CN218206815U

CN218206815U - Camshaft module for an internal combustion engine

Info

Publication number: CN218206815U
Application number: CN202221790911.5U
Authority: CN
Inventors: 蒂洛·亨切尔; 贾斯特斯·希姆施泰特; 安东尼奥·梅农纳; 路易斯·诺依曼
Original assignee: Mahle International GmbH
Current assignee: Mahle International GmbH
Priority date: 2021-07-13
Filing date: 2022-07-12
Publication date: 2023-01-03
Anticipated expiration: 2032-07-12
Also published as: BR102022013802A2; DE102021207428A1

Abstract

The invention relates to a camshaft module (1) having a camshaft (6) and a radial bearing (12), the radial bearing (12) being designed in a closed manner for rotatably mounting a shaft arrangement (7) of the camshaft (6). By configuring the axially outermost side of the radial bearing (12 a) to be axially wider than at least one other of the radial bearings (12 b), an increased mechanical stability and an increased mechanical load-bearing capacity of the camshaft module (1) are achieved.

Description

Camshaft module for an internal combustion engine

Technical Field

The utility model relates to a camshaft module for internal-combustion engine, it includes the camshaft and is used for rotationally installing the radial bearing of camshaft device of camshaft.

Background

Camshafts are used in internal combustion engines and are commonly used to control valves of internal combustion engines. For this purpose, the camshaft has a shaft arrangement with at least one shaft, on which at least one cam is arranged in a torque-proof manner. In order to actuate the respective valve, the shaft arrangement rotates about a rotational axis during operation. To achieve this rotation, radial bearings are usually used, by means of which the shaft arrangement is rotatably mounted about the axis of rotation. The radial bearings are arranged at a distance from one another.

The camshaft is usually arranged on a cylinder head on the associated internal combustion engine. The cylinder head may include a bearing race for receiving the camshaft. The radial bearing is designed in a separate manner and is closed after the camshaft is arranged on the cylinder head. This means that a part of each radial bearing is provided on the cylinder head, wherein the camshaft, in particular the shaft arrangement, is arranged in this part of the radial bearing. Subsequently, another part of each radial bearing is connected, e.g. screwed, to the relevant part to form each radial bearing. This requires increased work in the production of the camshaft and the cylinder head as well as in the installation. This therefore leads to an increase in the duration of installation and production and an increase in the production costs.

So-called closed camshaft modules are also known, in which the radial bearing is constructed in a closed manner and therefore cannot be opened in a non-destructive manner. Here, the camshaft module is prefabricated and then mounted on the cylinder head. This allows simplified production and installation of the camshaft module and the cylinder head. In addition, in this way, the camshaft module can be mounted on the cylinder head in a variable manner.

A disadvantage of such a camshaft module is that the possible mechanical stresses of the associated camshaft are limited. As a result, a limited drive force can be transmitted to the camshaft. The possible performance increase of the associated internal combustion engine is therefore limited.

SUMMERY OF THE UTILITY MODEL

The present invention is therefore based on the problem of providing an improved or at least different embodiment for a camshaft module of the type mentioned in the introduction, which embodiment is characterized in particular by an increased mechanical load capacity and/or reduced manufacturing costs.

The invention is based on the general idea that in a camshaft module with a radial bearing, which radial bearing is constructed in a closed manner for rotatably mounting the camshaft module, the radial bearing closest to the drive transmission is constructed on the camshaft so as to be larger than at least one of the other radial bearings, preferably the remaining radial bearings. The present invention makes use of the knowledge that the radial bearing closest to the drive transmission is the radial bearing with the greatest mechanical stress. By means of the larger construction of the radial bearing, improved mechanical stability of the camshaft module and an increase in the possible drive forces which can be transmitted to the camshaft are thus achieved. By means of the smaller design of the remaining radial bearing, the material and manufacturing costs and the weight of the camshaft module are simultaneously reduced. Overall, therefore, by the concept according to the invention, in addition to the stabilization and increased load-bearing capacity of the camshaft module, a reduction in the production costs and an increased efficiency of the camshaft module and/or of the associated internal combustion engine is achieved.

