Crankcase for an internal combustion engine, internal combustion engine

Description

[0001] The invention relates to a crankcase with at least one cylinder for an internal combustion engine, wherein the cylinder further comprises: a cylinder liner arranged within a cylinder interior, and a cylinder head closing the cylinder interior, wherein the cylinder head has a receiving means and a cooling system with a cooling chamber that guides a coolant flow. The invention also relates to an internal combustion engine according to claim 12. A receiving means can in particular be formed as a receiving sleeve or receiving bushing or the like comprising and / or guiding a receiving means for a device or component extending into the cylinder, in particular for an injector or an ignition device.

[0002] Crankcases for internal combustion engines, especially those with cooling systems, are well known.

[0003] For example, AT005939U1 describes a cylinder head for a liquid-cooled internal combustion engine, with a cooling chamber arrangement adjacent to a fire deck, which is divided by an intermediate deck formed substantially parallel to the fire deck into a lower partial cooling chamber on the fire deck side and an upper partial cooling chamber adjoining this in the direction of the cylinder axis, wherein the lower and upper partial cooling chambers are fluidly connected by at least one overflow opening.

[0004] Alternative crankcases and engines are known from WO2008122544, DE102015014514 or CN106988851.

[0005] However, these approaches still require improvement, especially with regard to efficient cooling. This efficiency refers in particular to relatively high cooling performance with relatively low equipment costs. Equipment costs refer in particular to the weight, installation space, and / or cost of the cooling device.

[0006] This is where the invention comes in, its object being to remedy at least one of the aforementioned disadvantages. In particular, it is intended to enable efficient cooling of a cylinder arranged in a crankcase.

[0007] This object is achieved by a motor according to claim 1.

[0008] The invention is based on a crankcase with a number of at least one cylinder, for an internal combustion engine, wherein the cylinder further comprises: a cylinder liner arranged within a cylinder interior, and a cylinder head closing the cylinder interior, wherein the cylinder head has a receiving means, in particular a receiving sleeve or receiving bush or the like comprising and / or guiding receiving means for a device or component extending into the cylinder, in particular for an injector or an ignition device, and a cooling system with a cooling chamber guiding a coolant flow.

[0009] According to the invention, the crankcase a distribution system arranged in the crankcase for dividing the coolant flow into a primary partial flow and at least one secondary partial flow, wherein a main channel is provided for the primary partial flow and a branch passage is provided in the crankcase for the secondary partial flow, said branch passage being arranged transversely to the main channel and leading from the main channel.

[0010] In this context, a "branch passage extending transversely to the main channel" refers in particular to an arrangement of the at least one branch passage relative to the orientation of the main channel that significantly changes the flow direction of the coolant flow, in particular a perpendicular arrangement of the at least one branch passage relative to the orientation of the main channel. An ignition device can be designed, in particular, as a spark plug.

[0011] The invention is based on the realization that more efficient cooling of a cylinder in a crankcase represents a significant improvement in an internal combustion engine.

[0012] The invention recognizes that an even higher cooling performance can be achieved with an existing coolant flow if, on the one hand, it is applied to the cylinder in accordance with the cooling requirements and, on the other hand, is distributed appropriately. The invention recognizes that certain regions of the cylinder are exposed to particularly high heat generation and thus have a higher cooling requirement compared to other regions. Such regions with increased cooling requirements include, in particular, the flame deck of the cylinder head and the so-called top liner area, i.e., the upper area of ​​the cylinder liner facing the cylinder head.

[0013] Cooling efficiency is increased by dividing the coolant flow according to cooling requirements. For this purpose, the crankcase has a distribution system for dividing the coolant flow into a primary sub-flow and at least one secondary sub-flow. This allows for the creation of different cooling circuits with different coolant quantities, particularly coolant mass flows, each adapted to an individual cooling requirement.

