Bearing assembly for a camshaft of an internal combustion engine, and crankcase comprising same

Abstract

The invention relates to a bearing assembly (1) for a camshaft of an internal combustion engine (100), wherein the internal combustion engine (100) has a crankcase (1), the camshaft (5) has a camshaft gearwheel (9) and a shaft end (7) associated with the camshaft gearwheel (9), and the bearing assembly (1) has an axial bearing (11) which is set up to support the camshaft (5) on the side of the shaft end (7). According to the invention the thrust bearing (11) has a crescent-shaped plain bearing body (13), which is designed to axially support the camshaft (5) and to be attached to the crankcase (1) by means of a mounting interface (19).

Description

[0001] Bearing arrangement for a camshaft of an internal combustion engine and crankcase with the same

[0002] DESCRIPTION

[0003] The invention relates to a bearing arrangement for a camshaft of an internal combustion engine, wherein the internal combustion engine has a crankcase, the camshaft has a camshaft gear and a shaft end associated with the camshaft gear, and the bearing arrangement has an axial bearing which is designed to support the camshaft on the side of the shaft end.

[0004] Bearing arrangements of the aforementioned type are well known and are used in engine construction to ensure a stable and precisely positioned camshaft in the crankcase. Since the camshaft controls the timing of the engine's ignition points, smooth running and the highest possible reliability are of utmost importance.

[0005] While the known bearing arrangements generally perform their bearing function satisfactorily, there is a desire to improve the bearing arrangements in terms of cost efficiency without compromising the quality and functional reliability of the bearing arrangement.

[0006] The invention was therefore based on the object of mitigating the above-described disadvantages as far as possible in a bearing arrangement of the type described above. In particular, the invention was based on the object of providing a bearing arrangement that enables simplified maintenance and assembly without compromising the running quality of the camshaft.

[0007] The invention solves the underlying problem by proposing a bearing arrangement according to claim 1. In particular, in a bearing arrangement of the type initially described, the invention proposes that the axial bearing have a crescent-shaped plain bearing body which is designed to axially support the camshaft and to be fastened to the crankcase by means of a mounting interface. In a first development, the camshaft has a bearing groove which is circumferentially formed in the camshaft; the crescent-shaped plain bearing body is designed to be inserted into the bearing groove for axially supporting the camshaft, to axially support the camshaft in the inserted state, and to be fastened to the crankcase by means of the mounting interface in the inserted state.

[0008] Alternatively, the invention proposes that not the camshaft, but the plain bearing body has the bearing groove and is designed to be pushed onto a corresponding shoulder of the camshaft for axial support of the camshaft, to support the camshaft axially in the pushed-on state and to be held in the pushed-on state by means of a

[0009] Mounting interface to be attached to the crankcase. The following considerations and preferred embodiments also apply accordingly to this alternative.

[0010] The invention is based on the realization that conventional axial bearings, due to their reduced, yet still relatively high, number of parts compared to rolling bearings, entail assembly effort that could be optimized. In conventional axial bearings, in which rotating parts are to be axially supported on stationary parts, the axial bearings were designed as dedicated units in which a stationary part always had to be attached to a first component and a rotating part was attached to the second, rotating component. These stationary and rotating components of the axial bearing were each designed as one or more parts and often included additional interaction elements forming the sliding surface or other bearing surface.

[0011] The invention departs from this conventional concept by constructing the axial bearing from only two mechanical elements, including the camshaft. Strictly speaking, the axial bearing comprises only a single component, namely the crescent-shaped plain bearing body, which engages the groove with its bearing surfaces adapted to the groove.

[0012] In the context of the invention, the term sickle shape is to be understood as meaning that the plain bearing body has a section with a substantially semicircular shape, which conforms to the circumferential bearing groove, in particular has an identical curvature.