According to the utility model discloses the camshaft module of thinking has the camshaft. The camshaft comprises a shaft arrangement extending in the axial direction. Furthermore, the camshaft comprises at least one cam which is mounted on the shaft arrangement in a torque-proof manner. The shaft arrangement extends in the axial direction and is mounted rotatably in the camshaft module about the axis of rotation by means of radial bearings. The radial bearings are here spaced apart from one another in the axial direction and thus in the axial direction. Furthermore, the radial bearing is constructed in a closed manner. This means that the radial bearings cannot be opened separately in a non-destructive manner. The outermost radial bearing in the axial direction is hereinafter also referred to as the outermost radial bearing, while the remaining radial bearings are hereinafter also referred to as the inner radial bearings. Here, the width of the outermost radial bearing extending in the axial direction according to the invention is greater than the width of at least one of the inner radial bearings extending in the axial direction, preferably greater than the width of the respective inner radial bearing.

The increased width of the outermost radial bearing causes the area of the outermost radial bearing to increase for rotational mounting. This results in an improved vibration behavior of the camshaft. Thus, in addition to a further increase in the load-bearing capacity, a reduced noise development is achieved.

The directions indicated here relate to axial directions corresponding to the longitudinal extent of the shaft arrangement, except preferably corresponding to the axis of rotation of the shaft arrangement. The circumferential direction thus extends around the axial direction. Furthermore, it runs "radially" transversely to the axial direction.

In principle, the radial bearings can be realized in any desired manner.

Preferably, at least one of the radial bearings, preferably each radial bearing, is designed as a plain bearing.

Advantageously, the outermost radial bearing is arranged on the axially outer side, via which bearing a force is transmitted to the camshaft for driving the camshaft. This means that the outermost radial bearing is arranged axially on this side, via which bearing the drive force for rotating the camshaft, in particular the shaft arrangement, is transmitted to the shaft arrangement.

In principle, the shaft arrangement can have a single shaft on which the at least one cam is mounted in a torque-proof manner.

It is also conceivable for the shaft arrangement to have a radially inner shaft and a radially outer shaft which are rotatable relative to one another. In this case, advantageously, at least one associated cam is arranged on each shaft in a torque-proof manner.

Embodiments are considered advantageous in which the width of the outermost radial bearing is the width of at least one of the inner radial bearings, advantageously 1.1 to 2.3 times the width of each inner radial bearing. This means that the ratio between the width of the outermost radial bearing and the width of at least one of the inner radial bearings, preferably the width of each inner radial bearing, is 1.1 to 2.3. A high load capacity of the camshaft arrangement and at the same time a simplified and economical production with increased efficiency are thus achieved in a particularly efficient manner.

Advantageously, the shaft arrangement is further mounted axially in the camshaft module. For this purpose, at least one axial bearing separate from the radial bearing can be used.

The embodiment is considered to be preferred wherein the outermost radial bearing additionally axially supports the shaft arrangement. Simplified production of the camshaft module is thus achieved. Furthermore, due to the enlarged configuration of the outermost radial bearing, the axial support can be realized in an efficient and simplified manner.

Preferably, the radially extending inner diameter of the outermost radial bearing is greater than the radially extending inner diameter of at least one of the inner radial bearings, advantageously greater than the inner diameter of each inner radial bearing. This achieves, in addition to an improved force absorption and thus increased load-bearing capacity by the outermost radial bearing, a simplification and an improvement of the axial bearing of the shaft arrangement.

In an advantageous embodiment, the shaft arrangement is axially connected at the end face in a torque-proof manner to a drive plug, by means of which drive is transmitted to the shaft arrangement in operation for rotating the shaft arrangement. The drive plug is preferably mounted rotatably in the outermost radial bearing. This enables the forces to be absorbed better by the outermost radial bearing, so that the load-bearing capacity of the camshaft is increased.

