DE102013022320A1 - Connection of an adjusting actuator to a central valve system for a dry belt drive - Google Patents

Abstract

The invention relates to a camshaft staggering frame (1) with a vane type camshaft adjuster (2) in which a central valve (3) distributing a pressure fluid is present, and an adjusting actuator (4) acting on the central valve (3) controlling the distribution of pressure fluid the camshaft adjuster (2) is driven or drivable by means of a dry running traction drive, wherein the Verstellaktuator (4) at a connection point (47) on a combustion engine housing fixed component (22) is mounted or attachable, and with a component of the camshaft adjuster (2) via a Coupling element (49) is in communication with the coupling element (49) is formed and arranged, and / or the connection point (47) is formed so that tumbling movements in the radial direction of the camshaft adjuster (2) from the combustion engine housing fixed component (22) are decoupled a stator-fixed cover component (25) in the form of a Cavity enclosing spring cover for receiving a return spring (30) configured and arranged. The invention also relates to a drive train for a motor vehicle with such a camshaft Verstellstemstem (1).

Description

Field of the invention

The invention relates to a camshaft adjusting system, which can also be referred to as a kit, with a camshaft phaser of the vane type, in which a pressurized fluid, such as oil, distributing central valve is present, and with a Verstellaktuator, such as an electrically actuated Zentralmagnetaktuators on the central valve controlling the pressure fluid distribution, wherein the camshaft adjuster is driven or drivable by means of a dry running traction drive, such as a belt, wherein the Verstellaktuator is attached or attachable to a connection point on a combustion engine housing fixed component, and with a component of the camshaft adjuster via a coupling element in connection stands, wherein the coupling element is designed and arranged, and / or the connection point is formed so that wobbling movements in the radial direction of the camshaft adjuster from the internal combustion engine housing are decoupled solid component. The invention also relates to a drive train for a motor vehicle, with such a Nockenwellenverstellsystem / kit, with a dry-running traction drive, such as a belt drive that drives the stator of the camshaft adjuster at least in the operating state, and with a combustion engine housing fixed component, such as a cylinder head housing or the traction drive enclosing Zugmittelkasten, wherein the Verstellaktuator is attached to the combustion engine housing fixed component.

Various designs of kits / Nockenwellenverstellern / Nockenverstellanordnungen / Nockenverstellsystemen are already known from the prior art. From the EP 1596040 A2 is a camshaft adjuster for adjusting and fixing the phase position of a camshaft of an internal combustion engine with respect to a phase angle of the crankshaft known. The camshaft adjuster has a driven by the crankshaft drive wheel, and a camshaft fixed output member, wherein the output member is mounted on a camshaft or an extension of the camshaft. The output member is also driven by the drive wheel via a hydraulic actuator. The actuator consists of at least one pair of hydraulic pressure chambers working against each other. The pressure chambers are supplied with pressure medium via a pressure medium distributor and pressure medium lines. The pressure medium distributor and the camshaft adjuster together with a cylinder-head-fixed component form a camshaft thrust bearing.

A disadvantage, however, which is known from the prior art is that the Verstellaktuator is usually relatively rigidly connected to the camshaft adjuster, for example via a seal, with the central valve. By means of this relatively rigid connection, if the camshaft experiences strong dynamic loads during operation of the internal combustion engine, the camshaft adjuster can move / shift relatively far, in particular in the radial direction, for the adjusting actuator. As a result, in particular the attachment points of the Verstellaktuators, which are connected to a combustion engine housing fixed, such as cylinder head or belt chest fixed section, heavily loaded. In special cases, under extreme loads on the internal combustion engine, it may even lead to damage Verstellaktuator connection to the combustion engine housing fixed component, since the combustion engine housing fixed component is usually very rigid and is not very flexible.