[0013] Cost efficiency has already been optimized by reducing the number of parts. Cost efficiency is further optimized by the fact that the sickle-shaped plain bearing body can be inserted laterally into the bearing groove, namely in a radial or radial / tangential movement. This allows the camshaft and crankcase to be assembled and inserted into the predetermined position in the crankcase. Once the bearing groove is approximately in the designated assembly position, the plain bearing body can be engaged with the camshaft by being inserted into the locating groove. Since the camshaft is still movable in the axial direction at this point, the resulting unit consisting of camshaft and plain bearing body can then be assembled in a single step by attaching the plain bearing body to the crankcase using the assembly interface.

[0014] This also speeds up and simplifies assembly, further increasing cost efficiency. At the same time, the plain bearing body remains more accessible for maintenance work.

[0015] Whenever an axial direction is mentioned in the context of the invention, this refers to the direction of the camshaft's rotational axis. Likewise, a radial or tangential movement always refers to a movement relative to the camshaft's rotational axis.

[0016] The invention is advantageously further developed in that the mounting interface has a contact surface, wherein the crankcase has a corresponding contact surface, which is preferably arranged on a wall of the crankcase.

[0017] In preferred embodiments, a side wall, end wall, or other partition wall in the crankcase is used as the crankcase wall. The wall can completely enclose partial volumes of the crankcase or the entire crankcase, or even just parts of the crankcase. As an alternative to a wall, other structures that impart rigidity to the crankcase, such as struts or webs for holding the camshaft in general and the axial bearing in particular, can also be used.

[0018] In a preferred embodiment, the plain bearing body is designed to be axially bolted to the crankcase. The position of the plain bearing body on the crankcase can be defined very precisely by machining the contact surfaces of the mounting interface and the crankcase. This avoids the buildup of long tolerance chains, which are unavoidable with conventional axial bearings. The axial bolting of the plain bearing body to the crankcase also facilitates the assembly of the camshaft and plain bearing body assembly.

[0019] In a further preferred embodiment, the mounting interface on the plain bearing body has a number of through holes in a predetermined pattern, which extend in the axial direction from a first side facing away from the contact surface to a second side of the plain bearing body facing the contact surface, and wherein the crankcase has a number of threaded holes in the same pattern.

[0020] It may be advantageous to create the round holes that define the pattern on the plain bearing body and the crankcase in a single operation. In preferred embodiments, the holes of the pattern, i.e., the through holes on the plain bearing body and the threaded holes on the crankcase, are located on a common pitch circle around the camshaft axis.

[0021] In a further preferred embodiment, the plain bearing body has an increased material thickness in the axial direction in the region of the mounting interface, preferably formed as a projection on the first side. The regions of increased material thickness advantageously increase the clamping length for the screw connection. The material reinforcements can be formed integrally on the plain bearing body, for example, if it is a cast part; alternatively, they can also be additionally provided on the plain bearing body, for example, by means of discs or sleeves that are arranged on the plain bearing body or are firmly connected to it.

[0022] In a preferred variant, the plain bearing body can be provided as a cast part, or in a further preferred variant as a sheet metal part; in both variants, precise shaping and machining of the relevant contact surfaces and bearing surfaces is possible, even in large quantities.

[0023] In a further preferred embodiment, the plain bearing body has a first bearing surface and a second bearing surface opposite the first bearing surface. The bearing groove has two opposing groove flanks, and the bearing surfaces each face one of the groove flanks when the plain bearing body is inserted. The groove flanks and the plain bearing surfaces are preferably formed parallel to one another. In each case, a bearing surface of the plain bearing body and a groove flank facing it form a pair of plain bearing surfaces.In a preferred embodiment, the (first) axial distance between the opposing groove flanks is greater than the (second) axial distance between the opposing bearing surfaces of the plain bearing body, wherein the first axial distance is preferably greater than the second distance in a range of 0.01 to 0.5 mm, so that an axial bearing gap can form between the bearing surfaces and the groove flanks in the inserted state. Further preferably, the axial bearing gap on both sides of the bearing surfaces is 0.025 mm to 0.4 mm or more, particularly preferably 0.05 mm to 0.2 mm.

