DE102006036034B4 - Drive device between a camshaft adjuster and a camshaft - Google Patents

Abstract

Drive connection between an output element (5) of a camshaft adjuster (3) and a camshaft (2) for a motor vehicle, wherein the output element (5) of the camshaft adjuster (3) with the end face (14) via at least one fastener with an end face (11) Camshaft (2) is rotatably connected, wherein the end face (14) of the output element (5) and / or the end face (11) of the camshaft (2) is / are macroscopically provided with unevenness and a transmission of a drive torque between the driven element (5) and the camshaft (2) takes place via a macroscopic positive connection, characterized in that between the end faces (11; 14) a deformation element (20) with a reduced plastic limit is interposed, which involves tightening the fastening element in the region of the macroscopic unevenness of the at least one end face (11; 14) is plastically deformable, wherein the unevenness by a manufacturing has produced contour.

Description

Field of the invention

The invention relates to a drive connection for a motor vehicle between a camshaft adjuster and a camshaft according to the preamble of claim 1.

Background of the invention

In motor vehicles, camshaft adjusters are used, which serve to influence the relative rotational angle position of a camshaft relative to a crankshaft of an internal combustion engine, as a result of which operating times of the internal combustion engine can be influenced. This is particularly advantageous with regard to the design of the power delivery, the torque characteristic, the exhaust gas values, the consumption and / or a noise development of the internal combustion engine. For camshaft adjusters, there are different types, all of which can be used in connection with the relevant drive connection here, in particular camshafts with integrated gearbox, for example a single or multistage, uniformly or non-uniformly translated 3-shaft gearbox, a multi-link gearbox or coupling gearbox, a swashplate gearbox , an eccentric gear, a planetary gear, wave gear, cam gear, combinations of the aforementioned types of gears. In such transmissions, an adjusting movement can be fed in via a suitable actuator or a braking of a transmission element can be carried out. An exemplary alternative design for camshaft adjuster are those in vane or in axial piston design, in which an adjusting movement is generated via a hydraulic medium. Other possible designs are in particular those with swing wings or segment wings.

The camshaft adjusters form u. U. separate units that must be connected during assembly of the internal combustion engine, subsequently or as a variant of different embodiments of the internal combustion engine with a camshaft of the engine. In this case, production of the internal combustion engine or camshaft on the one hand and of the camshaft adjuster on the other hand often takes place from different manufacturers or suppliers. For a drive connections between the camshaft adjuster and the camshaft, a connecting element, also referred to as a central screw, is usually used, with which an output element, in particular an output shaft of the camshaft adjuster, is screwed to an end face of the camshaft, see FIG. for example. DE 100 38 354 C2 . DE 102 48 355 A1 . DE 196 11 365 C2 , A transmission of a drive torque from the output element of the camshaft adjuster to the camshaft is frictionally by pressing the end face of the output element to the end face of the camshaft via the central screw.

In alternative embodiments of a drive connection, the camshaft and output element are connected to one another in a flange manner, cf. DE 199 55 507 C2 , or the output member and the camshaft form a shaft-hub connection via which the drive torque is transmitted in a form-fitting manner in the circumferential direction, s. DE 102 48 355 A1 ,

The DE 101 61 698 A1 shows a device for the hydraulic rotation angle adjustment of a camshaft relative to a crankshaft of an internal combustion engine, which consists essentially of a standing with the crankshaft drive-connected drive unit and a rotatably connected to the camshaft drive unit. The output unit is fixed by the biasing force of a central fastening screw with its camshaft-facing side surface axially and circumferentially non-positively on the front side of the drive-side end of the camshaft. The drive unit is rotatably mounted on the output unit and is in force transmission connection therewith via at least two hydraulic pressure chambers formed within the device. Between the camshaft facing side surface of the output unit and the front side of the camshaft, an additional annular disc formed with a friction force enhancing coating is arranged, with which the necessary biasing force of the central mounting screw can be reduced and which is formed with mechanically or visually recognizable elements for checking their presence.