[0014] The distribution system is designed to guide the primary partial flow through a main channel and to branch off the at least one secondary partial flow via a branch passage arranged transversely to the main channel and extending from the main channel, in particular to supply the secondary partial flow to a cooling zone of the cylinder liner for cooling purposes. The distribution system can be incorporated into the crankcase as a system of bores and channels.

[0015] In particular, the at least one secondary partial flow can be used to specifically supply one or more individual regions of the cylinder liner separately via one or more cooling zones.

[0016] Overall, improved cooling can lead to several advantages. Firstly, this concerns the possibility of carrying out combustion within the cylinder with increased energy conversion due to the higher cooling capacity, resulting in increased performance while maintaining the same installation space. Alternatively or additionally, due to the improved cooling capacity, a lighter and / or more cost-effective material can be advantageously used to manufacture the cylinder head, resulting in weight and / or cost advantages in the manufacture of the engine. Overall, the inhomogeneous deformation of the cylinder and in particular of the cylinder liner is reduced due to the improved cooling, as is the overall thermally induced deformation, thereby improving the interaction between the cylinder liner and the parts moving within the cylinder liner, in particular the piston and piston rings.

[0017] The invention also solves the problem by applying it to an internal combustion engine with a motor, wherein the motor has a crankcase according to the concept of the invention. The advantages of the crankcase are advantageously utilized in the internal combustion engine.

[0018] Advantageous further developments of the invention can be found in the dependent claims and specify in detail advantageous possibilities for realizing the concept explained above within the scope of the task and with regard to further advantages.

[0019] According to the invention, the distribution system supplies the at least one secondary partial flow to a top liner region of the cylinder liner located closer to the cylinder head and the primary partial flow to a remaining region of the cylinder liner located further away from the cylinder head. Since higher temperatures are expected to occur in the top liner region than in the remaining region of the cylinder liner, it is particularly advantageous to divide the coolant flow and specifically supply the regions subject to greater mechanical and / or thermal stress, in particular the top liner region. Depending on requirements, the distribution system can be designed and / or adjusted such that a sufficient amount of coolant is supplied to the top liner region via the at least one secondary partial flow, in particular compared to the remaining region of the cylinder liner.According to the invention, the cooling system comprises a supply passage for supplying the coolant flow along the receiving means, in particular a receiving sleeve or receiving bushing or similarly comprising and / or guiding receiving means for a device or component extending into the cylinder, in particular for an injector or an ignition device, to a flame deck of the cylinder head in such a way that an impingement flow is created on the flame deck. This further development preferably comprises a substantially parallel orientation of the flow of the coolant flow along the flame deck, in particular more specifically a change in the flow direction. This further development utilizes the advantage that the cooling performance is particularly high when the coolant flow is guided substantially parallel to the surface of the flame deck and thus substantially in a radial orientation.It is therefore the impingement flow, i.e. the conversion of the essentially axial flow direction into an essentially radial flow direction of the coolant flow, that advantageously improves the cooling performance. This is achieved by the supply passage for supplying the coolant flow along the receiving means, in particular a receiving sleeve or receiving bushing or similarly comprising and / or guiding receiving means for a device or component extending into the cylinder, in particular for an injector or an ignition device, being designed on the flame deck in such a way that an impingement flow is created on the flame deck.

[0020] Such impingement flow creates high, near-wall flow velocities. These high, near-wall flow velocities increase heat transfer, thereby improving heat dissipation from the cylinder and, in particular, from the flame deck. This advantageously reduces the requirements for the material used to manufacture the cylinder head. For example, due to improved cooling of the cylinder head, combustion in the cylinder can be carried out with increased energy conversion, which leads to increased engine performance. Alternatively or additionally, the lower maximum temperatures in the cylinder head allow a more cost-effective and / or lighter material to be used for the cylinder head during production.