[0024] In a further preferred embodiment, the axial bearing is a fluid-lubricated axial bearing, and the plain bearing body has a fluid channel that can be fluidly connected to a lubricant supply, wherein the fluid channel has at least one outlet for each bearing surface that opens into the bearing surface. The application of lubricant to both bearing surfaces by means of the fluid channel has the advantage that a fluid film can form on both sides of the plain bearing body on the respective groove flank, which simultaneously promotes or brings about hydrodynamic centering of the plain bearing body in the bearing gap formed by the groove flanks. It is particularly preferred if the outlets of the fluid channel are each aligned symmetrically, particularly preferably in alignment with one another, towards the opposite sides of the plain bearing body.

[0025] In a further preferred embodiment, the plain bearing body has an inlet side and an exhaust side in the circumferential direction relative to the operating direction of the camshaft. In the context of the invention, the operating direction of rotation is understood to be the direction of rotation in which the camshaft rotates for the majority of its operating time during normal engine operation.

[0026] The outlets of the fluid channel are preferably positioned closer to the inlet side than the outlet side. This is beneficial for lubricant distribution along the bearing gaps.

[0027] As already indicated above, in a preferred embodiment the outlets of the fluid channel are preferably aligned coaxially with each other.

[0028] In a further preferred embodiment, the bearing surfaces have a circumferential end face at their inlet end, on each of which a chamfer is formed. The chamfer preferably has an angle of 2° to 10°, particularly preferably 4° to 6°, so that the plain bearing body is tapered in a wedge shape at the inlet end. The wedge-shaped taper created by the chamfers has the advantage, on the one hand, that the assembly, i.e., the insertion, of the plain bearing body into the bearing groove is significantly simplified.On the other hand, the wedge-shaped taper contributes to the fact that during operation, i.e. when the camshaft is rotating, lubricant which is not brought into the gap through the fluid channel but which is whirled up by the rotating parts in the engine housing and which hits the inlet side of the axial bearing is drawn into the wedge, which acts as a funnel, by the rotation of the camshaft, which further improves the lubrication of the axial bearing.

[0029] In a preferred embodiment, the bearing arrangement comprises a radial bearing for the camshaft, particularly in the region of the shaft end, wherein the radial bearing supports the camshaft radially on the crankcase. In such an embodiment, the radial bearing is preferably arranged in a bearing seat of the crankcase, and the axial bearing is arranged in the axial direction between the radial bearing and the camshaft gear.

[0030] In a preferred embodiment, the radial bearing is arranged in the wall of the crankcase, to which the axial bearing with its mounting interface is also attached from one of the axial end faces. Thus, the camshaft gear and the axial bearing are preferably located on the same side of the crankcase wall in which the radial bearing is located, which further simplifies assembly and maintenance. To service or replace the axial bearing, only the camshaft gear needs to be removed from the end face of the shaft, leaving the entire axial bearing exposed on the crankcase wall.

[0031] The axial bearing is preferably oriented such that the plain bearing body engages beneath the camshaft. In other words, the plain bearing body wraps around the camshaft from below—relative to the direction of gravity in the operational orientation of the crankcase. The sickle shape causes the plain bearing body to form a trough. This has the advantage that less oil escapes both during operation and when the engine is not running. This has the advantage, particularly after periods of downtime, of ensuring emergency lubrication until sufficient oil pressure is present in the lubricant supply to the bearing arrangement after the engine has started, preferably within a period of 15 to 20 seconds after the engine has started.

[0032] The invention has been described above with reference to a bearing assembly in a first aspect. In a second aspect, the invention further relates to a crankcase of an internal combustion engine, comprising a camshaft, a camshaft gear attached to the camshaft for driving the camshaft, and a bearing assembly.

[0033] According to the second aspect, the invention achieves the object described at the outset in that the bearing arrangement is designed according to one of the preferred embodiments described above.

[0034] With regard to the second aspect, the invention utilizes the same advantages as the bearing assembly according to the first aspect. Preferred embodiments of the bearing assembly according to the first aspect are simultaneously preferred embodiments of the crankcase according to the second aspect, and vice versa, which is why reference is made to the above statements to avoid repetition.

