel 83 in the region of the ignition device 6. The main cooling water transfer between the upper second cooling chamber 82 and the lower first cooling chamber 81 occurs via the connecting channel 83, which is arranged, for example, on the outlet side 4. The ignition device sleeve 60 directly borders the first cooling chamber 81, the connecting channel 83, and the second cooling chamber 82, as can be seen from Fig. 6. The connecting channel 83 forms the main cooling water transfer between the second cooling chamber 82 and the first cooling chamber 81.The cooling water flows from the second cooling chamber 82 via the connecting channel 83 into the inner annular channel 811 of the first cooling chamber 81 and from this inner annular channel 811 via the first web channel 813, the second web channels 814 in the engine longitudinal plane 12 and the third web channel 815 on the inlet side through the cooling channels 816, 817 on both sides of the injection device 7 into the outer annular channel 812 of the first cooling chamber 81, as indicated by arrows P in Fig. 5 and Fig. 6. Optionally, a coolant supply directly from a cylinder block (not shown in detail), which is connected to the cylinder head 1, can also be used to cool the injection device 7. As indicated by the arrows S in Fig.6, the coolant flows from the cooling jacket of the cylinder block via a connecting channel 84 provided on the inlet side 3 in the fire deck into a cooling chamber 85 which at least partially surrounds the injector sleeve and reaches the second cooling chamber 82 via at least one overflow channel not visible in Fig. 6. The coolant then flows through the second cooling chamber 82 and the first cooling chamber 81 in the top-down cooling process already described and the injection device 7 is cooled via the cooling channels 816, 817 which branch off from the third web channel.

[0050] Cylinder head 1 is particularly suitable for combustion processes using hydrogen, ethanol or methane as fuel.

[0051] The arrangement and orientation of the ignition device 6 and the injection device 7 with intake valves 312, 322 and exhaust valves 412, 422 arranged "vertically"—that is, parallel to the cylinder axis 2a—enable the implementation of a tumble combustion process. The generation of the tumble charge motion is supported by a suitable geometry of the intake port arrangement 30 and asymmetric machining of the intake valve seats 311, 321. An asymmetric or one-sided chamfer 311a, 321a (see Fig. 7) is machined into the fire deck 10 of the cylinder head 1 on the side of each intake valve seat 311, 321 facing the exhaust side 4 in order to direct the flow from the intake side 3 to the exhaust side 4. As shown in Fig. 2 and Fig. 3, the inlet channels 31, 32 are formed in an arc and / or inclined with respect to the cylinder axis 2a so that a tumble charge movement directed towards the ignition location of the ignition device 6 is generated in the combustion chamber 5.

[0052] The tumble charge movement in combustion chamber 5 is further supported by pistons 9 with piston bowls 90, which have a so-called "pent roof shape." This piston bowl 90, shown in Figs. 8 to 11, leads to a timely disintegration of the tumble flow and conversion into turbulence before reaching the ignition point of the ignition device 6. This creates an optimal turbulence field around the centrally arranged ignition device 6.