The DE 10 2005 034 276 A1 shows a camshaft adjusting device, which has at least one provided for coupling with a camshaft adjusting means, in particular a Flügelzellenstellerbauteil having a central valve, with a central clamping means. It is proposed that the camshaft adjusting device comprises a Zusatzfixiermittel, which is provided at least to support a rotationally fixed coupling of the actuating means with the camshaft.

Object of the invention

The invention has for its object to provide a drive connection between an output element of a camshaft adjuster and a camshaft, which is reliable, taking into account the space conditions, the forces acting and the transmissible drive torque.

Summary of the invention

According to the invention the object is achieved by a drive connection with the features of the independent claim 1 or 3. Further embodiments of the invention will become apparent according to the dependent claims.

The invention is based on the finding that known solutions of contact pressure of the end faces of output element and camshaft via a central screw require large normal forces in the central screw and in the contact surfaces, which is accompanied by large deformations of the components involved. The frictional contact of the end faces must be designed to be suitable for the drive torque with torque peaks and under the influence of vibrations u. Ä. Reliable and durable transfer. For this u. U. large friction radii and thus large end faces of the faces required, which negatively affects the required space in the radial direction. At the same time, the increased radial dimensioning means that even radially outboard arranged from the end faces components such as bearings, gear elements, actuators must be formed enlarged. This increases the construction cost of the aforementioned components and generates increased moment of inertia for the u. U. intermittently rotating components. Furthermore, increased radial dimensioning of functional surfaces such as bearings means that they have an increased effective radius, which can result in increased friction losses.

On the other hand, it has been recognized that when transmitting the drive torque via a positive connection by means of the shaft-hub connections or flange connections mentioned above, that these pretend one or more fixed relative angular positions between the output element and the camshaft. A fine adjustment of the angular position of the drive connection, which can also account for clearance or manufacturing tolerances, for example in the camshaft adjuster, is not possible. Furthermore, a production of the shaft-hub connection and a flange connection has proven to be costly and expensive.

According to the invention, a normal force acting between end faces of the output element and the camshaft can be reduced in the drive connection, without thereby reducing the torque which can be transmitted by the drive connection. Alternatively, while maintaining the normal force, the transmittable torque can be increased. As a result, according to the invention, the radial space for the drive connection, a dimensioning of the participating and surrounding components, in particular in the radial direction, the choice of strength and dimensioning of a u. U. used central screw can be reduced and / or the reliability of the drive connection can be increased.

In the context of the present invention, an "end face" (the camshaft or the driven element) is understood to mean a locally or globally plane or uneven surface via which a normal force generated by a central screw is transmitted between the output element and the camshaft. In this case, an end face can be oriented transversely to the longitudinal axis or at least partially inclined with respect to the plane oriented transversely to the longitudinal axis, so that in such a subregion the aforementioned normal force forms only one component. The front side can be arbitrarily curved or flat.

According to the proposal of the invention, an end face of the driven element and / or an end face of the camshaft is macroscopically provided with unevenness, for example roughness, protrusions, depressions, recesses, grooves or the like. A transmission of a drive torque between output element and camshaft via a macroscopic positive connection. Thus, the invention leaves the way, with a known drive torque to be transmitted to estimate the required normal force, which must be provided via a central screw, from such a drive torque, taking into account friction radii and friction coefficients. For the embodiment according to the invention, a normal force provided by a central screw is more likely to produce the macroscopic positive connection during assembly and to maintain the positive locking after assembly and during operation of the internal combustion engine. At least one subcomponent of the drive torque is thus not transmitted via a frictional connection, but rather via the macroscopic positive connection. For example, the unevenness may extend in the axial direction, so that the form-fit is produced via an axial joining of the components of the drive connection involved, in particular in connection with a tightening of the central screw.

The positive connection according to the invention and the unevennesses involved can be provided in the area of surface roughness or contours produced by manufacturing methods, whereby fracture or crack surfaces can also be used similar to a cracked connecting rod bearing. In addition to the transmission of the drive torque via the macroscopic positive locking further measures may be taken, for example, an additional frictional or positive locking in the region of an end face or a lateral surface.

