Prechamber ignition unit
Patent Information
- Authority / Receiving Office
- WO · WO
- Patent Type
- Applications
- Current Assignee / Owner
- Filing Date
- 2026-02-04
- Publication Date
- 2026-08-13
Smart Images
Figure AT2026060028_13082026_PF_FP_ABST
Abstract
Description
[0001]
[0002] pre-chamber ignition unit
[0003] The invention relates to a pre-chamber ignition unit for an internal combustion engine, comprising a substantially hollow cylindrical housing for receiving an ignition device opening into a pre-chamber of the pre-chamber ignition unit, wherein at least one sealing and / or support ring is arranged in at least one sealing and / or support area of the pre-chamber ignition unit between the ignition device and the housing, and wherein the pre-chamber ignition unit has at least one residual gas reservoir – formed in particular by a jacketed space between the ignition device and the housing – which is fluidically connected to a pre-chamber of the pre-chamber ignition unit via at least one passage. The invention further relates to an internal combustion engine with at least one cylinder and such a pre-chamber ignition unit associated with the cylinder.From AT 526 244 A4, a spark-ignition internal combustion engine with an ignition unit is known. This unit has a passive pre-chamber connected to a main combustion chamber, into which an ignition device opens. The ignition unit has a radical storage volume that is either flow-connected to or integrated into the pre-chamber. The radical storage volume is formed by an annular space surrounding the ignition device between the cylinder head and the ignition device and is arranged axially spaced from the pre-chamber. The radical storage volume is flow-connected to the pre-chamber via one or more connecting channels.
[0004] AT 520 987 Bl describes a spark plug with an outer part and an inner part, wherein in a lower area of the transition from the outer part to the outside to a next element in the direction of a combustion chamber a concave or convex or conical shaped first seat surface is provided, which is designed for power transmission and heat transmission, wherein the inner part has a concave or convex or conical shaped second seat surface in relation to the outer part.
[0005] The sealing of the spark plugs in the component that receives the spark plug is usually achieved by means of, for example, a metallic sealing and / or support ring.
[0006] DE 10 2021 214 326 A1 discloses a spark plug with a first sealing and / or support ring having axial openings, wherein the axial openings serve to facilitate the assembly of the sealing and / or support ring on the spark plug. Furthermore, DE 284 71 36 A1 discloses a spark plug with a sealing and / or support ring which has a radial air guide bore in which a check valve is arranged that prevents radial outward flow but allows radial inward flow when the pressure of the combustion gases in the cylinder is lower than the ambient atmospheric pressure.
[0007] German patent DE 10 2022 134 984 describes a pre-chamber spark plug with an ignition unit opening into a pre-chamber, wherein a residual gas reservoir is formed between the ignition unit and a housing of the pre-chamber ignition unit in a region facing away from the pre-chamber. A seal is arranged between the ignition unit and the housing in a region adjacent to the residual gas reservoir. In a region facing the pre-chamber, the housing has a projection spaced apart from the outer surface of the insulator. Flow channels are formed between the projection and the insulator, creating passages for residual gas between the pre-chamber and the residual gas reservoir. The distance between the projections and the insulator thermally decouples the ignition unit and the housing.
[0008] A similar pre-chamber spark plug is known from DE 10 2023 135 834 A1. Overheated center electrodes of ignition devices are frequently the cause of irregular combustion phenomena such as pre-ignition in spark-ignition internal combustion engines.
[0009] The object of the invention is to reduce irregular combustion events in internal combustion engines.
[0010] According to the invention, the problem is solved with a pre-chamber ignition unit of the type mentioned above by arranging a first sealing and / or support ring in a first sealing and / or support area and a second sealing and / or support ring in a second sealing and / or support area between the ignition device and the housing, wherein the first sealing and / or support area and the second sealing and / or support area are axially spaced apart from each other with respect to the longitudinal axis of the ignition device, wherein preferably the first sealing and / or support area is arranged at an electrode-side first end of the insulator and the second sealing and / or support area is arranged at a second end of the insulator facing away from the first end, wherein at least the first sealing and / or support ring is arranged in the area of the transition and has at least one transition channel for the flow connection between the residual gas storage and the pre-chamber.
