DE102015206699A1 - Camshaft adjuster with hydraulic fluid conduits in / at torque-transmitting interlocking elements - Google Patents

Abstract

The invention relates to an adjusting system (25), comprising a camshaft adjuster (1) and a camshaft (4), wherein the camshaft adjuster (1) has a rotor (3) arranged radially inside a stator (2), which relative to the stator (2). wherein the rotor (3) and the stator (2) define fluid chambers (11) which can be filled by means of a hydraulic fluid, the camshaft (4) having camshaft fluid passages (12) and the rotor (3) having rotor fluid passages (13) wherein the camshaft (4) and the rotor (3) are non-rotatably connected to one another via a positive connection, wherein the camshaft fluid channels (12) and the rotor fluid passages (13) are formed in the region of the form-locking sections.

Description

The invention relates to an adjustment system, comprising a camshaft adjuster and a camshaft, wherein the camshaft adjuster comprises a radially disposed within a stator rotor which is rotatable relative to the stator, wherein the rotor and the stator define fluid chambers, which are filled by means of a hydraulic fluid, said Camshaft has camshaft fluid channels and the rotor has rotor fluid channels, wherein the camshaft and the rotor are rotatably connected to each other via a positive connection.

The publication DE 10 2010 046 619 A1 discloses a rotor for a phaser and a camshaft phasing system. Thus, it describes a rotor for a camshaft adjuster with a substantially annular rotor base body, which has an end face for axial connection to a camshaft. In addition, the publication relates to a camshaft adjusting system with such a rotor.

Furthermore, the disclosure document describes DE 10 2008 032 949 A1 a device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine. There, a device for variably adjusting the timing of gas exchange valves of an internal combustion engine is disclosed, wherein the device comprises a drive element and an output member and a camshaft, wherein an axial side surface of the camshaft rests against an axial side surface of the output member, wherein at one of the adjacent axial side surfaces Forming element is provided for aligning the output element on the camshaft with respect to the circumferential direction, which engages in a counter-form-locking element of the other component.

Another disclosure in this area is the DE 10 2012 200 099 A1 , This discloses a camshaft adjuster, which has a cover element which has at least one deformation region, which is deformed by mounting the cover element with the drive element or the output element such that a biasing force acts, which presses the cover element and the drive element or the driven element to each other.

Also the publication DE 101 34 320 A1 is located in this area. It discloses a device for changing the timing of gas exchange valves of an internal combustion engine, in particular of Rotationskolbenverstelleinrichtungen for Deckelwinkelverstellung a camshaft relative to a crankshaft. As a special feature of this disclosure, the region of the power cone of the fastening screw on the output unit as a separate, consisting of a pressure-resistant material and at the same time provided as a prefabricated pressure medium manifold of the device sleeve is formed on the output unit axially, radially and circumferentially positively and / or non-positively lockable and can be screwed without deformation on the camshaft.

The European patent application EP 1 471 215 A2 discloses a camshaft adjuster for vehicles. The device disclosed therein is characterized in that the camshaft has at least one form and / or force-locking part on which the rotor is non-rotatably seated with a base body which has a different diameter than a circle circumscribing the cams of the camshaft.

The invention is in the field of internal combustion engines, particularly hydraulic and electric camshaft adjusters for chain and belt drives for both gasoline and diesel engines, and also applications for concentric camshaft phasers. The known prior art usually describes such camshaft adjuster, which are fastened with a central screw on the camshaft.

The well-known prior art describes a connection technique, which is based on a frictional connection by a screw connection. By tightening the central screw, a biasing force is applied in the axial direction. By this axial force a tangential operating force (torque) to be transmitted. Since a coefficient of friction acts between the axial force and the tangential force, a very high axial force must be applied in order to transmit the required tangential force. Due to this high axial force, the parts in the clamping assembly are heavily loaded and partially deformed. These deformations have negative effects on the centering accuracy and leakage gaps between the involved components, e.g. the rotor internal geometry and the central valve. Another disadvantage of screwing the phaser on the camshaft is that the tightening torque of the central bolt on the phaser must be countered. For this purpose, a positive connection must be created on special geometry elements on the rotor. These must be designed to be robust, since they are loaded with the same moment, which acts in the screw tightening. As a rule, there is not enough surface available on the rotor to create elements which can transmit this moment undamaged.