[0021] According to the invention, it is further provided that the branch passage is fluid-conductingly connected to a top liner region of the cylinder liner. In concrete terms, this can involve different cooling zones being formed within the top liner region, each of which is supplied by a secondary partial flow. In this way, even within the top liner region, different regions of the top liner region can advantageously be supplied with cooling in accordance with their cooling requirements. In further developments, for example, an annular arrangement of cooling zones, for example four cooling zones, can be provided within the cylinder liner, wherein in particular a cooling zone located further towards the cylinder head has a higher cooling capacity than a cooling zone located further away from the cylinder head. In this way, a spatially precise and needs-based distribution of the cooling capacity within the top liner region can be achieved.

[0022] In a further development, the distribution system comprises a number of distribution sections, each of which is fluidically connected to a branch passage. In this way, a respective secondary partial flow can be branched off in a distribution section for a cooling zone assigned to that distribution section.

[0023] It is preferably further provided that a distribution section has a cross-section that is smaller than the cross-section of a distribution section arranged upstream in a flow direction of the coolant flow. In particular, a number of cylindrically shaped distribution sections can be arranged concentrically on a distributor axis of the distribution system and axially adjacent. A respective cooling zone is fluid-conductingly connected to the distribution section via a branch passage running transversely, in particular perpendicularly, to the distributor axis. Due to the cross-sections of the distribution sections decreasing in the flow direction, stepped shoulders are thus created. At such a stepped shoulder of a distribution section, the flow of the coolant flow is deflected from its movement along the distributor axis, in particular throttled and / or swirled.As a result, the geometric design influences the amount of fluid, so that the step acts as a resistance in the coolant flow. The portion of the coolant flow deflected in a distribution section can thus advantageously flow as a secondary partial flow into the cooling zone assigned to this distribution section. The greater the cross-sectional difference between a specific distribution section and a distribution section downstream in the flow direction, the greater the resistance and thus the deflected secondary partial flow and, accordingly, the cooling performance in the cooling zone assigned to this specific distribution section. The portion of the coolant flow that is still present in the main channel at the end of the distribution system, i.e. the remaining primary partial flow, can finally be fed via a residual passage to a remaining area of ​​the cylinder liner for cooling purposes.In this way, the cooling capacity for a cooling zone can be advantageously determined by designing the cross-sectional area of ​​a distribution section. The stepped geometry described here is advantageous for ensuring a uniform supply to all cooling zones connected to the distribution system. With a distribution system geometry without such a stepped shape, the coolant flow could largely bypass the branch passages due to its flow dynamics and only be deflected at the end of the distribution system or when encountering obstacles. This could lead to an uneven distribution of the cooling capacity.

[0024] Preferably, the cross-section is further provided to be round. A round cross-sectional area of ​​a distribution section can be produced with relatively little manufacturing effort, for example, by drilling or milling, since only one machining step is required due to the concentric cross-sections along the drilling axis (Christmas tree drilling).

[0025] According to the invention, the distribution system is arranged behind the cylinder head in the flow direction. This includes, in particular, that the coolant flow is first directed in the cooling chamber of the cylinder head in an impingement flow onto the flame deck and is then divided into a primary partial flow and at least one secondary partial flow by means of a distribution system for the purpose of cooling the cylinder liner. In such a serial arrangement of the cooling water supply, the entire coolant flow can initially be used to cool the cylinder head (and in particular the flame deck), and then the (already warmed) coolant flow can be used to cool the cylinder liner. During cooling of the cylinder liner by the distribution system, a further division can be made, in particular between the top liner area and the remaining area.Thus, prioritization can be done in the (descending) order: cylinder head - top liner area - remaining area.

[0026] It is further preferably provided that the distribution system or a branch is arranged upstream of the cylinder head in the flow direction. This includes, in particular, that the coolant flow is divided upstream of the cylinder head in the flow direction, and a partial flow, in particular the secondary partial flow, is fed to the top liner area of ​​the cylinder liner. Another partial flow, in particular the primary partial flow, is, however, first fed to the cylinder head – and in particular to the flame deck – and subsequently to the remaining area of ​​the cylinder liner. In such a parallel arrangement of the cooling water supply, cooling the top liner area is given higher priority compared to the serial arrangement. This is particularly the case since cooling takes place with coolant that has not yet been used to cool the cylinder head.Furthermore, the lower pressure losses in parallel arrangement have a further positive effect on the overall performance of the system.