[0011] Because the preferably rigid first sealing and / or support ring has at least one transfer channel to the flow connection between the residual gas storage and the - in particular passive - pre-chamber, good gas exchange between the residual gas storage and the pre-chamber is enabled in a simple way.
[0012] The two sealing and / or support rings – especially the first sealing and / or support ring – ensure good heat transfer, thereby improving the thermal coupling of the ignition device and the housing and preventing irregular combustion phenomena as well as damage to the ignition device due to thermal overload.
[0013] To avoid static overdetermination, it is advantageous if the first sealing and / or support ring and the second sealing and / or support ring are designed with different stiffnesses and / or consist of materials with different moduli of elasticity, preferably the stiffness and / or the modulus of elasticity of the first sealing and / or support ring being greater than that of the second sealing and / or support ring.
[0014] One of the sealing and / or support rings is therefore flexible, and the other sealing and / or support ring is rigid, in order to prevent static overdetermination of a double fit. In particular, the second sealing and / or support ring can be flexible, and the first sealing and / or support ring can be rigid.
[0015] One embodiment of the invention provides that a first modulus of elasticity of the first sealing and / or support ring is greater than 120 GPa, preferably at least 130 GPa, and / or that a second modulus of elasticity of the second sealing and / or support ring is a maximum of 120 GPa, preferably a maximum of 115 GPa. Due to the temperature load, the use of a highly thermally conductive metallic material such as copper, aluminum, or an alloy thereof is advantageous. For example, the first sealing ring can be made of a copper-nickel-silicon-chromium alloy and the second sealing ring of copper.
[0016] Due to its higher stiffness, the first sealing and / or support ring also has the function of a support ring.
[0017] Preferably, the first sealing and / or support ring is essentially rotationally symmetrical with respect to a fictitious first axis of rotation of the first sealing and / or support ring, wherein, advantageously, the fictitious first axis of rotation is parallel or congruent with a fictitious second axis of rotation of the prechamber and / or the longitudinal axis of the ignition device in the assembled state. Preferably, the prechamber is designed as a passive prechamber. A passive prechamber is understood here to be a prechamber into which no fuel injection device opens. During the compression process, the residual gas is forced from the prechamber into the residual gas reservoir and temporarily stored. The residual gas components temporarily stored in the residual gas reservoir enter the prechamber with a delay during the power stroke, whereby pre-ignition of the mixture at the hot center electrode of the ignition device is prevented by heat absorption and charge dilution.Uniform heat absorption and charge dilution can be achieved if the first sealing and / or support ring has several transfer channels, which are preferably arranged evenly distributed around the fictitious first axis of rotation.
[0018] In one embodiment of the invention, it is provided that the at least one transfer channel has a cross-section with a closed profile line, wherein preferably the cross-section of the transfer channel is essentially elongated and has a width measured in a circumferential direction or in a tangential direction of the first sealing and / or support ring which is greater than a width measured in a radial direction of the first sealing and / or support ring.
[0019] In other words, the transfer channel has an elongated cross-section, with the cross-section of the transfer channel extending essentially in the circumferential direction with its longer sides.
[0020] The cross-section and number of transfer channels allow the cooling and retention behavior of the residual gas to be specifically influenced and optimized.
[0021] Preferably, the width of the cross-section of at least one transition channel corresponds to at least twice, preferably at least three times, and particularly preferably at least four times the width of the cross-section of the transition channel. Alternatively or additionally, it can be provided that the width of the cross-section of at least one transition channel has an angular extent of at least 10°, preferably at least 30°, and particularly preferably at least 40° about the fictitious first axis of rotation.
[0022] Particularly good results can be achieved if at least one transfer channel has a cross-section of at least 3 mm. 2 , in particular at least 4 mm 2 , wherein preferably the cross-section is a maximum of 7 mm 2, in particular a maximum of 6 mm 2 amounts.
[0023] To achieve good cooling of the central electrode during the return flow of residual gas from the residual gas storage into the pre-chamber, it is advantageous if at least one transfer channel has a channel axis which is inclined to the fictitious first axis of rotation of the first sealing and / or support ring, wherein preferably the angle of inclination between the channel axis and the fictitious first axis of rotation of the first sealing and / or support ring is between 30° and 60°, particularly preferably about 45° ±5°.
[0024] Advantageously, at least one transition channel extends between an outer surface and an inner surface of the support ring.