[0035] Because in the crankcase according to the invention the camshaft has the camshaft gear and a shaft end assigned to the camshaft gear, and the bearing arrangement has the axial bearing, which axially supports the camshaft on the side of the shaft end, wherein the camshaft has the position groove which is circumferentially introduced into the camshaft, and the axial bearing has the sickle-shaped plain bearing body, which is inserted into the position groove for axially supporting the camshaft, axially supports the camshaft, and is fastened to the crankcase by means of the mounting interface, a reliable bearing of the camshaft is achieved, which is significantly easier to install and maintain than conventional axial bearings, without having to make any compromises on the quality of the axial positioning of the camshaft.

[0036] The plain bearing body does not need to be pressed, but can be axially bolted to the crankcase. The fluid channel of the plain bearing body can be easily connected to a lubricant supply, ensuring lubrication of the plain bearing.

[0037] 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.

[0038] Embodiments of the invention will now be described below with reference to the drawings, in comparison with the prior art, some of which are also illustrated. With regard to supplements to the teachings immediately apparent from the drawings, reference is made to the relevant prior art. It should be noted that numerous modifications and changes regarding the form and detail of an embodiment can be made without deviating from the general idea of ​​the invention.

[0039] The general concept of the invention is not limited to the exact form or detail of the preferred embodiment shown and described below, nor is it limited to a subject matter that would be limited compared to the subject matter claimed in the claims. In the case of specified dimensioning ranges, values ​​within the stated limits are also intended to be disclosed as limit values ​​and can be used and claimed as desired.

[0040] 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:

[0041] FIG. 1 is a schematic spatial representation of a crankcase according to a preferred embodiment,

[0042] FIG. 2 is a partially sectioned schematic plan view of the crankcase according to FIG. 1 from a different perspective,

[0043] FIG. 3 is a partially sectioned schematic plan view of the crankcase according to FIG. 1 and FIG. 2 from a different perspective,

[0044] FIG. 4 is a partially sectioned schematic plan view of the crankcase according to FIG. 1 to FIG. 3 from a different perspective,

[0045] FIG. 5 is a plan view of a wall of the crankcase according to FIG. 1 to FIG. 3 with the camshaft gear removed, and

[0046] FIG. 6 shows various, partially sectioned detailed views of a plain bearing body for the crankcase of FIG. 1 to FIG. 5.

[0047] FIG. 1 shows a crankcase 1 of an internal combustion engine 100. The crankcase 1 has a wall 3 in which a camshaft 5 is mounted by means of a bearing arrangement (cf. FIG. 2 to FIG. 6). The camshaft 5 has a shaft end 7 to which a camshaft gear 9 is fastened. The camshaft gear 9 is designed to be driven by a gear and to rotate the camshaft 5 in an operating direction of rotation B about a rotation axis A. The crankcase 1 can be closed with one or more covers, which are not necessary for explaining the invention here and are therefore not shown.

[0048] As can be seen from FIGS. 2 to 5, an axial bearing 11 is arranged between the camshaft gear 9 and the wall 3. The axial bearing 11 has a crescent-shaped plain bearing body 13. The plain bearing body 13 has a bearing section 15 that is inserted into a bearing groove 17 provided circumferentially on the camshaft 5.

[0049] The sliding bearing body 13 further comprises a mounting interface 19 by means of which the sliding bearing body 13 is fastened to the wall 3.

[0050] The assembly is preferably carried out in such a way that the camshaft 5 is pushed approximately into its designated operating position in the direction of the axis A. Then, preferably with the camshaft gear 9 not yet mounted, the plain bearing body 13 is laterally engaged with the camshaft 5 in such a way that the bearing section 15 dips into the position groove 17.

[0051] The plain bearing body 13 is then brought into contact with the wall 3 by means of the mounting interface and secured, for example, by axial screwing, as shown in the present embodiment. For this purpose, the bearing assembly has a number, in particular a plurality, of screws 21, which are attached to the plain bearing body 13 and the wall 3 along a predetermined pattern.