From the DE 10 2008 051 145 A1 is also a camshaft adjuster with a belt drive for an internal combustion engine, comprising a stator driven by a crankshaft of the internal combustion engine via a belt, a rotatably connected to the camshaft rotor disposed between the stator and the rotor and acted upon by an oil pressure working chambers passing through the rotor assigned wings are divided into opposing pressure chambers, known, being provided for controlling the oil pressure in the pressure chambers of the working chambers, a central valve with a longitudinally displaceable guided in the central valve piston, which is acted upon by a drive side of the camshaft adjuster of an actuator with a force, and the camshaft adjuster has at its drive side a seal which prevents the escape of the oil flow in the belt drive receiving space.

Also, a seal assembly from the DE 42 09 953 A1 known. There is a seal assembly for sealing a through the bore of a wall-guided shaft, comprising a radial shaft sealing ring which sealingly seals the shaft to be sealed with at least one sealing lip made of elastomeric material under radial prestress. The sealing lip is fixed to a radially inwardly pointing first leg of a substantially L-shaped first stiffening ring, wherein the second leg extends in the axial direction, is encased in elastomeric material at least in the region of its axial boundary and sealingly touches the wall under radial bias , In the radial direction between the shaft and the second leg is a rolling bearing It is thus an object of the present invention to overcome the disadvantages known from the prior art and to provide a camshaft adjuster, through which the durability of the Verstellaktuators is significantly improved and the number of components is reduced.

Disclosure of the invention

This is inventively achieved in that the statorfeste cover member in the form of a cavity surrounding a spring cover, for receiving a return spring of the camshaft adjuster, designed and arranged.

Then, for example, a component already connected to the camshaft adjuster at the same time can also serve as a camshaft adjuster-side spring retainer. In this case, a spring cover is preferably fixedly connected to a side wall of the stator and arranged rotationally fixed thereto.

As a result, in particular the loads which are detrimental in the radial direction for the attachment of the adjusting actuator are only very strongly damped / not transmitted to the region of the housing-fixed component receiving the adjusting actuator. As a result, this area is particularly relieved and the probability of failure of the Verstellaktuators used significantly reduced.

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

Thus, it is also possible that the statorfeste cover member has a stator facing the sealing contour, which is sealingly attached to a side wall of the stator and seals the cavity from the environment. This makes an additional seal easy to implement. For example, the seal may be configured as a bead seal, such as a sheet-metal bead seal. Thus, for example, an elevation, which preferably runs around the entire circumference of the cover component, can be formed on the side of the seal cover facing the stator, for example by means of a sheet metal forming process. This survey is then in the operating state form, force and / or cohesively engaging in a recess of the lid member facing side of the side wall of the stator. Preferably, the survey is pressed into the recess.

If the coupling element is formed as a combination component of a seal and a roller bearing or as a sliding, at least in the radial direction compressible seal, so efficient movement decoupling between the internal combustion engine housing fixed component, such as a cylinder head housing or the dry traction engine haven belt box / receiving space, and the camshaft adjuster be implemented.

In this context, it is also advantageous if the coupling element between a camshaft adjuster fixed component and the internal combustion engine housing fixed component is arranged. If the coupling element is arranged in such a way, then preferably this coupling element can also be used as a replacement for an otherwise separately used seal between the combustion engine housing-fixed component and the camshaft adjuster-fixed component. This further reduces the number of components.

In this context, it is also advantageous if the coupling element seals a Druckfluidverteilraum the camshaft adjuster relative to the environment of the camshaft adjuster. As a result, the surroundings of the camshaft adjuster in which the dry-running traction mechanism drive is usually arranged can be sealed by the coupling element. Thus, the coupling element takes on two tasks at the same time, namely the task of the seal, as well as the task of storage between the Verstellaktuator and the camshaft adjuster. This can further reduce the number of components.