The transmission of the drive force to the shaft arrangement can in principle take place in any desired manner. Advantageously, the shaft arrangement is drivingly connected to the associated internal combustion engine for this purpose. For this purpose, a belt drive, a chain drive or the like can be drivingly connected to the shaft device, in particular by means of a drive plug.

Advantageously, the radially extending outer diameter of the outermost radial bearing is greater than the outer diameter of at least one of the inner radial bearings, advantageously greater than the outer diameter of each inner radial bearing. Thus, in addition to improved force absorption by the outermost radial bearing, the axial mounting of the shaft arrangement can be improved and simplified.

Embodiments are preferred in which the radial outer diameter of the outermost radial bearing is 1.1 to 1.6 times the outer diameter of at least one of the inner radial bearings, advantageously each inner radial bearing.

Advantageously, the radial bearing configured as a plain bearing is supplied with lubricant by the outermost radial bearing.

For this purpose, the outermost radial bearing preferably has at least one inlet opening leading from the radially outer side to the radially inner side of the outermost radial bearing, so that in operation the flow path of the lubricant enters the interior of the shaft arrangement from the outer side via the inner side. The shaft arrangement, in particular the radially outermost shaft of the shaft arrangement, here has at least one associated outlet opening for each inner radial bearing, so that the flow path leads from the interior of the shaft arrangement via each outlet opening to the associated inner radial bearing. In operation, lubricant flows into the camshaft module via the inlet opening and is distributed by rotation of the shaft arrangement such that it flows along the flow path. Openings, in particular bores, leading into the respective inner radial bearing and/or into the associated cylinder head for supplying lubricant to the inner radial bearing can thus be dispensed with. This results in a simplified production of the camshaft module and the associated cylinder head and therefore of the associated internal combustion engine.

The flow path advantageously opens into the interior of the shaft arrangement via at least one inlet opening and opens into the radial gap between the respective inner radial bearing and the shaft arrangement via an outlet opening. Advantageously, the flow path, in particular through the inlet opening, is such that in operation the radial gap between the outermost radial bearing and the shaft arrangement and/or the drive plug is also supplied with lubricant.

In principle, the shaft arrangement may have a single outlet opening for each inner radial bearing. Preferably, a plurality of outlet openings are provided for each inner radial bearing, which outlet openings are spaced apart from one another in the circumferential direction. The outlet openings can have a size of a few millimeters, for example between one and four millimeters.

The outlet openings relate in particular to oil outlet openings. In this case, it is preferred that the corresponding outlet opening is punched into the shaft arrangement. Advantageously, each outlet opening is punched from a radially inner side to a radially outer side. Thereby preventing or at least reducing possible post-processing of the shaft arrangement.

Advantageously, the shaft arrangement is closed at the end face axially remote from the outermost radial bearing. For this purpose, closure elements, such as DIN caps, pump drive plugs, closure plugs or the like, are advantageously used.

At least one of the at least one inlet opening may be configured as a radially extending bore. Likewise, at least one of the at least one inlet opening may be configured as an oil inlet groove extending in the circumferential direction. The groove preferably extends in the circumferential direction over a subsection, thus extending over less than 360 °.

Advantageously, the camshaft module has a phase adjuster. In particular, the phase adjuster serves to rotate the shaft arrangement about the axis of rotation and thus to change the phase for adjusting the valve by means of the cam.

It is preferred here that the flow path leads further from the inlet opening to the phase adjuster. This means that the phase adjuster is also centrally supplied with lubricant via the outermost radial bearing.

Alternatively, the inner radial bearing may be supplied with lubricant by a phase adjuster.