The bumps may be in a specific surface topology that may be made by, but is not limited to, these embodiments by rastering, knurling, or roughening. For example, surface roughening may be achieved by spark erosion, chemical, electrochemical, spiked, embossed, impressed or reshaped patterns, or hard particles introduced or embedded in the base material which are partially exposed by surface (chemical or mechanical) treatment, respectively.

From the pamphlets DE 101 61 701 A1 and DE 199 21 890 C1 it is already known to provide a face of the camshaft and the associated end face of the driven element of the camshaft adjuster targeted with a roughness, for example in the form of a friction layer of tungsten carbide, stellite cobalt, aluminum titanium dioxide or the like, wherein the friction layer by flame spraying, high-velocity flame spraying, Arc spraying and plasma spraying can be applied (DE 199 21 890 C1). DE 101 61 701 A1 proposes the use of a sheet, which on the one hand serves to provide unevenness in the region of contacting end faces and on the other hand serves as a pulser disk. DE 101 61 701 A1 also addresses the possibility of completely dispensing with the use of additional sheet-metal shaped parts with a friction-enhancing coating and instead incorporating silicon or other hard-material particles into the base material of the camshaft, which are etched free in the region of the connection to the device and increasing the friction contribute between the device and the camshaft. Alternatively, silicon or other hard material particles can also be pressed into the camshaft-facing side surface of the drive unit of the device in the area of the connection with the camshaft, since the base material of the output shaft is generally softer than the base material of the camshaft. Regardless of how the bumps are provided for prior art designs, the prior art embodiments are evidently based on the recognition that once a roughness has been introduced, an increase in the transferability of a torsional moment at a given tightening force of a central screw is Gearing of the unevenness of contacting end faces is based. With increasing difference in the roughness of the contacting end faces, however, this effect is less and less effective. In the ideal case of an uneven front and a theoretically, ideally smooth front side, such a toothing does not come into play at all. Thus, according to the prior art, the contacting end faces must be adapted to each other in the production, which increases the production cost and inaccurate manufacturing carries the risk that the drive torque can not be reliably transmitted.

The invention here is a new way by selectively interposed between the end faces an element for which deliberately deformations are accepted. Such a deformation element has a lower plastic limit than an unevenness provided with the unevenness and / or the bumps themselves. With a generation of a normal force between the end faces, which is greater than a plastic limit of the deformation element, it comes in the area of the unevenness of the end face to a deformation the deformation element, so that it can form a positive connection. The deformation element may extend over the entire end face or only a portion of the same. By way of example, the end face is a disk or cap which does not merely bear against the end face but can laterally surround the end face with a cap edge. Under certain circumstances, a (cold) solidification of the deformation element can occur with the deformation.

An improved assembly of the drive connection and an increase in the reliability of the created drive connection can result if the previously described deformation element is formed as a kind of disc. Inside or radially outboard of this disc, a front side associated with a lateral surface can be supported, whereby an assembly aid is given and during operation and during tightening of the central screw, the deformation element can be guided radially relative to the associated end face.

For an alternative embodiment of the invention, the front sides of the output element and camshaft have different plasticity limits. In this case, the end face formed with the "harder" material less prone to plastic deformation may be macroscopically provided with the unevenness. In the event that with a mounting and tightening a central screw normal forces are generated, which are greater than the plastic limit of the softer material, takes place in the region of the bumps plastic deformation of the other end face, which is formed with the softer material. In this case, due to the plastic deformation only a positive connection can be made. Alternatively, it is also possible that a positive connection is reinforced by the plastic deformation, for example, "depressed material" fills remaining gaps in the "toothed" end faces, so that a game can be avoided.

In the context of the invention reference is made to a central screw, which brings about the normal force between the end faces. Of course, alternative elements for generating a normal force or more "central" screws can be used.

It is possible that at least one end face of output element and / or camshaft has a coating. Such a coating can, for example, provide at least one molding element with which unevenness of the end face is formed and which is then used for a macroscopic positive fit. It is conceivable that both end faces have coatings of the same hardness, which interlock with one another with the shaped element formed, for example in the form of grains or particles. It is also conceivable that the coating is formed harder than the uncoated end face, so that the coating can be pressed into the uncoated end face under plastic deformation of the uncoated end face.