[0025] The first sealing and / or support ring transmits mechanical forces from the ignition device to the housing and ensures secure support of the ignition device. Thus, the first sealing and / or support ring also functions as a support ring. According to one embodiment of the invention, the first sealing and / or support ring has a first end face with a conical first seating surface facing the ignition device, wherein a conical bearing surface of the ignition device rests on the conical first seating surface. The first seating surface also enables centering and precise positioning of the ignition device within the housing.
[0026] Furthermore, for the secure anchoring of the ignition device, it is advantageous if the first sealing and / or support ring has a second end face facing away from the first end face, with a flat or conical second seating surface which rests on a flat or conical support surface of a circumferential shoulder of the housing. Heat is also dissipated into the housing via the second seating surface and the flat support surface.
[0027] Heat dissipation into the housing and further into the cylinder head that receives the housing can be improved if the first sealing and / or support ring has a heat dissipation surface, preferably formed by the outer surface of the casing and in particular cylindrical, which rests against a corresponding inner surface of the housing. Preferably, the corresponding inner surface is cylindrical. In addition, heat dissipation also occurs via the conical first seating surface and the conical or flat second seating surface.
[0028] In order to achieve rapid ignition of the mixture in the main combustion chamber after ignition by the ignition device, it is advantageous if the pre-chamber ignition unit has a nozzle cap connected to the housing - preferably detachably - or formed in one piece with it, with at least one nozzle channel - preferably with at least two nozzle channels.
[0029] Optimal combustion of the fuel-air mixture in the main combustion chamber can be achieved if at least one first nozzle axis of a first nozzle channel, together with a fictitious second axis of rotation of the pre-chamber, defines a first inlet angle, and at least one second nozzle axis of a second nozzle channel, together with the fictitious second axis of rotation of the pre-chamber, defines a second inlet angle, which differs from the first inlet angle. It is particularly advantageous if the second inlet angle is larger—preferably by at least 10°, and more preferably by at least 20°—than the first inlet angle.
[0030] In a further embodiment of the invention, the volume of the residual gas storage is adjustable, preferably by including at least one sleeve-like insert in the jacket space, and preferably by fixing the position of the insert in the jacket space by a shoulder – preferably formed by the housing. The sleeve-like insert reduces the volume of the residual gas storage. Thus, various sleeve-like inserts with different volumes can be used to optimize the remaining volume of the residual gas storage and, consequently, the effect on preventing pre-ignition.
[0031] To ensure efficient heat dissipation, it is advantageous for the pre-chamber ignition unit to have a threaded section in the first outer casing surrounding the pre-chamber and / or the ignition device. This threaded section is designed for screwing onto a cylinder head, and preferably a second outer casing section adjoining the first, but facing away from the pre-chamber, is unthreaded. It is advantageously provided that the second axial extent of the second outer casing section, relative to the hypothetical second axis of rotation of the pre-chamber, is 10% to 90%, preferably 20% to 70%, and particularly preferably 30% to 50% of the first axial extent of the first outer casing section. This ensures concentrated heat dissipation in the first outer casing section.
[0032] The problem is further solved by an internal combustion engine with at least one cylinder and a pre-chamber ignition unit of the type described associated with the cylinder, in that a first sealing and / or support ring is arranged between the ignition device and the housing in a first sealing and / or support area and a second sealing and / or support ring is arranged in a second sealing and / or support area, wherein the first sealing and / or support area and the second sealing and / or support area are axially spaced apart from each other with respect to the longitudinal axis of the ignition device.
[0033] Preferably, the pre-chamber of the pre-chamber ignition unit opens into the main combustion chamber via at least one nozzle channel - preferably via at least two nozzle channels.To achieve optimal combustion of the fuel-air mixture, it is advantageous if the internal combustion engine, in particular its cylinder head, has an intake side and an exhaust side, wherein at least one first nozzle channel directed towards the intake side opens into the combustion chamber at a first entry angle and at least one second nozzle channel directed towards the exhaust side opens into the combustion chamber at a second entry angle different from the first entry angle, wherein the first entry angle is defined by a first nozzle axis of the first nozzle channel and the fictitious second axis of rotation of the pre-chamber and the second entry angle is defined by a second nozzle axis of the second nozzle channel and the fictitious second axis of rotation of the pre-chamber, wherein preferably the second entry angle is larger than the first entry angle - in particular by at least 10°, especially preferably by at least 20°.According to one embodiment of the invention, the pre-chamber ignition unit is arranged in the region of a cylinder axis of the cylinder, wherein preferably a fictitious second axis of rotation of the pre-chamber is formed parallel to the cylinder axis or coincides with the cylinder axis.