For this purpose, the phase adjuster is advantageously arranged on the side of the outermost radial bearing facing away from the inner radial bearing. To adjust the shaft arrangement, the phase adjuster is connected to the shaft arrangement by a drive plug. The phase setter has at least one inlet opening. The drive plug is provided with a cavity in its interior which is axially open on both sides. Thus, the drive plug defines a cavity within its interior. The chamber is open here on the axial side facing the phase adjuster by an inlet opening facing the phase adjuster. Furthermore, the cavity is open towards the shaft arrangement through an outlet on the side facing axially towards the inner radial bearing. Through the outlet, the drive plug is fluidly connected with the interior of the shaft assembly. The phase adjuster also has a passage leading from the inlet opening to the outlet opening of the drive plug, which passage is also referred to below as a feed passage. Thus, the flow path of the lubricant is from the inlet opening of the phase adjuster through the supply channel to the cavity of the drive plug and through the cavity of the drive plug to the interior of the shaft arrangement. The shaft arrangement has at least one outlet for each inner radial bearing. The shaft arrangement thus has an associated outlet opening for each inner radial bearing. Thus, the flow path leads from the interior of the shaft device further to the associated inner radial bearing through each outlet opening. Thus, each inner radial bearing may be supplied with lubricant during operation.

In a preferred embodiment, the outermost radial bearing is also supplied with lubricant by means of a phase adjuster. For this purpose, the drive plug preferably has, in its part arranged in the outermost radial bearing radially delimiting the cavity, a radial opening connecting the cavity to the outermost radial bearing. Thus, the flow path leads from the cavity further to the outermost radial bearing.

In principle, the connection of the drive plug to the shaft arrangement for the rotary shaft arrangement can be realized in any defined manner.

Embodiments are preferred in which the drive plug enters axially into the shaft arrangement with an axially projecting lug which delimits the cavity radially and engages with the shaft arrangement in a torque-proof manner by means of the lug. The projection thus forms an engagement pin of the drive plug, by means of which the drive plug is engaged with the shaft arrangement. Advantageously, the projection here projects axially from the part of the drive plug which is arranged in the outermost radial bearing. A simple and stable connection between the drive plug and the shaft arrangement and thus between the shaft arrangement and the phase setter can thus be achieved.

The projection is preferably shaped in a curved manner on at least one axially outer side. This means that the projection is shaped in a curved manner on the side axially facing the shaft device and/or on the side axially facing away from the shaft device, so that the phase adjuster is formed. The curved shape is advantageously configured as a rounded corner. The curvature on the projection leads in particular to an improved flow of lubricant from the drive plug into the interior of the shaft arrangement during operation. In this way, therefore, the flow of lubricant into the interior of the shaft arrangement and thus the supply of lubricant to the radial bearing is improved.

In principle, the projection of the drive plug may cooperate with the shaft arrangement in any desired manner.

An embodiment is preferred in which the projection is fitted with the shaft means by a press fit. Advantageously, the axial length of the projection corresponds to the press-fit length of the press fit.

It should be understood that the phase adjuster may have two or more inlet openings. It will also be appreciated that in a phase adjuster, two or more feed channels may lead from at least one inlet opening to the inlet of the drive plug.

Other important features and advantages of the present invention will become apparent from the accompanying drawings and the accompanying description thereof with reference to the drawings.

It is to be understood that the features mentioned above and those yet to be elucidated below can be used not only in the respectively indicated combination but also individually and in other combinations without departing from the scope of the invention.

Drawings

Preferred exemplary embodiments of the invention are shown in the drawings and will be explained in more detail in the following description, wherein like reference numerals refer to identical, similar or functionally identical components.

The lower figures are each schematically represented

Figure 1 is a highly simplified cross-sectional view of an internal combustion engine having a camshaft module,

figure 2 is a cross-sectional view of a camshaft module,

FIG. 3 is a cross-sectional view of a camshaft module in another exemplary embodiment.

Detailed Description

The camshaft module 1 as shown in fig. 1 to 3 is used in an internal combustion engine 2, for example as shown in fig. 1. The internal combustion engine 2 has at least one, preferably a plurality of cylinders 3, wherein the internal combustion engine 3 shown has, by way of example only, four such cylinders 3. A piston, not shown, is accommodated in each cylinder 3 in a stroke-adjustable manner. At least one valve 4, preferably at least two valves 4, is associated with each cylinder 3. In the example shown in fig. 1, two valves 4, i.e. an inlet valve 4a for feeding air or a separate fuel/air mixture into the cylinders and an outlet valve 4b for discharging exhaust gases from the cylinders 3, are associated with each cylinder 3, by way of example only. Upon actuation of the valves 4, the camshaft module 1 comes into use.