[0027] In particular, it is provided that the supply passage, both in a parallel and a serial arrangement, is arranged concentrically around the receiving means. A receiving means can be formed, in particular, as a receiving means comprising and / or guiding a receiving sleeve or bushing or the like for a device or component extending into the cylinder, in particular for an injector or an ignition device. This results in the coolant flow flowing around the receiving means, thus cooling it evenly along its outer circumference.

[0028] In particular, it is further provided that the supply passage and the receiving means, in particular a receiving sleeve or receiving bushing or similar comprising and / or guiding receiving means for a device or component extending into the cylinder, together form a nozzle with an annular cross-section. Such a nozzle shapes the coolant flow, in particular, into a free jet, which transforms into an impingement flow upon impact with the flame deck. Such a transformation leads, in particular, to a change from a substantially axial direction of movement of the coolant flow along the main axis to a substantially radial direction of movement of the coolant flow along the surface of the flame deck.

[0029] Embodiments of the invention will now be described below with reference to the drawings in comparison to the prior art, some of which are also shown. These are not necessarily intended to represent the embodiments to scale; rather, where useful for explanation, the drawings are schematic and / or slightly distorted. With regard to supplementing the teachings immediately apparent from the drawings, reference is made to the relevant prior art. For specified design ranges, values ​​within the stated limits are also intended to be disclosed as limit values ​​and can be used and claimed as required. Further advantages, features, and details of the invention will become apparent from the following description of the preferred embodiments and from the drawings, which show: Fig. 1 shows a cylinder of a crankcase according to the concept of the invention; Fig. 2A, B shows a possible arrangement of a cylinder, cooling system, and distribution system; Fig. 3 shows a detailed view of a distribution system; Fig. 4 shows an internal combustion engine with a crankcase according to the concept of the invention.

[0030] Fig. 1 shows a cylinder 100 according to the concept of the invention. The cylinder 100 has a cylinder interior 120, which is delimited in the radial direction by a cylinder liner 140 and in which a piston 122, shown here in a highly simplified manner and movable translationally along a main axis HA, can be accommodated. The cylinder liner 140 can be inserted into a crankcase of an internal combustion engine 1000 (not shown here). In order to generate a drive movement, the piston 122 is moved up and down by combustion carried out within the cylinder interior 120. A cylinder head 160 closes the cylinder 100 on an upper side, i.e., the side of the cylinder 100 opposite a crankshaft of the internal combustion engine. At the transition to the cylinder interior 120, the cylinder head 160 has a flame deck 164, which represents the boundary surface to a combustion chamber 124, in which combustion takes place within the cylinder interior 120.The flame deck 164 thus forms the end-face boundary of the combustion chamber 124 opposite the piston 122. The cylinder head 160 has a receiving means 162, in particular a receiving sleeve or receiving bushing or the like, comprising and / or guiding a receiving means for a device or component extending into the cylinder, in particular for an injector or an ignition device for an injector or an ignition device 162. By means of an injector 162.1, fuel can be guided into the combustion chamber 124, particularly in embodiments used in a diesel engine.

[0031] By means of an ignition device 162.2, which can be designed in particular as a spark plug, a mixture located in the cylinder interior 120 can be ignited. This is particularly the case in embodiments used in gas or gasoline engines.

[0032] The receiving means 162 can be designed to receive an injector 162.1 or an ignition device 162.2, or can already be formed as a one-piece receptacle with an integrated injector 162.1 or an integrated ignition device 162.2; thus, the receiving means 162 does not necessarily have to be present as a separate part, but the receiving means 162 can simply be formed as a receptacle in a workpiece or device. Furthermore, the cylinder head 160 has a cooling system 170 with a cooling chamber 166 essentially designed as an internal cavity. In the present case, the receiving means 162, in particular a receiving sleeve or receiving bushing or the like comprising and / or guiding a receiving means for a device or component extending into the cylinder, in particular for an injector or an ignition device, is arranged rotationally symmetrically about the main axis HA.