[0034] In a further embodiment of the invention, the pre-chamber ignition unit is screwed to the cylinder head via a thread arranged in the housing in a first jacket section surrounding the pre-chamber and / or the ignition device. Preferably, a second jacket section adjoining the first jacket section and facing away from the pre-chamber is open to the cylinder head and unthreaded. Thus, for example, one-quarter to one-third of the entire jacket section surrounding the pre-chamber has no thread. The axial extent of the second jacket section forming the open area, relative to the fictitious second axis of rotation of the pre-chamber, is particularly 10% to 90%, preferably 20% to 70%, and most preferably 30% to 50% of the axial extent of the first jacket section. This open area facilitates heat dissipation in the first jacket section.
[0035] The invention will be explained in more detail below with reference to the non-limiting embodiment shown in the figures. These schematically show:
[0036] Fig. 1 shows an internal combustion engine according to the invention in an axonometric representation;
[0037] Fig. 2a shows a pre-chamber ignition unit according to the invention in a first embodiment variant in a longitudinal section;
[0038] Fig. 2b shows a pre-chamber ignition unit according to the invention in a second embodiment in a longitudinal section; Fig. 3 shows a first sealing and / or support ring of this pre-chamber ignition unit in an axonometric view;
[0039] Fig. 4 shows the first sealing and / or support ring in a top view;
[0040] Fig. 5 shows the first sealing and / or support ring in a section along line VV in Fig. 4; and
[0041] Fig. 6 shows the first sealing and / or support ring in a section along line VI - VI in Fig. 4.
[0042] Fig. 1 shows an internal combustion engine 1 according to the invention, comprising several cylinders 2, a cylinder block 3, and a cylinder head 4 connected to the cylinder block 3. A reciprocating or up-and-down piston 5 is arranged in each cylinder 2 and acts on a crankshaft (not shown) via a connecting rod (not shown). A main combustion chamber 7 is formed in each cylinder 3 between the piston 5 and a combustion chamber cover surface 6 (e.g., roof-shaped) formed by the cylinder head 4.
[0043] In the embodiments shown in Figures 2a and 2b, a pre-chamber ignition unit 10, opening into the main combustion chamber 7, is arranged in the cylinder head 4 for each cylinder 2 in the region of a cylinder axis 2a. The pre-chamber ignition unit 10 is inserted into a bore (not shown) in the cylinder head 4 of the internal combustion engine 1 and is firmly anchored in the cylinder head 4, for example, screwed into a thread of the bore. The pre-chamber ignition unit 10 according to the invention essentially has a hollow cylindrical, rotationally symmetrical housing 11 with an ignition device 14 comprising at least one insulator 12 and a central electrode 13, which opens into a pre-chamber 15, for example, a passive one. The pre-chamber 15 is formed at least partially by the housing 11. Reference numeral 16 designates ground electrodes inserted through radial openings in the housing 11.
[0044] The pre-chamber ignition unit 10 is screwed to the cylinder head 4 via a thread 40 arranged in the housing 11 within a first jacket section 111, which surrounds the pre-chamber 15 and / or the ignition device 14 and faces the main combustion chamber 7. A second jacket section 112, facing away from the first jacket section 111 and the pre-chamber 15, is freestanding and unthreaded relative to the cylinder head 4. The second axial extent e2 of the second jacket section 112, which forms the freestanding area, is, for example, 10% to 90%, and in particular 30% to 50%, of the first axial extent el of the first jacket section 11. This ensures that heat dissipation into the cylinder head 4 occurs primarily via the first jacket section 111.