If a central valve is provided for screwing the adjuster to the camshaft, the angular position of the radial bores in the assembled state is not defined. Depending on the tightening angle of the central valve, the radial bores, which guide the oil to the outside, are in different angular positions. Therefore, this angular position does not specifically in the continuing radial bores of the rotor, as they are in turn in any angular position to the valve. If the radial bores of the valve and the rotor are not aligned, this is detrimental to the oil supply to the pressure chambers. In addition, an annular channel must be created in the rotor, which is associated with increased flow losses and has a slower response of the adjustment system result. In addition, the ring channels in the rotor mean a more complex production process and a larger radial space of the rotor.

In order to set the control times of the gas exchange valves reliably during assembly of the adjuster, a defined angular position between the teeth of the adjuster and the cam position must be achieved. When connected by means of a central screw, the control times must be adjusted by means of additional measures, e.g. Fixing the camshafts are ensured. About a positive connection between the adjuster and the camshaft, the angular position between the camshaft and the toothing is firmly defined and does not have to be set consuming or otherwise fixed. A corresponding timing feature (timing pin), which is required by some customers can therefore be omitted.

The development of the camshaft adjuster requires ever smaller radial and axial space. Specifically, the axial length can not be reduced arbitrarily in a Zentralschraubenverband, as it also reduces the clamping length of the screw assembly. As a result, it is not possible to achieve a sufficient elongation length in a screw connection, the connection becomes very stiff and reacts very unfavorably to a possible setting behavior. A loosening of the central screw in operation would be the result. When transmitting the torque by means of a positive connection, the axial rigidity of the rotor does not affect the load capacity of the connection.

Furthermore, the complex design of the central valve as a screw is to be avoided. This screw housing must withstand high mechanical loads (preload and bolting torque) and must therefore be made stably. This extra housing also obstructs the flow of oil. If this housing is omitted, the valve can be made smaller and optimal in terms of the oil flow. Likewise the assembly inside the camshaft is simpler and can e.g. be realized by a locking ring.

Another problem with the bolted camshaft adjuster is the multiple assembly. If the central screw is pulled into the plastic area, it can only be used once, since then the required preload force is not reliably reached again. A form-fitting solution is easier, faster and can be reinstalled as often as desired. In addition, the connection quality of the screw solution depends on the accuracy of the Anschraubverfahrens. Scattering in the tightening process results in higher or lower preload forces. A positive connection depends only on component tolerances and thus significantly more constant with respect to the transmittable torque. In addition, a simple hand assembly without additional tools is desirable.

The disadvantages of the prior art are thus, inter alia, that the assembly of the camshaft adjuster can be performed on the camshaft only by means of very low manufacturing tolerances and high assembly costs so that the camshaft adjuster assumes the intended position relative to the camshaft. In addition to the high production costs, resulting from the low manufacturing tolerances, and any central screw, which is necessary for the intended position of the camshaft adjuster on the camshaft, another disadvantage of the known devices disadvantage is that the assembly is very time consuming. Furthermore, with the existing devices assembly errors can not be completely avoided.

It is therefore the object of the present invention to overcome the disadvantages of the prior art and in particular to provide a device which ensures an efficient fluid supply to the fluid chamber.

This is inventively achieved, the camshaft fluid channels and the rotor fluid channels are formed in the region of the positive locking causing sections. Such, for example, aligned arrangement makes it possible that no annular channel must be created in the rotor, which on the one hand less flow losses and also keeps the production costs low, since this arrangement is much easier to implement. Ultimately, this arrangement also causes the response of the adjustment system to changes in hydraulic fluid pressure to be extremely fast, as the fluid travels little distance from the hydraulic tank into the fluid chamber.

Advantageous embodiments are claimed in the subclaims and are explained in more detail below.

Thus, it is advantageous if the rotor fluid channels and the camshaft fluid channels extend exclusively in the radial direction. Thus, it is avoided that too much space in the circumferential direction is seized by the side of the fluid channels. Furthermore, the radial course of the fluid channels allows a minimum of flow losses, since the hydraulic fluid is not diverted multiple times on its way from the inner part of the adjustment system into the hydraulic chamber. Furthermore, the channels are much cheaper to realize in their production, if they run only in one direction. In addition to the very simple production process, the radially extending hydraulic passages also result in a very small radially required installation space. In this way, the compactness of the unit increases, while the fluidic advantages are also obvious.