[0033] Furthermore, the cylinder head 160 has a supply passage 210 arranged concentrically around the receiving means 162. The supply passage 210 has an approximately annular cross-section, but one whose radius varies, in particular, in sections in the axial direction, and serves to supply a coolant flow KS. Due to the annular cross-section around the receiving means 162 and in particular a taper 212, the supply passage 210 and the receiving means 162, which is formed here as a sleeve or bushing, form a nozzle 214, which shapes the coolant flow KS into an impingement flow PS, which impinges on the flame deck 164 within the cooling chamber 166. The impingement flow PS ensures that the coolant flow KS spreads along the flame deck 164 in a near-wall, radially expanding flow at a relatively high speed. This leads to a relatively high heat transfer.This means that the heat transferred from the combustion chamber 124 to the cooling chamber 166 via the flame deck 164 due to combustion taking place in the cylinder 100 is effectively absorbed and dissipated by the coolant flow KS. The coolant flow KS, which spreads in the form of the impingement flow PS over the flame deck 164, is subsequently discharged from the cooling chamber 166 via a discharge passage 220 and guided into a distribution system 240.

[0034] The distribution system 240 divides the coolant flow KS, which has already absorbed a first amount of heat in the cylinder head 160, into a primary partial flow K1 and at least one secondary partial flow K2. In this case, four secondary partial flows K2.1, K2.2, K2.3, K2.4 are branched off, each of which is fed to a cooling zone 142.1, 142.2, 142.3, 142.4 of a top liner region 142 of the cylinder liner 140 for cooling purposes. The remaining primary partial flow K1, i.e., the non-branched portion of the coolant flow KS, is fed to a residual region 144, which in this case is located below the top liner region 142.

[0035] "Below" in this context means further away from the cylinder head in the direction of the crankshaft. The top liner region 142 is the zone of the cylinder interior 120 in which the highest temperatures are expected to occur due to combustion. Therefore, according to the concept of the invention, at least one separate cooling circuit is provided for this region, which is supplied via the at least one secondary partial flow K2.1, K2.2, K2.3, K2.4. The remaining region 144 is accordingly a zone of the cylinder interior 120 in which lower temperatures occur compared to the top liner region. Therefore, this region can be cooled, in particular, with a lower specific cooling capacity. It is also possible, for example, to cool the remaining region 144 with the same absolute cooling capacity as the top liner region 142, but to design the remaining region 144 larger, so that the specific cooling capacity in the remaining region 144 is lower.

[0036] In this case, the top liner area 142 is again divided into four cooling zones 142.1, 142.2, 142.3, 142.4. These are arranged axially adjacent within the top liner area 142, viewed from the main axis HA. Each cooling zone 142.1, 142.2, 142.3, 142.4 is designed as an annular cooling channel tangentially encircling the cylinder interior 120 within the cylinder liner 140. The cooling channels do not have to be arranged as separately arranged and separate channels, but can also be different zones of a cooling chamber that can be partially or fully connected to one another by fluid flow. Each cooling zone 142.1, 142.2, 142.3, 142.4 is supplied via the respective secondary partial flow K2.1, K2.2, K2.3, K2.4. By dividing the top liner area 142 into individual cooling zones, an even more precise local influence on the cooling performance can be advantageously achieved.In particular, a correspondingly higher cooling performance can be achieved in a zone of the combustion chamber 124 in which a higher temperature development is to be expected.

[0037] For branching off the secondary partial flows K2.1 to K2.4, the distribution system 240 has a main channel 250, which in turn has a base section 242.0 with a circular cross-sectional area A0 and four cylindrical distribution sections 242.1, 242.2, 242.3, 242.4 axially spaced along a distributor axis VA. A distribution section 242.1, 242.2, 242.3, 242.4 each has a cavity with a circular cross-sectional area A1, A2, A3, A4 with a radius R1, R2, R3, R4, which is smaller than the cross-sectional area A0, A1, A2, A3 of a base or distribution section 242.0, 242.1, 242.2, 242.3 located upstream in the flow direction RS of the primary partial flow K1.