The camshaft module 1 comprises a camshaft 6 with a shaft arrangement 7. The camshaft 7 further comprises at least one cam 8 for actuating the valve 4. In the exemplary embodiment shown, the camshaft 6 has, by way of example only, an associated cam 8 for each valve 4. The shaft arrangement 7 extends in an axial direction 9 and is rotatable about a rotational axis 10, wherein the rotational axis 10 in the exemplary embodiment shown preferably corresponds to the axial direction 9. The cams 8 are mounted on the shaft arrangement 7 in a torque-proof manner, so that when the shaft arrangement 7 rotates they rotate to actuate the respective associated cam 8.

The shaft arrangement 7 comprises at least one shaft 11, wherein in the exemplary embodiment shown, it is assumed by way of example only that the shaft arrangement 7 has a single shaft 11, to which shaft 11 the cams 8 are each connected in a torque-proof manner. For the rotatable mounting of the shaft arrangement 7 about the axis of rotation 10, the camshaft module 11 has a plurality of radial bearings 12 which are axially spaced apart from one another. The axially outermost side of the radial bearing 12 will be referred to as the outermost radial bearing 12a, and the remaining radial bearings 12 will be referred to as the inner radial bearings 12b. In the exemplary embodiment shown, the camshaft 6 is rotated about the axis of rotation 10 by means of a drive plug 13 in order in particular to adjust the phase of the cams 8. The drive plug 13 is connected here in a torque-proof manner to the shaft arrangement 7. In the exemplary embodiment shown, the drive plug 13 passes directly through the outermost radial bearing 12a and is rotatably mounted in the outermost radial bearing 12 a.

Each radial bearing 12 is a plain bearing 14, which is further embodied in a closed manner. In the present case, a closed configuration is understood to be a configuration in which the radial bearing 12 cannot be opened in a non-destructive manner. For producing the camshaft module 1, the shaft arrangement 7 is advantageously thermally coupled to the cam 8. Advantageously, by means of the temperature difference of the shaft means 7 and the radial bearing 12, the shaft means is further guided at least through the inner radial bearing 12b, so that the radial bearing 12 is hotter than the shaft means 7.

As can be seen in particular from fig. 2 and 3, each radial bearing 12 has an axial running width 15, a radial running inner diameter 16 and a radial running outer diameter 17. As can be further seen in particular from fig. 2, the width 15a of the outermost radial bearing 12a is greater here than the width 15b of at least one of the inner radial bearings 12b. In the exemplary embodiment shown, the width 15a of the outermost radial bearing 12a is greater than the width 15b of each inner radial bearing 12b. In this way, the outermost radial bearing 12a, which forms the mechanically most stressed radial bearing 12, can receive the driving force acting on the camshaft 6 in an improved manner and thus lead to an increased mechanical stability of the camshaft module 1. Furthermore, in this way the possible mechanical stress of the camshaft module 1 is increased, so that an increased driving force can be transmitted to the camshaft 6 via the drive plug 13 in the example shown. At the same time, the smaller design of the inner radial bearing 12b leads to a simplified and economical production and assembly of the camshaft module 1 and the associated internal combustion engine 2.

As can be seen in particular from fig. 2 and 3, in the exemplary embodiment shown, the inner diameter 16a of the outermost radial bearing 12a is greater than the inner diameter 16b of at least one of the inner radial bearings 12b, and in the exemplary embodiment shown is greater than the inner diameter 16b of the respective inner radial bearing 12b. Further, in the exemplary embodiment shown, the outer diameter 17a of the outermost radial bearing 12a is greater than the outer diameter 17b of at least one of the inner radial bearings 12b, and in the exemplary embodiment shown, is greater than the outer diameter 17b of each inner radial bearing 12b.