[0052] The wall 3 has a contact surface 23 for receiving the plain bearing body 13, corresponding to its mounting interface 19. This contact surface can be formed as a single piece or segmented into several spaced-apart parts. After the plain bearing body 13 has been mounted and secured to the wall 3, the camshaft gear 9 can finally be connected to the shaft end 7 of the camshaft 5 in a known manner.

[0053] The engagement of the plain bearing body 13 in the camshaft 5, particularly in its bearing groove 17, is shown in more detail in FIGS. 3 and 4. The bearing groove 17 has a groove base 25, a first groove flank 27, and an oppositely arranged second groove flank 29.

[0054] The groove flanks 27, 29 are preferably axially aligned with their surface normal and parallel to each other.

[0055] The bearing section 15 has a first bearing surface 31 and an opposite second bearing surface 33. The first bearing surface 31 preferably faces the groove flank 27, while the second bearing surface 33 faces the second groove flank 29. The bearing surfaces 31, 33 are preferably axially aligned with their surface normals and parallel to one another.

[0056] The camshaft 5 is mounted radially in the wall 3 of the crankcase 1 by means of a radial bearing 34 designed as a plain bearing, so that the axial bearing 11 acts adjacent to and at a distance from the radial bearing 35 on the one hand and the camshaft gear 9 on the other hand of the camshaft 5.

[0057] The fit of the camshaft 5 is ensured by the fine machining of the contact surface 23 of the wall 3 on the one hand and the dimensionally accurate machining of the mounting interface 19. As further illustrated in particular in FIG. 4, the screws 21 extend axially from a first side S1 of the plain bearing body 13 to a second side S2 of the plain bearing body (see FIG. 6).

[0058] The material thickness in the radially outer region of the plain bearing body 13, i.e. radially outside the bearing section 15, has an increased material thickness in the axial direction, which leads to a higher stability of the plain bearing body 13 and to an increased clamping length for the screws 21.

[0059] FIGS. 3 and 4 show a cross section through the crankcase 1 along the axis A.

[0060] The area of ​​increased material thickness extends as a projection in the direction of the axis A on the first side S1 of the plain bearing body 13.

[0061] FIG. 5—specifically divided into FIG. 5a and FIG. 5b—illustrates the crescent-shaped structure of the plain bearing body 13. The term "crescent shape" describes that the bearing section 15 takes on a substantially semicircular shape in order to optimally fit into the bearing groove 17. It is possible, and in preferred variants also provided, to further extend the shoulders on an inlet side 37 and an exhaust side 39 lying opposite in the circumferential direction; however, the wrap angle that the bearing section 15 assumes in the bearing groove 17 around the camshaft 5 remains limited to 180° or less to maintain assembly capability.

[0062] FIG. 5a shows a plan view of the plain bearing body in the mounted position on the wall 3 of the crankcase 1 with the camshaft gear 9 hidden.

[0063] The plain bearing body 13 is approximately semicircular from the inlet side 37 to the outlet side 39 in the direction of the operating direction of rotation B. The axial bearing 11 shown in FIGS. 5a and 5b is fluidly connected to a lubricant source 43 via a supply channel 41 in the wall 3 of the crankcase 1 for the lubricant supply.

[0064] The outer contour of the plain bearing body can also be essentially semicircular, as shown. However, the exact contour along the mounting interface 19 with the screw connections 21 is not essential for the bearing itself, but rather of manufacturing economic interest and depends on the desired or required arrangement of the screws 21, the supply channel 41, etc., in the application.

[0065] As can be seen from FIG. 5b, the plain bearing body 13 has in its interior, shown there in cross section, a fluid channel 45 through which lubricant is guided in the direction of the arrow Pi to the inlet side 37.

[0066] On the inlet side 37, the plain bearing body 13 has two outlets 47, 49, one of which opens into the bearing surfaces 31, 33 towards the first side S1 and the other towards the second side S2, wherein the outlets 47, 49 are aligned coaxially and symmetrically to one another.