[0038] From each distribution section, a branch passage 146.1, 146.2, 146.3, 146.4 branches off transversely to the distribution axis VA, and in particular perpendicular to the distribution axis VA, which connects the respective distribution section 242.1, 242.2, 242.3, 242.4 to the corresponding cooling zone 142.1, 142.2, 142.3, 142.4 in a fluid-conducting manner. For example, the first branch passage 146.1 connects the first distribution section 242.1 to the first cooling zone 142.1.

[0039] Due to the axially adjacent arrangement of the cylindrical distribution sections 242.1, 242.2, 242.3, 242.4, ring-shaped step shoulders S1, S2, S3, S4 are created due to the radii decreasing in the direction of flow (see Fig. 3 ), at each of which the coolant flow KS moving along the distributor axis VA is partially throttled and / or swirled. This ensures that the coolant flow KS does not flow past a respective branch passage 146.1, 146.2, 146.3, 146.4, but is specifically throttled and thus fed as a secondary partial flow K2.1, K2.2, K2.3, K2.4, in particular to the respective branch passage 146.1, 146.2, 146.3, 146.4. In this way, an even distribution of the cooling capacity across different cooling zones 142.1, 142.2, 142.3, 142.4 is advantageously achieved with relatively little design effort. Alternatively, in addition to a uniform distribution - via a corresponding design of the cross-sectional areas A1, A2, A3, A4 - a deliberately uneven distribution is also possible in a specific cooling zone or a specific number of cooling zones 142.1, 142.2, 142.3, 142.4 a larger or smaller amount of cooling is supplied than to another cooling zone or number of cooling zones 142.1, 142.2, 142.3, 142.4. A residual passage 230 is connected to the fourth distribution section 242.4, which fluid-conductingly connects the distribution system 240 to the annular residual region 144, which tangentially surrounds an axial section of the cylinder interior 120. The remaining primary partial flow K1 can be supplied to the residual region 144 for cooling via the residual passage 230. In general, within the scope of the invention, several regions can also be distinguished other than the top liner region 142 and the residual region 144 by considering further regions, each of which has at least one cooling zone.

[0040] The Figuren 2A und 2B shows a possible arrangement of the cooling water supply, designated as cooling devices 200, 200`. Fig. 2A shows a serial arrangement, Fig. 2B a parallel arrangement of the cooling water flow. Fig. 2A The cooling device 200 shown essentially corresponds to the one shown in Fig. 1 A coolant source 260 provides a coolant, in particular cooling water, which is fed in the form of a coolant flow KS into the cooling chamber 166 of a cylinder head 160. There, the coolant flow KS initially cools - as in Fig. 1 shown and not illustrated in detail here - via an impingement flow PS onto the flame deck 164 of the cylinder head 160. The coolant flow KS is then fed to a distribution system 240, where it is divided into a primary partial flow K1 and at least one secondary partial flow K2. These partial flows K1, K2 each supply a region of a cylinder liner 140 for cooling purposes. The at least one secondary partial flow K2 is fed to a top liner region 142, and the primary partial flow K1 to a residual region 144. Subsequently, the partial flows K1, K2 are fed to a coolant sink 262.