As can be further seen from fig. 2 and 3, the outermost radial bearing 12a can further be used for axial mounting of the camshaft 6. To this end, in the exemplary embodiment shown in fig. 2, the drive plug 13 abuts a radially projecting shoulder 18 against the side of the outer radial bearing 12a facing axially away from the inner radial bearing 12b. Furthermore, the stop element 19 axially abuts on the side of the outer radial bearing 12a facing the inner radial bearing 12b. In the exemplary embodiment shown in fig. 3, the stop element 19 is formed as a radially protruding shoulder on the side of the drive plug 13 facing the inner radial bearing 12b and abuts the side of the outer radial bearing 12a facing the inner radial bearing 12b.

As can be seen from fig. 2, the supply of lubricant to the radial bearings 12 may be performed through the outermost radial bearing 12 a. For this purpose, the outermost radial bearing 12a has at least one inlet opening 22 extending from the radially outer side 20 to the radially inner side 21 of the outermost radial bearing 12a for letting lubricant into the interior 5 of the shaft arrangement 7. In the exemplary embodiment shown in fig. 2, the outermost radial bearing 12a has a plurality of such inlet openings 22 which are distributed in the circumferential direction 23, wherein each inlet opening 22 is configured as a bore 24. As can be seen from fig. 2, the flow channel 25 for the lubricant thus opens into the interior 5 of the shaft arrangement 7 via the at least one inlet opening 22. The shaft arrangement 7 also has at least one outlet opening 26 for each inner radial bearing 12b, so that the flow path 25 leads from the interior 5 of the shaft arrangement 7 to the respective associated inner radial bearing 12b. Therefore, in the case where the inner radial bearings 12b do not have corresponding openings, holes, or the like, the radial gaps 27 (see fig. 2) between the respective inner radial bearings 12b and the shaft device 7 are supplied with the lubricant. Furthermore, via the at least one inlet opening 22, lubricant can reach radially between the outermost radial bearing 12a and the drive plug 13.

As can be further seen from fig. 2, in the exemplary embodiment shown, the illustrated phase adjuster 28 of the camshaft module 1 is further supplied with lubricant via the outermost radial bearing 12 a. This means that the fluid path 25 leads further to the phase adjuster 28.

As can be further seen from fig. 2, the shaft arrangement 7 is closed at the end face 29 remote from the outermost radial bearing 12a by a closing element 30, so that lubricant is prevented from flowing out at the end face 29.

For each inner radial bearing 12b, several associated outlet openings 26 can be provided, which outlet openings 26 are distributed in the circumferential direction 23, wherein in each case only one outlet opening 26 can be seen in fig. 2 and 3. For example, for each inner radial bearing 12b, four associated outlet openings 26 may be provided, which outlet openings 26 are distributed in the circumferential direction 23. The outlet openings 26 can each be designed as oil outlet openings 31. Preferably, the outlet opening 31 is drilled radially from the inside to the outside. It is also preferred if the at least one hole 24 is drilled radially from the inside outwards.

The exemplary embodiment shown in fig. 3 also differs from the exemplary embodiment shown in fig. 1 in that lubricant is supplied to the inner radial bearing 12b by the phase adjuster 28.