A further advantageous embodiment is that the rotor fluid channels are arranged in the region of the rotor form-fitting elements. Thus, it is guaranteed without much effort that the camshaft fluid ducts and the rotor fluid ducts are actually aligned, since the ducts only have to be formed in the region of the form-locking elements. This reduces the complexity in the production and increases the comfort in the assembly.

A further advantageous embodiment is characterized in that the camshaft fluid channels are arranged in the region of the camshaft form-fitting elements. Thus, it is guaranteed that the camshaft fluid channels are aligned with the rotor fluid channels, since it is ensured with the above-described inventive features that the rotor form-fitting elements and the camshaft form-fitting elements mesh with each other.

It is also advantageous if the camshaft fluid channels are such that they can be connected at their radially inner end with a central valve. In this way, a reliable oil supply of the camshaft fluid channels and thus the rotor fluid channels and the hydraulic chambers of the camshaft adjuster is guaranteed. A functional work of the camshaft adjuster is thus ensured.

A further advantageous embodiment is that an angular orientation between the rotor and the camshaft is made via the positive locking. This makes it possible to perform a centering without additional effort. This minimizes the installation space and above all the costs to be incurred, since no extra component for angle orientation is necessary.

A further advantageous embodiment is characterized in that zero, one or two rotor fluid passages run radially per rotor form-fitting element. With this number of radially extending rotor channels per rotor form-fitting element is guaranteed that each hydraulic chamber of the rotor via one channel hydraulic fluid to another and discharged via another channel hydraulic fluid.

It is also advantageous if a leakage gap is formed between the flanks of the rotor form-fitting elements and the flanks of the camshaft form-fitting elements, which can be filled with oil. In this way, an active oil lubrication of the camshaft adjuster is realized, which eliminates the extra effort that must normally be applied for oil lubrication. In addition to the increasing cost efficiency of the camshaft adjuster so a decreasing complexity of the entire unit is achieved.

So it is advantageous if the distal end portion is formed as a hollow shaft. This hollow shaft makes it possible to supply the camshaft adjuster via the radially inner part of the camshaft with hydraulic fluid. The space is used optimally in this way, since no external fluid channels are necessary.

An advantageous embodiment is also characterized in that the camshaft form-locking elements are in engagement with the rotor form-fitting elements, whereby the torque-transmitting form-fit comes about, wherein the rotor form-fitting element and the camshaft form-fitting element each have a height in the radial direction, said height does not have to be identical and the engagement is configured between the rotor form-fitting element and the camshaft form-locking element so that it extends at least over 70% of the flank height of the positive-locking element with the lower height, that has an engagement ratio of at least 0.7. This engagement ratio ensures sufficient power transmission, while at the same time the space situation is taken into account. Too high engagement ratios are avoided, which resulted in very high manufacturing tolerances and thus increased the cost in height. Furthermore, the risk of geometric over-determination of the arrangement, which would entail an engagement ratio of 1, banned.

Furthermore, it is advantageous if the rotor form-fitting elements extend in the axial direction over the entire rotor inner surface. In this way, the rotor form-fitting elements have a surface which is large enough to realize the positive connection necessary for torque transmission. Thus, the device allows, at axially scarce space to reliably transmit the forces and moments occurring.

A further advantageous embodiment is that at a distal end of the rotor, a distal end face is formed, which is adapted to be in contact with an axial limiting element, such as a retaining ring, a snap ring, a locking pin or a disc. This distal end face is in the operating state with the axial limiting element in contact. In this way, the rotor has a geometrically determined surface which meets the requirements placed on an axial contact surface. With regard to the choice of material and the surface finish of the distal end face, a choice can now be made which is capable of ideally achieving an axial form-fitting connection.

An advantageous embodiment is characterized in that a camshaft adjuster with a radially disposed within a stator rotor which is rotatable relative to the stator, wherein the rotor is prepared to be rotatably connected to a camshaft and a radially inner rotor surface with at least one rotor form-fitting element wherein the rotor form-fitting element is prepared to enter into a torque-transmitting positive engagement with a corresponding camshaft form-fitting element. It is particularly advantageous if a biasing element rests against the rotor in such a way that the elements of the rotor and of the camshaft, which are in positive engagement, are prestressed against one another in the axial direction. This idea may also be independent of an adjustment system comprising a phaser and a camshaft, wherein the phaser has a rotor disposed radially within a stator which is rotatable relative to the stator, wherein the rotor and the stator define fluid chambers which are fillable by means of a hydraulic fluid wherein the camshaft has camshaft fluid passages and the rotor has rotor fluid passages, wherein the camshaft and the rotor are non-rotatably connected to each other via a positive connection, wherein the camshaft fluid passages and the rotor fluid passages are formed in the region of the positive locking sections.