[0045] Between the ignition device 14 and the housing 11, a first sealing and / or support ring 30 is arranged in a first sealing and / or support area 300, and a second sealing and / or support ring 17 is arranged in a second sealing and / or support area 170. The first sealing and / or support area 300 and the second sealing and / or support area 170 are axially spaced apart from each other with respect to the longitudinal axis 14a of the ignition device. The first sealing and / or support area 300 is arranged in a first section 141 of the ignition device 14 facing the pre-chamber 15, and the second sealing and / or support area 170 is arranged in a second section 142 of the ignition device 14 facing away from the pre-chamber 15. The second section 142 is located adjacent to a mounting area 140 of the ignition device 14. In the mounting area 140, the ignition device 14 is firmly connected to the housing 11 by means of a nut 110 screwed to the housing 11.
[0046] The second sealing and / or support ring 17, located in the second sealing and / or support area 170 of the pre-chamber ignition unit 10, facing away from the pre-chamber 15 and between the ignition device 14 and the housing 11, seals the insulator 12 against the housing 11. The second sealing and / or support ring 17 is positioned between a conical sealing surface 18 of a shoulder 19 of the housing 11 and a conical or concave sealing surface 20 of the insulator 12. The insulator 12 of the ignition device 14 is detachably connected to the housing 11 by means of a clamping nut (not shown) that engages the thread 21.
[0047] A jacketed chamber 22 extends between the ignition device 14 and the housing 11, forming a residual gas reservoir 23. The volume of the residual gas reservoir 23 is determined by at least one sleeve-like insert 24 inserted into the jacketed chamber 22. By selecting inserts 24 of different lengths, the volume of the residual gas reservoir 23 can be optimized to meet specific requirements. In the embodiment shown in Fig. 2a, the jacketed chamber 22 can also be omitted. The sleeve-like insert 24 can be extended to the first sealing and / or support ring 30 – leaving a defined gap – to allow for stress-free thermal expansion. The residual gas reservoir 23 can be flow-connected to the pre-chamber 15 of the pre-chamber ignition unit 10 via at least one passage 25.
[0048] A first sealing and / or support ring 30 is arranged between a contact surface 29 of the ignition device 14 and the housing 11 in the area of the transition 25. The first sealing and / or support ring 30 is essentially rotationally symmetrical with respect to a fictitious first axis of rotation 30a of the first sealing and / or support ring 30. The fictitious first axis of rotation 30a of the first sealing and / or support ring 30 is parallel or coincident with a fictitious second axis of rotation 15a of the prechamber 15.
[0049] In the embodiment shown in Fig. 2a, the first sealing and / or support ring 30 is designed without a transfer channel 31.
[0050] In the embodiment shown in Fig. 2b, transfer channels 31 are formed in the first sealing and / or support ring 30, which form the transfers 25 between the pre-chamber 15 and the residual gas storage 23.
[0051] In each of the illustrated embodiments, the pre-chamber ignition unit 10 has a nozzle cap 26 which is detachably connected to the housing 11, for example, and has at least two nozzle channels 27, 28 opening into the main combustion chamber 7.
[0052] The internal combustion engine 1 has an intake side E and an exhaust side A, wherein the intake valve openings (not shown) and the intake valves are located on the intake side E, and the exhaust valve openings (not shown) and the exhaust valves are located on the exhaust side A in the cylinder head 4. At least one first nozzle axis 27a of a first nozzle channel 27 directed towards the intake side E of the internal combustion engine 1 forms a first inlet angle θ with the fictitious second axis of rotation 15a of the prechamber 15. At least one second nozzle axis 28a of a second nozzle channel 28 directed towards the exhaust side A of the internal combustion engine 1 forms a second inlet angle β with the fictitious second axis of rotation 15a of the prechamber 15. The second inlet angle β is configured differently from the first inlet angle θ and is, for example, at least 20° larger than the first inlet angle θ.
[0053] The first sealing and / or support ring 30 is shown in detail in Figures 3 to 6. The first sealing and / or support ring 30 has several transfer channels 31 arranged evenly around the fictitious first axis of rotation 30a for the flow connection between the residual gas storage 23 and the pre-chamber 15, which extend between an outer shell surface 32 and an inner shell surface 33 of the first sealing and / or support ring 30.
[0054] Each transition channel 31 has a cross-section with a closed profile line 31b. The cross-section of the transition channel 31 is essentially elongated and has a width W, measured in a circumferential or tangential direction to the first sealing and / or support ring 30, which is greater than a width B measured in a normal plane to the channel axis 31a of the transition channel 31. The width W of the cross-section of the transition channel 31, as shown in Fig. 4, is at least four times larger in the example shown than the width B of the cross-section of the transition channel 31, as shown in Fig. 5.