Claims

PATENT CLAIMS Internal combustion engine with a top-down cooling concept, in particular with several cylinders (2), with a liquid-cooled cylinder head (1) with a first cooling chamber (81) bordering a fire deck (10) and a second cooling chamber (82), which is separated from the first cooling chamber (81) by an intermediate deck and which is predominantly further away from the fire deck (10) than the first cooling chamber (81), wherein the first cooling chamber (81) and the second cooling chamber (82) are fluidly connected to one another in the region of the ignition device (6), with an inlet channel arrangement (30) on an inlet side (3) and an outlet channel arrangement (40) on an outlet side (4) of the cylinder head (1), with two inlet valves (312, 322) per cylinder, two outlet valves (412, 422), an ignition device (6) opening centrally into a combustion chamber (5) and a lateral one into the Injection device (7) opening into the combustion chamber (5),which is arranged between a first inlet port (31) and a second inlet port (32) of the inlet port arrangement (30), characterized in that the first inlet port (31) and the second inlet port (32) of each cylinder (2) in the cylinder head (1) are guided separately from at least one lateral flange surface (33) of the cylinder head (1), and in that the injection device (7) is at least partially surrounded by a cooling chamber (85) that is fluidly connected to the second cooling chamber (82) or formed as part of the second cooling chamber (82). Internal combustion engine according to claim 1, characterized in that the cooling chamber (85) is connected to a cooling jacket of a cylinder block adjacent to the cylinder head (1) via at least one connecting channel (84) arranged in the fire deck (10) on the inlet side (3). Internal combustion engine according to claim 1 or 2, characterized inthat at least one first cylinder head screw (151) is arranged between the first intake port (31) and the injection device (7). Internal combustion engine according to one of claims 1 to 3, characterized in that at least one second cylinder head screw (152) is arranged between the second intake port (32) and the injection device (7). Internal combustion engine according to one of claims 1 to 4, characterized in that at least two adjacent intake ports (31, 32) of two adjacent cylinders (2) extend from a common flange surface (33). Internal combustion engine according to one of claims 1 to 5, characterized in that at least two adjacent intake ports (31, 32) of adjacent cylinders (2) are arranged directly on both sides of a transverse engine plane (11) extending between two adjacent cylinders (2). Internal combustion engine according to one of claims 1 to 6, characterized in that in at least one cylinder (2), the first intake port (31) and the second intake port (32) are spaced apart from one another as far as possible, wherein the maximum distance (A) between the two intake ports (31, 32) particularly preferably corresponds approximately to the bore diameter (D) of the cylinder (2).Internal combustion engine according to one of claims 1 to 7, characterized in that in the region of at least one transverse engine plane (11) between two adjacent cylinders (2) at least one third cylinder head screw is arranged, wherein preferably the third cylinder head screw (153) has a smaller distance (b) from a longitudinal engine plane (12) spanned by the cylinder axes (2a) than the first cylinder head screw (151) and / or the second cylinder head screw (152).Internal combustion engine according to one of claims 1 to 8, characterized in that the first cooling chamber (81) has at least one first cooling channel (816) arranged between the first inlet channel (31) and the injection device (7), and at least one second cooling channel (817) arranged between the second inlet channel (32) and the injection device (7), wherein the first cooling channel (816) and / or the second cooling channel (817) is / are preferably cast and at least partially surrounds the injection device (7). Internal combustion engine according to one of claims 1 to 9, characterized in that the inlet valves (312, 322) and / or exhaust valves (412, 422) are arranged parallel to the cylinder axis (2a) with a maximum deviation of ±5°. Internal combustion engine according to one of claims 1 to 10, characterized in that the injection device (7) opens into a combustion chamber (5) at an angle (o) of approximately 45° ±15° to the cylinder axis (2a).Internal combustion engine according to one of claims 1 to 11, characterized in that a distance (a) between the mouth (71) of the injection device (7) and the cylinder axis (2a) is 35% to 45% of a bore diameter (D) of the cylinder (2). Internal combustion engine according to one of claims 1 to 12, characterized in that at least one intake port (31, 32) - preferably both intake ports (31, 32) - is / are designed to generate tumble. Internal combustion engine according to claims 1 to 13, characterized in that at least one preferably asymmetrical chamfer (311a, 321a) is incorporated into the fire deck (10) of the cylinder head (1) on the side of at least one intake valve seat (311, 321) facing the exhaust side (4). Internal combustion engine according to one of claims 1 to 14, characterized in that the first intake port (31) and the second intake port (32) of at least one cylinder (2) are designed symmetrically to at least one transverse engine plane (11, 111). Internal combustion engine according to one of claims 1 to 15, characterized in that the longitudinal axis (7a) of the injection device (7) is arranged in a transverse engine plane (11) containing the cylinder axis (2a).Internal combustion engine according to one of claims 1 to 16, characterized in that at least one outlet channel (41, 42) is connected to the first cooling chamber. (81) and borders on the second cooling chamber (82), wherein the second cooling chamber (82) is arranged at least partially - preferably completely - on a side of the outlet channel (41, 42) facing away from the first cooling chamber (81). Internal combustion engine according to one of claims 1 to 17, characterized in that the first cooling chamber (81) in the region of the ignition device (6) is fluidly connected to the second cooling chamber (82) via at least one connecting channel (83) - preferably arranged on the outlet side (4) and / or the inlet side (3) - wherein the connecting channel (83) is preferably a cast channel. Internal combustion engine according to one of claims 1 to 18, characterized in that an ignition device sleeve (60) for receiving the ignition device (6) is arranged in the cylinder head (1), wherein the ignition device sleeve (60) is preferably designed to be wet and directly borders the first cooling chamber (81) and / or the second cooling chamber (82).Internal combustion engine according to one of claims 1 to 19, characterized in that an injector sleeve (70) for receiving the injection device (7) is arranged in the cylinder head (1), wherein the injector sleeve (70) is preferably designed to be wet and directly borders on the cooling chamber (85) and / or the second cooling space (82).

Images