It is also advantageous if a proximal end face is formed / provided at a proximal end of the rotor and is adapted to be in contact with the biasing element. Thus, the proximal end face can be designed so that it optimally receives with respect to the introduction of force that it experiences from the side of the biasing member. Also, the proximal end side is thus made possible to tailor-made with regard to the choice of materials and the surface finish on their application.

It is further advantageous if the biasing element is configured as a plate spring and the biasing element is such that it is in contact with the camshaft at its proximal end and is in contact with the rotor at its distal end. From the design as a disc spring results that a standardized component can be used. Thus, on the one hand, the production costs decrease while, on the other hand, the logistic effort decreases. This has an advantageous effect on the entire cost structure of the unit. Characterized in that the biasing member is in contact with both the camshaft and with the rotor, it allows an axial bias of the two components relative to each other. For assembly is that arrangement in which the proximal end is connected to the camshaft and the distal end is in communication with the rotor, since the biasing member is mounted in time before the camshaft adjuster.

Furthermore, the device according to the invention discloses an adjustment system, which includes a camshaft adjuster, as described above, and comprises a camshaft, wherein said adjustment system designed the torque-transmitting connection as a splined or splined shaft connection. Splined joints are suitable for transmitting high torques, making this type of connection ideal for accurately translating the torque between the phaser and the camshaft. Furthermore, splines have a minimal clearance in the circumferential direction, whereby the geometric accuracy of the unit can be guaranteed. The involute flanks, which characterize a toothed shaft connection, furthermore ensure that the torque-transmitting positive locking can always be transferred to fulfill the function, since the involute flanks provide sufficient surface area.

A further advantageous embodiment is that a distal end portion has a shaft shoulder which is directed radially outward, wherein the shaft shoulder is arranged at such an axial position that in the direction of the distal end of the camshaft, a sufficiently long portion is formed to it to arrange the rotor and the biasing element. Thus, sufficient space for the biasing member and the camshaft adjuster in the direction of the distal end, whereby the biasing member may rest against the shaft shoulder and thus can apply its force. Furthermore, arranging the shaft shoulder at that axial position at which there is sufficient space in the direction of the distal end, that there are no problems with regard to the axial installation space for the camshaft adjuster.

A further advantageous embodiment is characterized in that rotor fluid passages which are suitable for transporting a hydraulic fluid are arranged inside the rotor and lead from the rotor inner surface to a rotor outer surface and in that the distal end portion has camshaft fluid passages which extend radially and which are suitable for this purpose to transport a hydraulic fluid. This continuous connection first from the rotor inner surface to the rotor outer surface allows the supply of the fluid chambers with hydraulic fluid, preferably hydraulic oil, whereby an efficient operation of the camshaft adjuster is ensured. The arrangement of the rotor fluid channels within the rotor causes a minimal axial space of the camshaft adjusting unit. By means of the camshaft fluid channels, it is also made possible to supply the fluid chambers of the camshaft adjuster through the camshaft with hydraulic fluid, whereby the function of the camshaft adjuster is ensured. With ensured strength of the camshaft, it is thus possible to keep the necessary space minimal because the fluid channels that supply the hydraulic chambers with fluid within the camshaft are arranged.

A further advantageous embodiment is that at least six rotor form-fitting elements are mounted on the rotor inner surface in the circumferential direction. This arrangement with six rotor form-fitting elements makes it possible to transmit the high torques occurring by means of a positive connection from the camshaft adjuster to the camshaft. In addition, the number of six rotor form-fitting elements has the advantage that this results in a symmetrical arrangement, which is an advantage in terms of manufacturing costs due to the low complexity.

It is also advantageous if the rotor form-fitting elements are designed as indentations which are directed radially outward. These indentations are suitable for protrusions which are attached to the camshaft projecting into them. The recesses are designed so that their height is sufficiently large to transmit the forces and moments occurring. Thus, a functional true fit is possible with minimal axial and radial space.