On the other hand, it is alternatively or cumulatively possible for a coating to provide a softer material that can be plastically deformed from the uncoated end face to produce the macroscopic positive fit.

In addition to the possibility of coating at least one end face there is additionally or alternatively the possibility of a connection of end face and form element and / or deformation element by Einsintern, pressing, soldering, welding, gluing, clips, clamps or a combination of the aforementioned connection method.

An alternative solution of the object underlying the invention is given by a drive connection according to the features of claim 5. This embodiment is based on the basic idea that the end faces of output element and camshaft are conical at least in a contact region. The resulting conical contact surfaces have the consequence that a, for example, via a central screw, applied normal force between the end faces is divided into a normal force component, which is oriented perpendicular to the cone surface, and a friction component of the normal force, but independent of a drive torque is divided, wherein the aforementioned components are dependent on the cone angle. U. U. can be reduced according to the invention with a suitable design of the cone angle of the quotient of acting normal force and maximum transmittable torque. At the same time can be done via the cone shape centering between output element and camshaft.

According to a particular embodiment, the cone angle of the end faces are slightly different from each other. This can u. Hold U. deformations, so that, for example, with a tightening a central screw faces of a cone subjected to different levels and elastically deformed. On the other hand, it can be achieved by means of different cone angles that the end faces lie predominantly radially outward, so that the normal force acts only in areas with large friction radii, as a result of which large drive torques can be transmitted.

In addition to the measures described above, a transmittable drive torque can be increased by assigning lateral surfaces to the end faces which are connected to one another in a form-fitting manner in the circumferential direction. Such a positive connection can constantly exist, so that the above-explained inventive measures and the transferable by these torques with the transferable by the form-fitting moments sum up. It is also conceivable that a form fit in the circumferential direction on the lateral surfaces only comes into effect when the macroscopic positive connection of the drive connection fails, for example, after overcoming a rotation angle between the output element and the camshaft.

For a particular embodiment of the drive connection according to the invention, an end face of the output element and / or the camshaft is formed by an adapter. Such an adapter can, for example, an adaptability of a type of camshaft adjusters with the same output element to different camshafts and u. U. allow internal combustion engines or allow use of different camshaft adjuster for identical camshafts. It is also possible that an adapter and / or the above-described inventive constructive measures are simplified or made possible: for example, the adapter a positive connection of lateral surfaces in the circumferential direction, a coating, the bumps, protrusions, roughness, a particularly hard or provide soft material for producing plastic deformations or the like.

Advantageous developments of the invention will become apparent from the claims, the description and the drawings. The advantages of features and of combinations of several features mentioned in the introduction to the description are merely exemplary, without them necessarily having to be achieved by embodiments according to the invention. Further features are the drawings - in particular the illustrated geometries and the relative dimensions of several Components to each other and their relative arrangement and operative connection - refer. The combination of features of different embodiments of the invention, or features of different claims is also possible deviating from the chosen back-relationships of the claims and is hereby stimulated. This also applies to those features which are shown in separate drawings or are mentioned in their description. These features can also be combined with features of different claims. Likewise, in the claims listed features for further embodiments of the invention can be omitted.

Brief description of the drawings

Further features of the invention will become apparent from the following description and the accompanying drawings in which embodiments of the invention are shown schematically. Show it:

1 a drive connection according to the invention of a camshaft adjuster with a camshaft in a longitudinal section;

2 a detail II-II of the drive connection according to 1 in which, however, deviating from 1 a disk-shaped deformation element is interposed in the drive connection;

3 a dimensioning of the functional surfaces for the drive connection according to 1 in a longitudinal section;

4 a dimensioning of the drive connection and the involved and surrounding components for a configuration according to the prior art in a longitudinal section;

5 one opposite 4 According to the invention improved embodiment of a drive connection in longitudinal section;

6 a drive connection according to the invention with conical end faces in a partial longitudinal section;

7 . 8th a drive connection with positive connection of lateral surfaces of the output element and the camshaft;

9 a drive connection with polygonal contour of the end faces in side view;

10 a drive connection with respect to the transverse plane inclined end faces in a side view and

11 a drive connection with the interposition of an adapter between the end faces of the camshaft and driven element in a partially sectioned side view.