[0055] In the illustrated embodiment, the width W of the cross-section of each transfer channel 31 has an angular extent y of approximately 40° around the fictitious first axis of rotation 30a, measured in the circumferential direction of the first sealing and / or support ring 30, as can be seen in Fig. 4.
[0056] In the tests carried out, cross-sectional areas of the transition channels 31 of, for example, 4 mm² were achieved. 2 or 6 mm 2 Excellent results in terms of preventing pre-ignition.
[0057] Each transition channel 31 has a channel axis 31a inclined to the fictitious first axis of rotation 30a of the first sealing and / or support ring 30. The angle of inclination θ between the channel axis and the fictitious first axis of rotation of the first sealing and / or support ring 30, shown in Fig. 5, is approximately 45° in the illustrated embodiment.
[0058] The first sealing and / or support ring 30 has a first seating surface 35 on a first end face 34 facing the ignition device 14, the shape and arrangement of which correspond to the bearing surface 29 of the ignition device 14. The bearing surface 29 of the ignition device 14, for example, which is conical, rests on the first seating surface 35, for example, which is conical, and thus supports the ignition device 14 against the first sealing and / or support ring 30.
[0059] The first sealing and / or support ring 30 has a second end face 36 facing away from the first end face 34, with a second seating surface 37 that is, for example, flat and rests on a corresponding support surface 9 of a circumferential shoulder 8 of the housing 11. The support forces between the housing 11 and the first sealing and / or support ring 30 are transferred via the second seating surface 37, and heat is dissipated from the first sealing and / or support ring 30 into the housing 11.
[0060] For further heat dissipation, the, for example, cylindrical outer shell surface 32 of the first sealing and / or support ring 30 is designed as a heat dissipation surface, which rests against, for example, a cylindrical corresponding inner surface 110 of the housing 11 and thus thermally contacts it.
[0061] The thickness d of the first sealing and / or support ring 30 is, for example, a maximum of 1 / 3 of the diameter D of the first sealing and / or support ring 30 (Fig. 6).
Claims
P AT E N T A N S P R Ü C H E 1. Prechamber ignition unit (10) for an internal combustion engine (1), comprising a substantially hollow cylindrical housing (11) for receiving an ignition device (14) opening into a prechamber (15) of the prechamber ignition unit (10), wherein at least one sealing and / or support ring (30, 17) is arranged in at least one sealing and / or support area (300, 170) of the prechamber ignition unit (10) between the ignition device (14) and the housing (11), wherein the prechamber ignition unit (10) has at least one residual gas reservoir (23) – formed in particular by a jacketed space (22) between the ignition device (14) and the housing (11) – which is connected to a prechamber (15) of the prechamber ignition unit (10) via at least one passage (25), characterized in thatthat a first sealing and / or support ring (30) in a first sealing and / or support area (300) and a second sealing and / or support ring (17) in a second sealing and / or support area (170) are arranged between the ignition device (14) and the housing (11), wherein the first sealing and / or support area (300) and the second sealing and / or support area (170) are axially separated from each other with respect to a longitudinal axis (14a) of the ignition device, wherein preferably the first sealing and / or support area (300) is arranged in a first section (141) of the ignition device (14) facing the pre-chamber (15) and the second sealing and / or support area (170) is arranged in a second section (142) of the ignition device (14) facing away from the pre-chamber (15),wherein at least the first sealing and / or support ring (30) is arranged in the area of the transition (25) and has at least one transition channel (31) for the flow connection between the residual gas storage (23) and the pre-chamber (15).
2. Pre-chamber ignition unit (10) according to claim 1, characterized in that the first sealing and / or support ring (30) and the second sealing and / or support ring (17) are designed with different stiffness and / or made of materials with different moduli of elasticity, wherein preferably the stiffness and / or the modulus of elasticity of the first sealing and / or support ring (30) is greater than that of the second sealing and / or support ring (17).
3. Pre-chamber ignition unit (10) according to claim 2, characterized in that a first modulus of elasticity of the first sealing and / or support ring (30) is greater than 120 GPa, preferably at least 130 GPa.