A further advantageous embodiment is characterized in that the axially running rotor form-fitting elements each have two side edges, wherein the first side edge is aligned in the direction of a circumferential direction and the second side edge is oriented in the direction of the opposite circumferential direction, wherein the distance in the circumferential direction between the first side flank and the second side flank is small compared to the axial length of the rotor form-fitting element. It follows that the recesses, which are defined by the side edges, leave in their interstices in the circumferential direction so much space available that the rigidity of the rotor is not impaired, whereby this can continue to fulfill its function in an optimal manner.

It is also advantageous if the first side flank and the second side flank are configured in such a way that centering of the rotor relative to the camshaft can be performed via them. This centering allows only a relative position of the rotor to the camshaft, whereby the assembly is simplified on the one hand, and on the other a faulty mounting is avoided. This decrease in the degree of complexity of the assembly entails not negligible cost advantages in the assembly.

It is also advantageous if the rotor is made of sintered steel. Thus, the rotor can be manufactured with a high geometric accuracy while still meeting the requirements of the material in terms of its strength. Widely used sintering techniques can be used, thereby reducing manufacturing costs.

It is also advantageous if the rotor is mechanically recompressed. This causes an increase in the strength of the rotor made of sintered steel. Thus, even the highest torques can be transmitted through the rotor to the camshaft, without the material being adversely affected.

A further advantageous embodiment is characterized in that an insertion phase is arranged on the proximal end face of the rotor for simplifying the assembly. This optimizes the assembly process, further reducing the complexity of the assembly. In addition, such an insertion phase minimizes the risk of incorrect installation.

It is also advantageous if the diaphragm spring is punched from spring steel and then formed. In this way, conventional manufacturing methods for the diaphragm spring can continue to be applied, whereby the existing expertise can also be used for the disc spring now installed in this unit. Development costs for the preparation of a new diaphragm spring thus eliminated.

It is also advantageous if the plate spring is reworked by means of a heat treatment. This post-processing ensures that the plate spring can apply the necessary forces for the axial form-fit or the axial preload. Also, the heat treatment guarantees a long life of the diaphragm spring. The standardized process of heat treatment also keeps the effort required to a minimum.

Another embodiment with advantageous properties is characterized in that the biasing element has a contact area and the contact area forms rounded edges. By means of this rounding, wear is avoided, which has a positive effect on the maintenance intervals and the service life of the camshaft adjuster. In addition, chips generated during operation are thus avoided due to excessive frictional forces, which positively influences the operating temperature and does not entail undesired friction bodies.

A further advantageous embodiment is characterized in that the pretensioning element is work hardened by means of shot peening. This strain hardening optimizes the biasing force that the biasing element can apply, thereby optimally performing the axial preload of the phaser relative to the camshaft.

It is also advantageous if the pretensioning element is configured by means of two disk springs placed opposite one another, thereby avoiding an abutment region lying obliquely against the rotor. The resulting from the oblique system inefficient power transmission is thus bypassed, whereby the initiated by the biasing element form-fitting is optimally designed.

It is also advantageous if the biasing element has a progressive spring characteristic. This has the effect that under high load a penetration of the spring is prevented, while in the range of the normal load, a soft comfortable suspension is realized. In this way, it is possible that the biasing element causes a force adapted to the operating state.

It is also advantageous if the biasing element is designed as a compression spring. This is very low in their production, resulting in decreasing production costs of the unit. Furthermore, compression springs have long lifetimes, which is not expected to be a maintenance of the spring.

It is also advantageous if the biasing element is designed as a rubber buffer. This has a very low density, resulting in a weight reduction of the unit, which increases the efficiency of the unit. Furthermore, a rubber buffer has damping properties, which may well be desirable for the vibrations occurring in the engine. Rubber buffers are also preferred to form progressive spring characteristics. With their low production costs, rubber buffers also represent an advantage in terms of cost-effectiveness.

It is also advantageous if the biasing element has a central through hole which exceeds the diameter of the diameter of the camshaft in diameter. In this way, it is guaranteed that the preload element can be easily mounted on the camshaft. Any wedges are also avoided, which avoids undesirably high assembly times.