Detailed description of the invention

In 1 is a drive connection 1 between a camshaft 2 and a phaser 3 shown. Without any limitation to such a design, the camshaft adjuster is 3 according to 1 shown in the design with swash plate gear. About the camshaft adjuster 3 can be a phase angle between a drive element 4 , which is driven by a traction means of a crankshaft, and an output member 5 to be changed. For the in 1 illustrated embodiment is the output element 5 with a circular ring in the first approximation 6 and an adapter 7 educated. While the disc 6 the drive movement and the drive torque passes radially inward, leads the adapter 7 the drive movement and the drive torque in the axial direction radially inwardly through the camshaft adjuster 3 and a control unit 8th through to the camshaft 2 , A central screw 9 is aligned with a longitudinal axis 10-10 in an end face 11 screwed. Between a head 30 the central screw 9 and the front side 11 the camshaft 2 are the disc 6 and the adapter 7 clamped axially one behind the other. One by tightening the central screw 9 provided, acting in the direction of the longitudinal axis 10-10 normal force thus acts between an end face 12 the disc 6 and an associated end face 13 of the adapter 7 as well as a front side 14 of the adapter 7 and the associated end face 11 the camshaft 2 , The front ends 12 . 13 and or 11 . 14 can be formed with macroscopically formed unevenness with respect to a transversely oriented to the longitudinal axis 10-10 transverse axis, so that in the transverse plane, a toothing or a macroscopic positive connection results over the between disc 6 and adapters 7 and / or adapters 7 and camshaft 2 a drive torque can be transmitted. A release of the positive connection is only under axial movement of the disc 6 , the adapter 7 or the camshaft 2 possible, what in the tightened state of the central screw 9 avoided by these. In particular, when producing the positive connection under plastic deformation, it may also be possible that the positive connection persists even when loosening the central screw.

For the in 1 illustrated embodiment has the end face 11 the camshaft a paragraph with a substantially cylindrical lateral surface 15 , via which a radially inner, upstream annular surface 16 from a radially outer, past annular surface 17 is disconnected. The lateral surface 15 lies on a corresponding inner surface 18 of the adapter 7 on, whereby a radial guide and / or aligned axial alignment between the camshaft 2 and adapters 7 is possible. While the radially inner annular surface 16 a game over the adapter 7 forms, lies the circular ring surface 17 with the from the central screw 9 provided normal force on a corresponding mating surface 19 of the adapter 7 on under macroscopic positive connection.

For the otherwise appropriate 1 trained embodiment is according to 2 between the front side 11 the camshaft 2 and the front side 14 of the adapter 7 a deformation element 20 interposed. For the illustrated embodiment, the deformation element 20 as a (circular) disc 31 formed, whose radial extent approximately the radial extent of the annular surface 17 corresponds and has an inner bore, in the area which is the deformation element 20 on the lateral surface 15 the camshaft is supported. With tightening the central screw 9 becomes the deformation element 20 plastically deformed and fills unevenness of the faces 11 and / or front side 14 out, so that a macroscopic positive connection is formed. In particular, when producing the positive connection under plastic deformation, it may be possible that the positive connection persists even when loosening the central screw, for example, by plastically deformed material fills macroscopic undercuts.

In 3 is a mean effective friction diameter 21 the contact surfaces between the front side 11 the camshaft 2 and front side 14 of the adapter 7 shown. The inventive design, the friction diameter 21 be reduced. A reduction of the friction diameter 21 has a reduction of other adjacent components result. diameter 22 . 23 . 24 For functional surfaces such as rolling bearings, flanges or contact surfaces of adjacent components are also reduced.