4. Prechamber ignition unit (10) according to claim 2 or 3, characterized in that a second modulus of elasticity of the second sealing and / or support ring (17) is a maximum of 120 GPa, preferably a maximum of 115 GPa.
5. Prechamber ignition unit (10) according to one of claims 1 to 4, characterized in that the first sealing and / or support ring (30) is formed in a substantially rotationally symmetrical manner with respect to a fictitious first axis of rotation (30a) of the first sealing and / or support ring (30), wherein preferably the fictitious first axis of rotation (30a) is formed in the assembled state parallel or coincident with a fictitious second axis of rotation (15a) of the prechamber (15) and / or the longitudinal axis (14a) of the ignition device.
6. Pre-chamber ignition unit (10) according to one of claims 1 to 5, characterized in that the first sealing and / or support ring (30) has several transfer channels (31) which are preferably arranged evenly distributed around the fictitious first axis of rotation (30a) of the first sealing and / or support ring (30).
7. Pre-chamber ignition unit (10) according to one of claims 1 to 6, characterized in that the at least one transfer channel (31) has a cross-section with a closed profile line (31b), wherein preferably the cross-section of the transfer channel (31) is substantially elongated and has a width (W) measured in a circumferential direction or in a tangential direction of the first sealing and / or support ring (30) which is larger than a width (B) measured in a radial direction of the first sealing and / or support ring (30).
8. Prechamber ignition unit (10) according to claim 7, characterized in that the width (W) of the cross-section of at least one transfer channel (31) corresponds at least twice, preferably at least three times, particularly preferably at least four times the width (B) of the cross-section of the transfer channel (31).
9. Pre-chamber ignition unit (10) according to claim 7 or 8, characterized in that the width (W) of the cross-section of at least one transfer channel (31) has an angular extent (y) of at least 10°, preferably at least 30°, particularly preferably at least 40° about the fictitious first axis of rotation (30a) of the first sealing and / or support ring (30).
10. Pre-chamber ignition unit (10) according to one of claims 1 to 9, characterized in that at least one transfer channel (31) has a cross-section which is at least 3 mm 2 , in particular at least 4 mm 2 , wherein preferably the cross-section is a maximum of 7 mm 2, in particular a maximum of 6 mm 2 amounts.
11. Pre-chamber ignition unit (10) according to one of claims 1 to 10, characterized in that at least one transfer channel (31) has a channel axis (31a) which is inclined to the fictitious first axis of rotation (30a) of the first sealing and / or support ring (30), wherein preferably the angle of inclination (θ) between the channel axis (31a) and the fictitious first axis of rotation (30a) of the first sealing and / or support ring (30) is between 30° and 60°, particularly preferably about 45° ±5°.
12. Pre-chamber ignition unit (10) according to one of claims 1 to 11, characterized in that at least one transfer channel (31) extends between an outer shell surface (32) and an inner shell surface (31) of the first sealing and / or support ring (30).
13. Pre-chamber ignition unit (10) according to one of claims 1 to 12, characterized in that the first sealing and / or support ring (30) has a first end face (34) with a conical first seating surface (35) facing the ignition device (14), wherein a conical bearing surface (29) of the ignition device (14) rests on the conical first seating surface (35).
14. Pre-chamber ignition unit (10) according to claim 13, characterized in that the first sealing and / or support ring (30) has a second end face (36) facing away from the first end face (34) with a second seating surface (37) which is in particular flat or conical and rests on a support surface (9) of a circumferential shoulder (8) of the housing (11) which is in particular flat or conical.
15. Pre-chamber ignition unit (10) according to one of claims 1 to 14, characterized in that the first sealing and / or support ring (30) has a preferably cylindrical heat dissipation surface formed by the outer shell surface (32), which abuts a corresponding inner surface (110) of the housing (11).
16. Pre-chamber ignition unit (10) according to one of claims 1 to 15, characterized in that the pre-chamber ignition unit (10) has a nozzle cap (26) connected to the housing (11) - preferably detachably - or formed integrally with it, with at least one nozzle channel (27; 28) - preferably with at least two nozzle channels (27, 28).
17. Prechamber ignition unit (10) according to claim 16, characterized in that at least a first nozzle axis (27a) of a first nozzle channel (27) with a fictitious second axis of rotation (15a) of the prechamber (15) defines a first inlet angle (o) and at least a second nozzle axis (28a) of a second nozzle channel (28) with the fictitious second axis of rotation (15a) of the prechamber (15) defines a second inlet angle (β), which is preferably different from the first inlet angle (o).