A further advantageous embodiment is characterized in that the biasing element is designed such that it exerts a purely axial force on the rotor in the direction of the distal end. In this way, a positive connection is made possible by means of the fastened at the distal end fastener without loss of power. The effect of the force in the axial direction also prevents unwanted bending moments occurring within the components involved, which would have a negative effect on the life of the individual parts.

Furthermore, it is an advantageous embodiment, when the camshaft is such that it has a distal end portion which is in contact with the rotor at its radially outer circumferential surface. The separate design of such an end section causes it to be such that it optimally fulfills the requirements imposed on it. Due to the geometric separation of the torque transmitting portion, so the distal end portion to the rest of the camshaft, these two have separate material properties, whereby both are able to fulfill their function satisfactorily with the least possible cost of materials. This separation of the function of the individual sections of the camshaft causes the camshaft is designed with the greatest possible efficiency.

It is also advantageous if the outer diameter of the distal end portion exceeds the outer diameter of the proximal, remaining camshaft. In this way, the distal end section is caused to have a sufficiently high area moment of inertia, which guarantees that, despite the configuration as a hollow shaft, sufficient force transmission takes place. The radially required space is thus kept minimal.

A further advantageous embodiment is characterized in that the distal End portion has an annular groove which is adapted to arrange the axial limiting element therein. Thus, the position of the limiting element is clearly defined, which entails a geometric determination of the camshaft adjuster in the axial direction. The axial fixing of the limiting element by means of an annular groove causes the axial limiting element can be conveniently mounted without a shaft shoulder would be necessary, which would increase the radial space.

It is also advantageous if an insertion phase is arranged at the distal end of the camshaft to simplify the assembly. Characterized in that thus given the opportunity to center the camshaft adjuster also on the camshaft, the flexibility of the arrangement is increased. The resulting simplified assembly has a positive effect on the required assembly time and thus the production costs.

It is also advantageous if the camshaft has at least six camshaft form-locking elements in the circumferential direction on a camshaft outer surface. The number of camshaft form-locking elements should correspond to the number of rotor form-fitting elements, thereby enabling an optimal positive connection. By means of those six camshaft form-fitting elements in turn a symmetrical arrangement is ensured, which reduces the manufacturing costs and the complexity of the arrangement.

It is also advantageous if the camshaft form-locking elements extend in the axial direction as long as the rotor form-fitting elements. In this way it is possible that no axial space is wasted and yet the force necessary for the positive connection is transmitted functionally filling.

It is also advantageous if the camshaft form-locking elements are formed as projections which are directed radially outward. These projections make it possible to intervene geometrically determined in the above-described indentations of the rotor.

A further advantageous embodiment is characterized in that zero, one or two rotor fluid passages run radially per rotor form-fitting element. With this number of radially extending rotor channels per rotor form-fitting element is guaranteed that each hydraulic chamber of the rotor via one channel hydraulic fluid to another and discharged via another channel hydraulic fluid.

In other words, it can be said that the inventive solution of the problem is the connection of the camshaft adjuster by an axially biased positive connection. The positive connection is the power transmission of the camshaft torque and can be realized in the form of a spline, splined shaft, keyway or polygon connection.

In addition, a spring element is used to generate an axial force on the stage / rotor. This has the task to eliminate the axial clearance, which is required for assembly, during operation. As a result, the rotor is fixed and does not rattle in operation due to axial vibrations of the camshaft. This spring element / biasing element can be designed as a plate spring, compression spring or as a rubber buffer. In order to receive the axial force of the spring element and to define the axial position of the rotor, a further axial positive engagement is realized. This can be designed as a simple circlip, snap ring, locking pin or disc.

In summary, it can be said that a contour which is pronounced prismatically in the axial direction, for example, is realized on the inner diameter of the rotor, which engages positively in a counter contour on the camshaft. Furthermore, a positive connection occurs, which centers the rotor and the camshaft to one another. The positive connection also has the task to transmit a torque between the rotor and the camshaft. In addition, the positive connection sets a fixed angular position between the rotor and the camshaft. It is another feature of the positive connection to realize radially aligned bores / channels between the rotor and the camshaft. This entails an efficient hydraulic supply to the pressure chambers. The device according to the invention also has an additional spring element between the rotor and the camshaft, which exerts a force in the axial direction and thus compensates for the axial play occurring after assembly. Furthermore, an additional form element is included, which projects radially into the camshaft and fixes the axial position of the rotor to the camshaft.