[0067] By symmetrically introducing lubricant through the fluid channel 45 and the outlets 47, 49, hydrodynamic centering of the plain bearing body 13 in the bearing groove 17 is achieved when the camshaft 5 rotates at the intended operating speed. The fluid channel 45 can, as in the illustrated embodiment, be designed as a combination of fluid-conducting, linear bores that are closed at the ends with suitable plugs. Since the distance between the bearing surfaces 31, 33 in the axial direction is somewhat smaller than the distance between the corresponding groove flanks 27, 29 of the bearing groove 17, a bearing gap forms on both sides of the bearing section 15 of the plain bearing body 13, which is filled with lubricant during operation to ensure essentially friction-free sliding of the camshaft 5 in the axial bearing 11.

[0068] FIG. 6 shows some further details of the plain bearing body 13 for the bearing assembly and the crankcase of FIGS. 1 to 5. FIG. 6 is divided into the three FIGS. 6a, 6b, and 6c. FIG. 6a shows the first side S1 of the plain bearing body 13.

[0069] Radially outwardly adjacent to the bearing section 15, the area of ​​the mounting interface, generally described above, is formed with increased material thickness. At the locations where the screws 21 (see FIGS. 1 to 5) are to be passed through corresponding through-holes 35 of the plain bearing body 13, a raised eye 51 with a support surface 53 is formed on the first side S1, wherein the support surface 53 is designed to bear against a screw head of the screws 21.

[0070] In FIG. 6a, the view of the first outlet 47 for the lubricant is also revealed.

[0071] FIG. 6b shows a cross-section through the plain bearing body 13 to again illustrate the course of the fluid channel 45. The fluid channel 45 has a first sub-channel 45a and a second sub-channel 45b, each of which is sealed fluid-tight at its end by corresponding plugs 55.

[0072] FIG. 6c provides an external view of the second side S2 of the plain bearing body 13. On the second side S2, a flat surface 57 is formed, which merges seamlessly into the bearing surface 31, preferably forming a continuous flat surface with it.

[0073] On the inlet side 37, the bearing surface 31 has an end face 59, on which a chamfer 61 is arranged on both the first side S1 and the second side S2. The chamfers 61 each preferably have an angle relative to the respective bearing surface 31, 33 of 2° to 10°, preferably 4° to 6°, particularly preferably 5°, and thus create a wedge-shaped taper towards the end face 59. This simplifies the insertion of the plain bearing body 13 into the bearing groove 17. In addition, FIG. 6c shows an inlet 63 of the fluid channel 45, which can be fluidly connected to the lubricant source 43 and the supply channel 41 and from which the lubricant can be conveyed through the fluid channel 45 to the outlets 47, 49.

[0074] The structure outlined in FIGS. 1 to 6 can be converted from a fully disassembled to a fully assembled state in just a few steps and in a short time, is easy to maintain, and can be manufactured cost-effectively. The quality of the axial bearing is in no way inferior to conventional axial bearings.

[0075] LIST OF REFERENCE SYMBOLS

[0076] I Crankcase

[0077] 3 Wall

[0078] 5 Camshaft

[0079] 7 Shaft end

[0080] 9 Camshaft gear

[0081] II Axial bearing

[0082] 13 plain bearing bodies

[0083] 15 Storage section

[0084] 17 Courage

[0085] 19 Mounting interface

[0086] 21 screws

[0087] 23 Contact surface

[0088] 25 groove base

[0089] 27 first groove flank

[0090] 29 second groove flank

[0091] 31 first storage area

[0092] 33 second storage area

[0093] 34 Plain bearing / radial bearing

[0094] 35 through hole

[0095] 37 Inlet side

[0096] 39 Exhaust side

[0097] 41 Supply channel

[0098] 43 Lubricant source

[0099] 45 Fluid channel

[0100] 45a first sub-canal

[0101] 45b second sub-channel

[0102] 47, 49 outlets

[0103] 53 Support surface

[0104] 55 plugs

[0105] 57 flat surface

[0106] 59 front side

[0107] 61 Phase 100 Internal Combustion Engine

[0108] A rotation axis

[0109] B Operating direction Pi arrow

[0110] 51 first page

[0111] 52 second page

Claims

CLAIMS 1. Bearing arrangement (1) for a camshaft of an internal combustion engine (100), wherein the internal combustion engine (100) has a crankcase (1), the camshaft (5) has a camshaft gear (9) and a shaft end (7) assigned to the camshaft gear (9), and the bearing arrangement (1) has an axial bearing (11) which is designed to support the camshaft (5) on the side of the shaft end (7), characterized in that the axial bearing (11) has a crescent-shaped plain bearing body (13) which is designed to support the camshaft (5) axially and to be fastened to the crankcase (1) by means of a mounting interface (19).