18. Prechamber ignition unit (10) according to claim 17, characterized in that the second inlet angle (β) is larger – preferably by at least 10°, particularly preferably by at least 20° – than the first inlet angle (o).
19. Pre-chamber ignition unit (10) according to one of claims 1 to 18, characterized in that the volume of the residual gas storage (23) is variable, wherein preferably at least one, in particular sleeve-like, insert (24) can be inserted into the jacket space (22), wherein the position of the insert (24) in the jacket space (22) is particularly preferably fixed by a shoulder - preferably formed by the housing (11).
20. Internal combustion engine (1) according to one of claims 1 to 19, characterized in that the pre-chamber ignition unit (10) has a thread (40) in a first jacket area (111) of the housing (11) surrounding the pre-chamber (15) and / or the ignition device (14), which is designed to be screwed to a cylinder head (4), wherein preferably a second jacket area (112) adjoining the first jacket area (111) and facing away from the pre-chamber (15) is designed without threads.
21. Prechamber ignition unit (10) according to claim 20, characterized in that a second axial extent (e2) of the second jacket area (112) forming the clearance, relating to the fictitious second axis of rotation (15a) of the prechamber (15), is 10% to 90%, preferably 20% to 70%, particularly preferably 30% to 50% of a first axial extent (el) of the first jacket area (11).
22. Internal combustion engine (1) with at least one cylinder (2) with a pre-chamber ignition unit (10) associated with the cylinder (2), according to one of claims 1 to 21, characterized in that a first sealing and / or support ring (30) in a first sealing and / or support area and a second sealing and / or support ring (17) in a second sealing and / or support area are arranged between the ignition device (14) and the housing (11), wherein the first sealing and / or support area and the second sealing and / or support area are axially spaced apart from each other with respect to the longitudinal axis (14a) of the ignition device.
23. Internal combustion engine (1) according to claim 22, characterized in that the pre-chamber (15) of the pre-chamber ignition unit (10) opens into the main combustion chamber (7) via at least one nozzle channel (27; 28) – preferably via at least two nozzle channels (27, 28).
24. Internal combustion engine (1) according to claim 23, characterized in that the internal combustion engine (1) has an inlet side (E) and an outlet side (A), wherein at least one first nozzle channel (27) directed towards the inlet side (E) opens into the main combustion chamber (7) at a first inlet angle (o) and at least one second nozzle channel (28) directed towards the outlet side (A) opens into the main combustion chamber (7) at a second inlet angle (β) different from the first inlet angle (o).wherein the first inlet angle (o) is defined by a first nozzle axis (27a) of the first nozzle channel (27) and the fictitious second axis of rotation (15a) of the prechamber (15) and the second inlet angle (β) is defined by a second nozzle axis (28a) of the second nozzle channel (28) and the fictitious second axis of rotation (15a) of the prechamber (15), wherein preferably the second inlet angle (β) is larger than the first inlet angle (o) - in particular by at least 10°, especially preferably by at least 20°.
25. Internal combustion engine (1) according to one of claims 22 to 24, characterized in that the pre-chamber ignition unit (10) is arranged in the region of a cylinder axis (2a) of the cylinder (2), wherein preferably a fictitious second axis of rotation (15a) of the pre-chamber (15) is formed parallel to the cylinder axis (2a) or coincides with the cylinder axis (2a).
26. Internal combustion engine (1) according to one of claims 22 to 25, characterized in that the pre-chamber ignition unit (10) is screwed to the cylinder head in a first jacket area (111) surrounding the pre-chamber (15) and / or the ignition device (14) via a thread (40) arranged in the housing (11), wherein preferably a second jacket area (112) adjoining the first jacket area (111) and facing away from the pre-chamber (15) is free from the cylinder head (4) and is designed without threads.
27. Internal combustion engine (1) according to claim 26, characterized in that the second axial extent (e2) of the second shell area (112) forming the clearance, which is related to the fictitious second axis of rotation (15a) of the pre-chamber (15), is 10% to 90%, preferably 20% to 70%, particularly preferably 30% to 50% of the first axial extent (el) of the first shell area (11). 2026 02 04 FU