[0041] The Fig. 2B The arrangement of a cooling device 200' shown in FIG. 1 differs essentially from that shown in FIG. Fig. 2A illustrated development in that a distribution system 240' is arranged between the pressure medium source 260 and a cylinder head 160'. Alternatively, instead of the distribution system 240', a branch 244, for example designed as a T-piece or similar branch, can be used. Thus, the coolant flow KS is already divided into two partial flows K1, K2 before it is fed to the cylinder head 160'. A partial flow K1, K2, in particular the branched secondary partial flow K2, is guided past the cooling chamber 166' of the cylinder head 160' via a cylinder head bypass 168, without dissipating heat therefrom, that is to say practically without developing any cooling power. The primary partial flow K1, on the other hand, is, analogously to the Fig. 2A shown further development, for the purpose of cooling into the cooling chamber 166', where it impinges on the flame deck 164 in particular by means of an impingement flow PS not shown here. The secondary partial flow K2, which is guided via the cylinder head bypass 168 and therefore practically not yet used for cooling, is fed to the top liner area 142 of the cylinder liner 140 following the cylinder head bypass 168. Here, the secondary partial flow K2 can optionally be further divided with a further distribution system, not shown here, according to the concept in order to supply various cooling zones within the top liner area 142, analogous to the Fig. 1 The primary partial flow K1, which is already used to cool the cylinder head 160', is supplied to the remaining area 144 for cooling the same. Both partial flows K1, K2 are supplied to a coolant sink 262 following the respective areas 142, 144 of the cylinder liner 140.

[0042] Fig. 3 shows a section of the distribution system 240 in detail. Particularly visible here are the annular stepped shoulders S1, S2, S3, S4, which are formed at the transitions between the distribution sections 242.1, 242.2, 242.3, 242.4 of the sub-distributor 242, as well as at the transition of the distribution section 242.4 to the remaining passage 230. For example, the first stepped shoulder S1 is formed at the transition between the first distribution section 242.1 and the second distribution section 242.2. Analogously, the second stepped shoulder S2 is formed at the transition between the second distribution section 242.2 and the third distribution section 242.3, and the third stepped shoulder S3 is formed at the transition between the third distribution section 242.3 and the fourth distribution section 242.4. At the transition of the distribution section 242.4 to the remaining passage 230 the fourth step S4 is formed.

[0043] The coolant flow KS guided through the distribution system 240 is diverted at the stage offsets S1, S2, S3, S4 and fed to a branch passage 146.1, 146.2, 146.3, 146.4 for supplying a cooling zone 142.1, 142.2, 142.3, 142.4. The mass flow of the secondary partial flow K2.1, K2.2, K2.3, K2.4 branched off at this stage offset S1, S2, S3, S4 can be influenced by designing the size of an annular step surface AS1, AS2, AS3, AS4 of a stage offset S1, S2, S3, S4. If, for example, the step surface AS2 of the second step shoulder S2 is selected to be larger, a correspondingly larger proportion of the coolant flow KS is deflected at this second step shoulder S2 and fed as a second secondary partial flow K2.2 to the second branch passage 146.2 in order to supply the second cooling zone 142.2 with coolant.

[0044] Fig. 4shows an internal combustion engine 1000 with an engine 700. The engine 700 has a crankcase 800, which in turn has a number Z of eight cylinders 100—illustrated here in a highly simplified manner. Each cylinder 100 has a distribution system 240, which, according to the concept of the invention, divides a coolant flow (not shown here) into a primary cooling flow and at least one secondary cooling flow. LIST OF REFERENCE SYMBOLS

[0045] 100 Cylinder 120 Cylinder interior 122 Piston 140 Cylinder liner 142 Top liner area of ​​the cylinder liner 142.1 - 142.4 Cooling zone of the top liner area 144 Remaining area of ​​the cylinder liner 146, 146.1 - 146.4 First to fourth branch passages 160, 160` Cylinder head 162 Receiving means, in particular receiving sleeve or receiving bush or similar comprising and / or guiding receiving means for a device or component extending into the cylinder, in particular for an injector or an ignition device 162.1 Injector 162.2 Ignition device 164 Flame deck 166, 166` Cooling chamber 168 Cylinder head bypass 170 Cooling system 200, 200` Cooling device 210 Feed passage 212 Taper 214 Nozzle 220 Discharge passage 230 Remaining passage 240, 240` Distribution system 242.0 Basic section 242.1 - 242.4 Distribution section 250 Main channel 260 Coolant source 262 Coolant sink 700 engine 800Crankcase 1000 internal combustion engine A, A1-4Cross-section, first to fourth cross-section AS, AS1 - AS4Step surface, first to fourth step surface HAMain axis K1Primary partial flow K2Secondary partial flow K2.1 - K2.4First to fourth secondary partial flow KSCoolant flow PSSwivel flow RSSFlow direction of the coolant flow S, S1 - S4Stage offset, first to fourth stage offset VADistributor axis ZNumber of cylinders