2. Bearing arrangement according to claim 1, characterized in that the camshaft (5) has a bearing groove (17) which is circumferentially introduced into the camshaft (5), and the sickle-shaped plain bearing body is designed to be inserted into the bearing groove (17) for axially supporting the camshaft (5), to support the camshaft (5) axially in the inserted state, and to be fastened to the crankcase (1) by means of the mounting interface (19) in the inserted state.

3. Bearing arrangement according to claim 1, characterized in that the plain bearing body has a bearing groove and is designed to be pushed onto a corresponding shoulder of the camshaft for axial mounting of the camshaft, to support the camshaft axially in the pushed-on state and to be fastened to the crankcase by means of a mounting interface in the pushed-on state.

4. Bearing arrangement according to one of the preceding claims, characterized in that the mounting interface (19) has a contact surface (23), wherein the crankcase (1) has a corresponding contact surface (23) which is preferably arranged on a wall (3) of the crankcase (1).

5. Bearing arrangement according to claim 4, characterized in that the plain bearing body (13) is designed to be axially screwed to the crankcase (1).

6. Bearing arrangement according to claim 5, characterized in that the plain bearing body (13) in the region of the mounting interface (19) has an increased material thickness in the axial direction, preferably formed as a projection on the first side (S1).

7. Bearing arrangement according to one of the preceding claims, characterized in that the plain bearing body (13) has a first bearing surface (31) and a second bearing surface (33) opposite the first bearing surface (31), the bearing groove (17) has two opposite groove flanks (27, 29), and the bearing surfaces (31, 33) in the inserted state each face one of the groove flanks (27, 29).

8. Bearing arrangement according to claim 7, wherein an axial distance between the opposite groove flanks (27, 29) is greater than an axial distance between the opposite bearing surfaces (31, 33), so that in the inserted state an axial bearing gap can form between the bearing surfaces (31, 33) and the groove flanks (27, 29).

9. Bearing arrangement according to claim 8, characterized in that the plain bearing body (13) has a fluid channel (45) which can be connected in a fluid-conducting manner to a lubricant supply (43), wherein the fluid channel (45) has at least one outlet (47, 49) for each bearing surface (31, 33) which opens into the bearing surface (31, 33).

10. Bearing arrangement according to one of the preceding claims, characterized in that the plain bearing body (13) has an inlet side (37) and an outlet side (39) in the circumferential direction with respect to an operating direction of rotation (B) of the camshaft (3).

11. Bearing arrangement according to claim 9 and 10, characterized in that the outlets (47, 49) are positioned closer to the inlet side (37) than to the outlet side (39).

12. Bearing arrangement according to one of claims 9 to 11, characterized in that the outlets (47, 49) are aligned coaxially with one another.

13. Bearing arrangement according to one of claims 10 to 12, characterized in that the bearing surfaces (31, 33) have at their inlet-side end an end face (59) in the circumferential direction, on each of which a chamfer (61) is formed, so that the plain bearing body (13) is tapered in a wedge shape at the inlet-side end.

14. Bearing arrangement according to one of the preceding claims, comprising a radial bearing on the side of the shaft end (7), which supports the camshaft (3) radially on the crankcase, characterized in that the radial bearing is arranged in a bearing seat of the crankcase (1), and the axial bearing (11) is arranged between the radial bearing and the camshaft gear (9).

15. Crankcase (1) of an internal combustion engine (100), with a camshaft (3), a camshaft gear (9) fastened to the camshaft (3) for driving the camshaft, and a bearing arrangement according to one of the preceding claims.

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