5 shows the reduced diameter for the inventive design compared to known from the prior art designs according to 4 , It can be seen that for the inventive embodiment according to 5 a u. U. required centering or bushing 26 for rolling bearings with reduced diameter 25 can be formed, which u. U. also a paragraph for bridging a radial distance can be omitted.

The inventive design of the power flow for the clamping force of the central screw 9 become more direct, which in turn has positive effects on the stress on the components and thus their dimensioning. Due to the macroscopic fit, the required normal force in the clamping screw 9 be reduced. This can also lead to improved dimensions of the components of the camshaft adjuster 3 itself and / or in the design of the central screw 9 be taken into account. For example, instead of an otherwise used screw M12 now a screw M10 can be used.

As a result of a smaller dimensioning enabled according to the invention, advantages for the function of the adjusting unit can result. On the one hand, functional surfaces such as radial bearings or thrust bearings of web shafts, gear wheels and / or drive chain or pulley can be arranged on a smaller diameter. These reduced functional radii result in reduced frictional losses that affect the overall energy balance of the camshaft adjuster 3 influence positively. Finally, the rotating masses can be reduced and pulled inwards. This results in a reduction of the moment of inertia. Moving parts during an adjustment process can therefore be delayed or accelerated faster. The control behavior and a maximum achievable adjustment speed can thus be significantly improved. An inventively achievable reduced dimensioning of the cross sections can also be in an actuator or actuator 8th continue, especially in an arrangement of the actuator 8th according to the camshaft 1 and 3 is advantageous. A comparison of 4 and 5 shows the inventively reduced contact surfaces, the simplified design of the barrel or guide bushing 26 , the reduced friction radii for the bearings used, the more direct power flow and an installation space reduction for the control unit 8th ,

6 shows an embodiment in which the end faces 11 . 14 are cone-shaped with the same or different cone angles 27 , While in this case, a macroscopic fit of the faces 11 . 14 is brought about and the lateral surfaces 15 . 18 form no positive connection, the drive connection 1 for the in 7 and 8th illustrated embodiments by a positive connection of the lateral surfaces 15 . 18 strengthened in the circumferential direction at least.

• – leichte Montier- und Demontierbarkeit,
• – geringe Spannungsspitzen durch eine abgerundete konvexe Profilform,
• – hohe Tragfähigkeiten gegenüber anderen formschlüssigen Welle-Nabe-Verbindungen,
• – passgenaue Fertigung auch gehärteter Verbindungspartner durch Schleifen,
• – Selbstzentrierung und Torsionslast bei einem P3G-Profil,
• – Gleichdickcharakter beim P3G-Profil,
• – gute axiale Verschiebbarkeit unter Torsionslast bei einem P4C-Profil,
• – Längsverschieblichkeit des Profils P4C unter Drehmoment,
• – Schleifbarkeit des Nabenprofils P3G.

Also conceivable is a pure positive connection of the lateral surfaces with or without the use of a central screw 9 , By omitting a central screw 9 can require expensive machining steps to introduce a thread into the camshaft 2 and / or in the driven element 5 omitted. Risks for the functional reliability of the components due to any machining residues from a cutting process for a thread are eliminated. An assembly of the internal combustion engine becomes significant simplified, since no tuning and / or monitoring of the Einschraubprozesses for the central screw 9 must be done. The components can then be accurately dimensioned, since a scattering of the clamping force is eliminated by tolerances in manufacturing and assembly. A risk of failure due to incorrect installation or design decreases. Screws can in such a case only to an axial securing in the drive connection 1 be used. The forces then occurring are only slight. A positive connection can be made by axially or radially oriented form elements or in combination. Embodiments for positive locking in the axial and / or radial direction are the use of a splined shaft, a countershaft, a feather key, claws, pins, gear couplings or a polygonal shaft. For example, a polygon shaft-hub connection can be used, such as a polygon P4C or polygon P3G shaft-hub connection, in particular according to the standards DIN 32711 and DIN 32712 and the corresponding embodiments available on the market and Variations can be designed. Such compounds can lead to the following advantages:

• - easy assembly and disassembly,
• Low stress peaks due to a rounded convex profile shape,
• High load capacity compared to other positive shaft-hub connections,
• - Tailor-made production of hardened connection partners by grinding,
• - self-centering and torsional load on a P3G profile,
• - even character in the P3G profile,
• Good axial displaceability under torsional load in a P4C profile,
• Longitudinal displacement of the profile P4C under torque,
• - Grindability of the hub profile P3G.