Furthermore, it is also possible that the Verstellaktuator is attached or attachable at its junction with at least one screw on the internal combustion engine housing fixed component, and / or the at least one screw as a screw, such as a threaded bolt configured, at least in the combustion engine housing fixed component with a first threaded portion is firmly screwed or screwed. In this way, simply and efficiently the adjusting actuator can be arranged in a stationary manner on the component that is fixed to the combustion engine housing. This allows a direct coupling between the Verstellaktuator and the cylinder head housing / the belt box. Component complexity is thereby further reduced. In the case where the screw is both firmly screwed into the combustion engine housing fixed component, as well as the Verstellaktuator. About its screw head firmly pressed against the housing-fixed component, the coupling element is preferably designed as a sliding seal / a sealing ring / Simmering. The seal can, in this case, continue to be designed such that its sealing lips also move relative to the adjustment actuator Camshaft adjuster fixed component always seal the Druckfluidverteilraum against the environment of the camshaft adjuster. It is also possible in another case, when the screw is screwed to the housing-fixed component such that at least one threaded portion firmly engages in the combustion engine housing-fixed component, while another portion of the screw has a clearance for Verstellaktuator, for example, a game in Axial- and / or radial direction. As a result, the adjusting actuator can tilt / twist / shift by the backlash relative to the combustion engine housing-fixed component. The coupling element can then be used not only as a seal, but also as a roller bearing, and in this case connect the camshaft adjuster fixed component with the Verstellaktuator in the radial direction taumelfest. In both cases, therefore, a particularly efficient way of decoupling is feasible.

If, in addition, the adjusting actuator is attached or attachable to the combustion-engine-housing-fixed component at the connection point in the axial and / or radial direction, the connection point is designed to be particularly tolerant of wobbling movements.

It is also possible for the adjusting actuator to be centered or arranged at the connection point, for instance by means of at least one dowel pin, for the component that is fixed to the combustion engine housing. Thereby, the Verstellaktuator can be centered in a simple way to the combustion engine housing solid component, this centering can be configured so that the Verstellaktuator is also optimally centered to the camshaft adjuster, which is already given when initiating the operating state, a centered connection between the Verstellaktuator and the camshaft adjuster. This further reduces the risk of misalignment and thereby damage to the Verstellaktuators / the housing-fixed component.

If the Verstellaktuator at the junction of the combustion engine housing solid component in the circumferential direction positively engages behind, as by a fork-groove connection, a spielaufweisende, counter to the direction of rotation of the camshaft adjuster bracket is achieved in a simple manner. This ensures in a simple manner that the Verstellaktuator on the one hand not directly rigid and firmly connected to the internal combustion engine housing fixed component, and on the other hand not undefined with the camshaft adjuster with rotates.

In a further variant, it is advantageous if between the camshaft adjuster and a housing of the Verstellaktuators via the central valve filled with pressurized Druckfluidverteilraum is provided which is sealed by a seal between the camshaft adjuster and the Verstellaktuator to the environment, the seal on the one hand a statorfesten cover component is in plant and on the other hand is located with a housing-fixed component in plant.

It is also advantageous if the statorfeste cover member and / or the housing-fixed component are positioned concentrically to a rotational axis of the camshaft adjuster and / or the statorfeste cover member is rotatable about the axis of rotation relative to the housing-fixed component. By this arrangement, advantageously, a seal for a simple, centered sealing system can be provided, which can be designed in the manner of a sliding seal / sliding seal.

Furthermore, it is advantageous if the seal on the part of the housing-fixed component on one of the axis of rotation facing or facing away from the sealing side edge of an axially extending annular element of the housing-fixed component and / or the seal on the part of the statorfesten cover component on one of the axis of rotation facing or facing away from the sealing side edge a ring member extending in the axial direction of the stator-fixed cover component rests. By the molding of such ring elements to the stator fixed cover component and / or to the housing-fixed component are connected in a simple manner integrally connected with these components sealing side edges. As a result, the component complexity can be further reduced and the manufacturing costs can be favorably influenced.