For this purpose, the phase adjuster 28 has at least one inlet opening 22 for the lubricant on a radial outer side 32 and/or on an axial outer side 33 facing away from the radial bearing 12. Preferably, the phase adjuster 28 has only a single inlet opening 22 on the radial outer side 32 or the axial outer side 33. In addition, the drive plug 13 is configured in a hollow manner. The drive plug 13 therefore has in its interior a radially defined cavity 34 which is open axially on both sides. This means that the chamber 34 is configured to be open on the side facing axially towards the phase adjuster 28 or respectively facing away from the inner radial bearing 12b and thus has an inlet 35. Furthermore, the chamber 34 or the respective drive plug 13 is open on the side facing axially away from the phase adjuster 28 and therefore has an outlet 36. Through the outlet 36, the cavity 23 is connected to the interior 5 of the hollow structure of the shaft device 7. Furthermore, at least one channel 37, which is only indicated in dashed lines in fig. 3, is provided relative to the phase adjuster 28, which channel connects at least one of the at least one inlet openings 22 to the cavity 34 via the inlet 35. This channel 37 is also referred to below as feed channel 37. In the exemplary embodiment shown, the supply channel 37 connects here the relevant inlet opening 22 to the inlet 35 and thus to the chamber 34. Thus, the flow path 25 of the lubricant is open to the interior 5 of the shaft device 7 via the inlet opening 22 and the supply channel 37 through the inlet 35 and the cavity 34 and the outlet 36. The flow paths 25 thus lead from the interior 5 of the shaft arrangement 7 via the respective outlet openings 28 to the associated inner radial bearing 12b.

In the exemplary embodiment shown in fig. 3, the supply of lubricant to the outermost radial bearing 12a also takes place via the phase adjuster 28 and the cavity 34. For this purpose, the drive plug 13 has, in its part arranged at the outermost radial bearing 12a, a radially open outlet opening 26 which fluidly connects the cavity 34 with the radial gap 30 between the outermost radial bearing 12a and the part of the drive plug 13. Advantageously, the drive plug 13 has two or more such outlet openings 29, which are spaced apart from one another in the circumferential direction 23.

To connect phase adjuster 28 to shaft assembly 7, drive plug 13 in the exemplary embodiment shown in fig. 3 is mated with shaft assembly 7. For this purpose, the drive plug 13 is inserted into the interior 5 of the shaft arrangement 7 via a projection 39 which projects on the side facing axially away from the phase adjuster 28 and serves as a mounting plug 38. Here, the outlet 36 is formed on a side of the projection 33 axially facing away from the phase adjuster 28. The projection 39 also defines the cavity 34 in the radial and circumferential directions 23. The radially outer portion of the projection 39 is slightly larger than the radially inner portion of the shaft means 7. Here, the projection 39 is connected to the shaft device 7 by press fitting. A stable and torque-resistant connection of the drive plug 13 to the shaft arrangement 7 is thus achieved. As can be seen from fig. 3, the projection 39 in the exemplary embodiment shown in fig. 3 is configured to be axially curved on both sides and thus curved in a circular manner. Thus, the flow of lubricant from the drive plug 13 to the interior 5 of the shaft arrangement 7 is improved.

By means of the camshaft module 1, an improved mechanical load-bearing capacity and a reduced production cost are achieved. Further, the lubricant can be easily and reliably supplied to the radial bearing 12.

Claims

1. A camshaft module (1) for an internal combustion engine (2),

-having a camshaft (6) with a shaft arrangement (7) and at least one cam (8) arranged on the shaft arrangement (7) in a torque-proof manner,

-wherein the shaft arrangement (7) extends in an axial direction (9),

-having an axially outermost radial bearing (12 a) and at least two inner radial bearings (12 b) by which the shaft arrangement (7) is rotatably mounted about an axis of rotation (10),

-wherein the radial bearings (12) are axially spaced apart from each other,

-wherein each radial bearing (12) has a width extending in the axial direction (9) and a radially extending inner diameter,

-wherein the radial bearings (12) are each constructed in a closed manner,

-wherein the width of the outermost radial bearing (12 a) is greater than the width of at least one of the inner radial bearings (12 b).

2. The camshaft module as claimed in claim 1,

it is characterized in that the preparation method is characterized in that,

the outermost radial bearing (12 a) has a width greater than the width of each inner radial bearing (12 b).

3. The camshaft module as claimed in claim 1 or 2,

it is characterized in that the preparation method is characterized in that,

the outermost radial bearing (12 a) has a width that is 1.1 to 2.3 times the width of at least one of the inner radial bearings (12 b).