The invention will be explained in more detail by means of figures.

Show it:

1 a cross section of the entire arrangement with a camshaft, a rotor and a stator along the line II 2 ;

2 a longitudinal section of the entire unit along the line II-II 1 and 3 , wherein besides the camshaft, the rotor and the stator, among other things, the biasing element is visible;

3 a plan view of the entire unit;

4 a perspective view of the rotor, together with its rotor fluid channels;

5 a perspective view of the camshaft with their camshaft fluid ducts.

The figures are merely schematic in nature and are for the sole purpose of understanding the invention. The same elements are provided with the same reference numerals.

In 1 is a camshaft adjuster 1 shown, one radially inside a stator 2 arranged rotor 3 having, wherein the rotor 3 relative to the stator 2 is rotatable. The rotor 3 is prepared to non-rotatably with a camshaft 4 to be connected. He also has a radially inner rotor surface 5 on, the at least one rotor form-fitting element 6 includes. The rotor form-fitting element 6 is prepared to with a corresponding camshaft form-fitting element 7 to enter a torque-transmitting form-fitting, as well as from the synopsis of 4 and 5 becomes clear.

2 shows a biasing element 8th that's the rotor 3 is present that the positive-locking elements of the rotor 3 and the camshaft 4 are biased against each other at least in the axial direction / braced.

Coming back to 1 points the rotor 3 a variety of rotor blades 9 on, in conjunction with a variety of stator wings 10 fluid chambers 11 form. The individual fluid chambers 11 are using hydraulic channels that are made up of camshaft fluid channels 12 and rotor fluid channels 13 put together, supplied with fluid, such as oil. The camshaft fluid channels 12 and the rotor fluid channels 13 are formed aligned with each other. In the circumferential direction are the rotor fluid channels 13 in the field of rotor form-fitting elements 6 arranged and the camshaft fluid channels 12 are in the range of camshaft form-locking elements 7 arranged.

The camshaft 4 has a distal end portion 14 on. This is integral with the camshaft 4 formed, but has one of the remaining part of the camshaft 4 deviating geometry.

Due to the larger radial space, the rotor 3 compared with the distal end portion 14 the camshaft 4 needed, are the rotor fluid channels 13 in their amount longer than the camshaft fluid channels 12 ,

In the in 1 illustrated embodiment, the positive connection is designed as a splined connection. Here protrude six projections 15 the camshaft 4 in six indentations 16 of the rotor 3 ,

The distal end section 14 the camshaft 4 is designed as a hollow shaft. The rotor fluid channels arranged therein 13 are in different positions both in the circumferential direction and in the axial direction.

2 clarifies that the stator 2 consists of several elements. These are with at least one connecting elements 17 held together. A wave shoulder 18 allows the biasing element 8th also an axial stop on the camshaft 4 , While the biasing element 8th at the radially inner end on the shaft shoulder 18 rests, it lies at its radially outer end on a proximal end face 19 of the rotor 3 at.

Towards the distal end, the rotor 3 a distal end 20 on. This in turn is in contact with an axial limiting element 21 , An annular groove 22 sets the boundary element 21 axially fixed, causing the camshaft adjuster 1 on the camshaft 4 geometrically determined. The boundary element 21 can as a circlip 23 be designed. This circlip 23 is also in 3 shown.

4 makes it clear at which positions in the circumferential direction the rotor fluid channels 13 are arranged. As part of the disclosure according to the invention they are in the field of rotor form-fitting elements 6 arranged. For an ideal alignment with the camshaft fluid channels 12 To reach, they are at the edge of the rotor form-fitting elements 6 arranged. The two in 4 represented rotor fluid channels 13 supply two different fluid chambers 11 , which is why one of the two rotor fluid channels 13 as supply and the other as discharge for the hydraulic fluid apply.