Claims

1. Engine (700) comprising a crankcase (800) with a number (Z) of at least one cylinders (100), for an internal combustion engine (1000), further comprising: - a cylinder liner (140) arranged within a cylinder interior (120) of the cylinder (100), and - a cylinder head (160) of the cylinder (100) that closes the cylinder interior (120) of the cylinder (100), wherein the cylinder head (160) has a receiving means (162) for a device or component that extends into the cylinder (100), and - a cooling system (170) that conducts a coolant flow (KS) with a cooling chamber (166), - a distribution system (240) arranged in the crankcase (800), for separating the coolant flow (KS) into a primary partial flow (K1) and at least one secondary partial flow (K2, K2.1, K2.2, K2.3, K2.4), wherein - the cooling system (170) has a feed passage (210) for feeding the coolant flow (KS) along the receiving means (162) onto a flame deck (164) of the cylinder head (160) in such a way that an impingement flow (PS) arises on the flame deck (164), and characterised in that - the distribution system (240) is arranged after the cylinder head (160) in the direction of flow (RS), wherein - for the primary partial flow (K1), a main channel (250) is arranged, and for the secondary partial flow (K2, K2.1, K2.2, K2.3, K2.4) a branching-off passage (146, 146.1, 146.2, 146.3, 146.4) arranged transversely to the main channel (250) and branching off from the main channel (250) is arranged in the crankcase (800), and wherein - the distribution system (240) is designed to supply the at least one secondary partial flow (K2, K2.1, K2.2, K2.3, K2.4) to a top liner region (142) of the cylinder liner (140) that is closer to the cylinder head (160), and the primary partial flow (K1) to a remaining region (144) of the cylinder liner (140) that is further away from the cylinder head (160).

2. Engine (700) according to claim 1, characterised in that the branching-off passage (146, 146.1, 146.2, 146.3, 146.4) is fluidically connected to a cooling zone (142.1, 142.2, 142.3, 142.4) of the cylinder liner (140), namely of the top liner region (142).

3. Engine (700) according to claim 1 or 2, characterised in that the distribution system (240) has a number of distribution sections (242.1, 242.2, 242.3, 242.4), wherein a distribution section is fluidically connected to a branching-off passage (146, 146.1, 146.2, 146.3, 146.4).

4. Engine (700) according to claim 3, characterised in that a distribution section (242.1, 242.2, 242.3, 242.4) has a cross section (A1, A2, A3, A4) that is smaller than the cross section (A1, A2, A3, A4) of a distribution section (242.1, 242.2, 242.3, 242.4) arranged before it in a direction of flow (RS) of the coolant flow (KS).

5. Engine (700) according to claim 4, characterised in that the cross section (A1, A2, A3, A4) is round.

6. Engine (700) according to one of the preceding claims, characterised in that a fork (244) is arranged before the cylinder head (160) in the direction of flow (RS).

7. Engine (700) according to one of the preceding claims, characterised in that the feed passage (210) is arranged concentrically around the receiving means (162).

8. Engine (700) according to one of the preceding claims, characterised in that the receiving means (162) is a receiving means that includes and / or carries a receiving sleeve or receiving bushing or the like for a device or component that extends into the cylinder.

9. Engine (700) according to one of the preceding claims, characterised in that the device or component extending into the cylinder is an injector or an ignition device for an injector or an ignition device.

10. Engine (700) according to one of the preceding claims, characterised in that the feed passage (210) and the seating for an injector or an ignition device (162) together form a nozzle (214) with an annular cross section.

11. Internal combustion engine (1000) with an engine (700) according to one of the claims 1 to 10.