4. The camshaft module as claimed in claim 1,

it is characterized in that the preparation method is characterized in that,

the outermost radial bearing (12 a) also axially supports the shaft arrangement (7).

5. The camshaft module as claimed in claim 1 or 2,

it is characterized in that the preparation method is characterized in that,

the outermost radial bearing (12 a) has an inner diameter greater than an inner diameter of at least one of the inner radial bearings (12 b).

6. The camshaft module as claimed in claim 1 or 2,

it is characterized in that the preparation method is characterized in that,

the radially extending outer diameter of the outermost radial bearing (12 a) is greater than the outer diameter of at least one of the inner radial bearings (12 b).

7. The camshaft module as claimed in claim 1 or 2,

it is characterized in that the preparation method is characterized in that,

-the outermost radial bearing (12 a) having at least one inlet opening (22) leading from a radially outer side (20) to a radially inner side (21) of the outermost radial bearing (12 a), such that a flow path (25) for lubricant leads from the outer side (20) via the inner side (21) to the interior of the shaft arrangement (7),

-the shaft arrangement (7) having at least one associated outlet opening (26) for each inner radial bearing (12 b), such that the flow path (25) leads from the interior of the shaft arrangement (7) via each outlet opening (26) to the associated inner radial bearing (12 b).

8. The camshaft module as claimed in claim 7,

it is characterized in that the preparation method is characterized in that,

-the camshaft module (1) has a phase adjuster (28) on the side of the outermost radial bearing (12 a) facing away from the inner radial bearing (12 b),

-the flow path (25) further leads from the at least one inlet opening (22) to the phase adjuster (28).

9. The camshaft module as claimed in claim 7,

it is characterized in that the preparation method is characterized in that,

at least one of the at least one inlet opening (22) is configured as a radially extending bore (24) or as a groove extending in the circumferential direction (23).

10. The camshaft module as claimed in claim 1 or 2,

it is characterized in that the preparation method is characterized in that,

-the camshaft module (1) has a phase adjuster (28) arranged on the side of the outermost radial bearing (12 a) facing away from the inner radial bearing (12 b) in the axial direction,

-the camshaft module (1) has a drive plug (13) which passes axially through the outermost radial bearing (12 a) and connects the phase adjuster (28) to the shaft arrangement (7) in such a way that, in operation, the phase adjuster (28) rotates the shaft arrangement (7) about a rotational axis (10),

-the phase adjuster (28) has at least one inlet opening (22) for letting in lubricant,

-the drive plug (13) delimits in its interior a cavity (34), the cavity (34) opening out to the phase adjuster (28) through an inlet (35) on the side axially facing the phase adjuster (28) and to the shaft arrangement (7) through an outlet (36) on the side axially facing the inner radial bearing (12 b),

-in the phase adjuster (28) at least one feed channel (37) leads from the at least one inlet opening (22) to an inlet (35) of the drive plug (13), so that a flow path (25) of the lubricant leads from the at least one inlet opening (22) via the at least one feed channel (37) and a cavity (34) of the drive plug (13) to the interior (5) of the shaft arrangement (7),

-the shaft arrangement (7) has at least one associated outlet opening (26) for each inner radial bearing (12 b), such that the flow path (25) leads from the interior (5) of the shaft arrangement (7) via each outlet opening (26) to the associated inner radial bearing (12 b).

11. The camshaft module as claimed in claim 1 or 2,

it is characterized in that the preparation method is characterized in that,

the outermost radial bearing (12 a) has a width 1.1 to 2.3 times the width of each inner radial bearing (12 b).

12. The camshaft module as claimed in claim 1 or 2,

it is characterized in that the preparation method is characterized in that,

the outermost radial bearing (12 a) has an inner diameter larger than the inner diameter of each inner radial bearing (12 b).

13. The camshaft module as claimed in claim 1 or 2,

it is characterized in that the preparation method is characterized in that,

the outermost radial bearing (12 a) has a radially extending outer diameter larger than the outer diameter of each inner radial bearing (12 b).