The form-fitting connections mentioned here by means of radial positive locking can be made purely positive or else non-positive or positive in the broader sense. In such a combination, the respective connection types can be assigned to corresponding load shares. For example, can be used for the high load by circumferential load (torque to be transmitted) the positive locking and securing against the usually much lower axial force a frictional connection. Embodiments for a possible axial securing are a central or fastening screw, retaining rings, an axial caulking or flanging, a cohesive connection, if this is elastic enough to compensate for any micro-movements due to games in positive engagement.

With a corresponding orientation of form-locking elements to the position of individual cams of the camshaft 2 At the same time, they can be used to define the positioning unit 8th and its end stops to a specific position of the camshaft 2 (Setting the tax time) are used.

9 and 10 show further embodiments for which a positive connection is not in the region of a lateral surface of the output element 5 and camshaft 2 takes place, but in the area of abutting end faces 11 . 14 , For the in 9 illustrated embodiment are the end faces 11 . 14 corresponding to polygon surfaces 28 formed while according to the in 10 illustrated embodiment, the end faces 11 . 14 as inclined surfaces 29 are formed. These embodiments are also referred to as "axial positive engagement". This requires that an axial fixation of the relative position of the output element 5 opposite the camshaft 2 done, for example, by a central screw 9 can be done. Alternatively, it is possible that a support of the camshaft adjuster 3 or of the drive element 4 , For example, compared to a cylinder head takes place. In the front pages 11 . 14 incorporated bumps may be, for example, a toothing with an arbitrary profile, a spline, a wave-shaped profile, two bevelled faces, two fractured surfaces analogous to a cracked connecting rod bearing, for example, the output element 5 previously cracked and before joining with the camshaft 2 is connected rotationally fixed or vice versa. Also conceivable is the use of a studded profile or a pin connection in the region of the end faces 11 . 14 , With an alignment of the unevenness of the front sides 11 . 14 must be taken into account that these u. U. the relative position between the output element 5 and camshaft 2 is predetermined, so that predefined mounting positions are given, which correspond to fixed timing, so that a sensitive adjustment is not possible. An axial securing between the front sides 11 . 14 may also have to be able to absorb the resulting axial forces from the support of a drive torque to be transmitted. For axial securing, pins, screws, circlips, caulking, or other fasteners and technologies may be used.

• – einem Stoff-/Kraftschluss, z. B. Klebeverbindung und Schraubverbindung, aufgrund des zusätzlichen Stoffschlusses kann die Klemmkraft derZentralschraube reduziert werden,
• – Form-/Kraftschluss, auch eine Vorspannung durch eine Federkraft eineselastischen Elements,
• – Form-/Stoffschluss,
• – Form-/Kraft-/Stoffschluss.

Also possible is a combination of the previously explained connection forms. In addition, combinations can be used by

• - a cloth / adhesion, z. B. adhesive bond and screw, due to the additional material bond, the clamping force of the central screw can be reduced
• - Form- / adhesion, even a bias by a spring force of an elastic element,
• - form / fabric closure,
• - Form / force / material connection.

In some applications, it may be necessary that due to space constraints in the area of the end faces 11 . 14 a macroscopic fit is required to transmit the drive torques. However, the production depth in the production of the camshaft can not allow such a connection possibility or the introduction of the mold elements or the application of a coating on the camshaft turns out to be too expensive. In such a case, it is possible that an adapter 7 is used (s. 11 ). The connection of the adapter 7 with the camshaft 2 or the output element 5 carried out by frictional or material connection or macroscopic form fit. The position of the connection is relatively free with respect to the camshaft 2 and the output element 5 to choose. It can thus be placed where u. U. sufficient radial space is available to realize the required for the transmission of the drive torque Reibradius. The connection between adapter and output element 5 can then be done via macroscopic positive locking, in which case a significantly reduced cross section is required. The same central bolt is used for the connection between the camshaft and the driven element 9 used. Alternatively, independent mounting options are also possible. The adapter 7 is in contrast to the camshaft 2 easy to handle. The restrictions on the choice of materials and the associated manufacturing technology are lower, so that interlocking elements are relatively easy to represent.