4 shows both the rotor fluid channels 13 as they are on the rotor inner surface 5 are arranged, as well as the arrangement of the rotor fluid channels 13 on the rotor outer surface 24 ,

The rotor fluid channels 13 are in the range of rotor form-fitting elements 6 arranged, which causes the rotor fluid channels 13 the rotor outer surface 24 near the rotor wing 9 run through. This guarantees efficient adjustment regardless of the relative position of the stator 2 to the rotor 3 ,

The from the camshaft 4 and the phaser 1 with its two components rotor 3 and stator 2 existing assembly, define an inventive adjustment 25 together with or without the biasing element 8th ,

In 5 is shown as the camshaft form-fitting elements 7 in this case as protrusions 15 are formed on the radially outer surface of the camshaft 4 are distributed uniformly in the circumferential direction. It becomes clear how the projections 15 axially have a significantly longer value than in the circumferential direction or in the radial direction between 20% and 75%, preferably 50% have their extent in the circumferential direction. This embodiment also has six symmetrically arranged projections 15 on. It can be seen that the wave shoulder 18 radially outwardly protrudes than the projections 7 , Thus, there is enough contact surface for the biasing element 8th guaranteed in the proximal direction.

LIST OF REFERENCE NUMBERS

1

 Phaser

2

 stator

3

 rotor

4

 camshaft

5

 Rotor inner surface

6

 Rotor interlocking element

7

 Camshafts interlocking element

8th

 biasing member

9

 rotor blades

10

 stator vanes

11

 fluid chamber

12

 Camshafts fluid channel

13

 Rotor fluid channel

14

 distal end portion

15

 head Start

16

 indentation

17

 connecting element

18

 shaft shoulder

19

 proximal end face

20

 distal end

21

 limiting element

22

 ring groove

23

 circlip

24

 Rotor outer surface

25

 adjustment

QUOTES INCLUDE IN THE DESCRIPTION

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Cited patent literature

• DE 102010046619 A1 [0002]
• DE 102008032949 A1 [0003]
• DE 102012200099 A1 [0004]
• DE 10134320 A1 [0005]
• EP 1471215 A2 [0006]

Claims (10)

Adjustment system ( 25 ), comprising a camshaft adjuster ( 1 ) and a camshaft ( 4 ), wherein the camshaft adjuster ( 1 ) one radially inside a stator ( 2 ) arranged rotor ( 3 ), which relative to the stator ( 2 ) is rotatable, wherein the rotor ( 3 ) and the stator ( 2 ) Fluid chambers ( 11 ), which can be filled by means of a hydraulic fluid, wherein the camshaft ( 4 ) Camshaft fluid channels ( 12 ) and the rotor ( 3 ) Rotor fluid channels ( 13 ), wherein the camshaft ( 4 ) and the rotor ( 3 ) are rotatably connected to each other via a positive connection, characterized in that the camshaft fluid channels ( 12 ) and the rotor fluid channels ( 13 ) are formed in the region of the form-locking causing sections. Adjustment system ( 25 ) according to claim 1, characterized in that the rotor fluid channels ( 13 ) in the region of the rotor form-fitting elements ( 6 ) are arranged. Adjustment system ( 25 ) according to one of claims 1 or 2, characterized in that the camshaft fluid channels ( 12 ) in the region of the camshaft form-fitting elements ( 7 ) are arranged Adjustment system ( 25 ) according to one of claims 1 to 3, characterized in that the rotor fluid channels ( 13 ) and / or the camshaft fluid passages ( 12 ) are arranged in the region of an axially extending edge of one of the positive-locking portions or adjacent thereto. Adjustment system ( 25 ) according to one of claims 1 to 4, characterized in that the camshaft fluid channels ( 12 ) are such that they can be connected at their radially inner end with a central valve. Adjustment system ( 25 ) according to one of claims 1 to 5, characterized in that an angular orientation between the rotor ( 3 ) and the camshaft ( 4 ) is made on the positive connection. Adjustment system ( 25 ) according to one of claims 1 to 6, characterized in that per rotor form-locking element ( 6 ) one, two or more rotor fluid passages ( 13 ) extend radially. Adjustment system ( 25 ) according to one of claims 1 to 7, characterized in that between the flanks of the rotor form-fitting elements ( 6 ) and the flanks of the camshaft form-fitting elements ( 7 ) A leakage gap is formed. Adjustment system ( 25 ) according to one of claims 1 to 8, characterized in that a distal end portion ( 14 ) is designed as a hollow shaft. Adjustment system ( 25 ) according to one of claims 1 to 9, characterized in that the camshaft form-fitting elements ( 7 ) with the rotor form-fitting elements ( 6 ) are in engagement, whereby the torque-transmitting positive connection is achieved, wherein the rotor form-fitting element ( 6 ) and the camshaft mold element ( 7 ) each have a height in the radial direction, said height is not identical.

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