LIST OF REFERENCE NUMBERS

1

drive connection

2

camshaft

3

Phaser

4

driving element

5

output element

6

disc

7

adapter

8th

actuating assembly

9

central screw

10

longitudinal axis

11

front

12

front

13

front

14

front

15

lateral surface

16

Annular surface

17

Annular surface

18

palm

19

counter surface

20

flexure

21

friction diameter

22

diameter

23

diameter

24

diameter

25

diameter

26

liner

27

cone angle

28

polygon area

29

sloping surface

30

head

31

disc

Claims (9)

Drive connection between an output element ( 5 ) of a camshaft adjuster ( 3 ) and a camshaft ( 2 ) for a motor vehicle, wherein the output element ( 5 ) of the camshaft adjuster ( 3 ) with its front side ( 14 ) via at least one fastening element with a front side ( 11 ) a camshaft ( 2 ) is rotatably connected, wherein the end face ( 14 ) of the output element ( 5 ) and / or the front side ( 11 ) of the camshaft ( 2 ) is / are macroscopically provided with unevenness and a transmission of a drive torque between the output element ( 5 ) and the camshaft ( 2 ) takes place via a macroscopic positive fit, characterized in that between the end faces ( 11 ; 14 ) a deformation element ( 20 ) is interposed with reduced plastic limit, which with tightening of the fastener in the range of macroscopic unevenness of the at least one end face ( 11 ; 14 ) is plastically deformable, wherein the unevenness has a contour produced by a manufacturing process. Drive connection according to claim 1, characterized in that the deformation element ( 20 ) is formed as a disc which is radially inward or outboard on one of the end face ( 11 ) associated lateral surface ( 15 ) is supported. Drive connection for a motor vehicle with a camshaft adjuster ( 3 ), which is an output element ( 5 ) whose front side ( 14 ) via at least one fastening element with a front side ( 11 ) a camshaft ( 2 ) is rotatably connected, wherein the end face ( 14 ) of the output element ( 5 ) and / or the front side ( 11 ) of the camshaft ( 2 ) is / are macroscopically provided with unevenness and a transmission of a drive torque between the output element ( 5 ) and the camshaft ( 2 ) takes place via a macroscopic positive fit, characterized in that an end face ( 14 ) of the output element ( 5 ) and an end face ( 11 ) of the camshaft ( 2 ) have different plasticity limits and the face formed with the harder material ( 11 ; 14 ) is macroscopically provided with bumps, in the area of which other end face formed with the more easily deformable material ( 14 ; 11 ) is plastically deformed with the tightening of the fastener, wherein the unevenness has a contour produced by a non-chemical manufacturing process. Drive connection according to one of claims 1 or 2, characterized in that at least the unevenness having face ( 11 ; 14 ) with the plastically deformed with the tightening of the fastener deformation element ( 20 ) is firmly connected. Drive connection according to one of the preceding claims, characterized in that the end faces pressed against one another via the fastening element ( 11 . 14 ) are conical. Drive connection according to claim 5, characterized in that the cone angle ( 27 ) of the end faces ( 11 . 14 ) are different. Drive connection according to one of the preceding claims, characterized in that the end faces ( 11 . 14 ) Lateral surfaces ( 15 . 18 ) are assigned, which are positively connected with each other in the circumferential direction. Drive connection according to one of the preceding claims, characterized in that a front side ( 14 ) of the output element ( 5 ) and / or the camshaft ( 2 ) from an adapter ( 7 ) is formed. Drive connection according to one of the preceding claims, characterized in that the fastening element is a central screw ( 9 ).

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