It is also advantageous if the sealing side edge of the housing-fixed component is arranged radially outside or radially inwardly of the sealing side edge of the stator-fixed cover component. Thus, the sealing side edges can be positioned overlapping in a compact design, between which the seal is arranged. Thus, a space required for the seal space is designed to save space.

It is also advantageous if the seal is attached in a rotationally fixed manner on the part of the sealing side edge of the stator-fixed cover component and / or on the part side of the sealing side flank of the housing-fixed component is designed as a sliding seal which is rotatable relative to the housing-fixed component at least in the operating state. As a result, the seal can continue to be designed particularly powerful. The seal can be designed to be particularly stable in the region which is non-rotatably against the stator-fixed cover component, while another region of the seal on the part of the housing-fixed component can be configured in a simple manner as sliding seal and therefore optimal for the Relative movements between the housing and the camshaft adjuster is designed. The side of the seal, which is applied to the housing-fixed component, can thus be configured friction-optimized. If the seal continues to be designed as a ring seal, such as a simmering ring, and / or a supportive reinforcing ring is integrated in the seal, a particularly durable seal can be implemented.

According to a further embodiment, the seal may be designed so that it adapts in the operating state in geometry at least to a radial axis offset between the statorfesten cover member and the housing-fixed component. The axial offset caused essentially by radial wobbling movements of the camshaft and the camshaft adjuster relative to the Verstellaktuator often leads to the fact that the probability of leakage of the seal increases during operation, especially at high dynamic loads of the camshaft. This implementation can significantly reduce this probability.

According to a further variant, it is also advantageous if a pressure fluid distribution space which can be filled via the central valve with pressure fluid is present and at least one pressure fluid return line is introduced into the rotor, the pressure fluid return line extending substantially in the axial direction / axial direction of the axis of rotation of the camshaft adjuster. If, in addition, the pressure fluid return line connects to an initial section on an axial side of the central valve facing the adjusting actuator on the central valve, a particularly compact construction of the line system providing the pressure fluid distribution can be configured.

According to a further embodiment, it is advantageous if the pressure fluid return line adjoins the central valve at an axial side of the central valve facing the adjusting actuator. As a result, a particularly compact design of the pressure fluid distribution making available line system can be configured.

It is also advantageous if the pressure fluid return line extends in the axial and / or radial direction from the Druckfluidverteilraum in the Verstellaktuator inside. Thus, the Verstellaktuator can be supplied with pressurized fluid. On the one hand, this has the advantage that the adjusting actuator is likewise lubricated. For example, the electromagnetically operable actuator pin / plunger, which then pushes the central valve from a first position to a second position, can be lubricated with fluid. On the other hand, the pressure fluid then serves as a coolant and can be passed through the Verstellaktuator, so that the electrically powered coil and its periphery is cooled. As a result, in particular the performance of the adjustment actuator can be further increased.

In addition, a pressure fluid supply line may also connect to the central valve on a side of the central valve facing away from the adjusting actuator. As a result, there is an even more pronounced spatial separation between Druckfluidzu- and Druckfluidabführleitung. The adjusting actuator can then be arranged on the output side directly next to the central valve, and even form the leading away from the central valve pressure fluid return line. This has particular fluidic advantages, since the Druckfluidzuführleitung can be performed over a short distance directly to the central valve input and only after flowing through the pressure fluid through the central valve and the control of the pressure chambers, the pressure fluid is then passed through the pressure fluid return line. Thus, in particular the flow of the pressurized fluid to the central valve is further optimized hydrodynamically.

According to a further advantageous embodiment, it is also possible that the pressure fluid return line is connected to a return spring of the camshaft adjuster receiving cavity. As a result, the cavity receiving the return spring can also be supplied with pressurized fluid and the return spring can be surrounded by pressurized fluid. This helps in particular to significantly dampen unwanted resonance effects of the return spring in certain operating conditions, since the pressure fluid can act on the dynamically aufschauernden in some operating conditions return spring damping.

It is also possible that the central valve is arranged concentrically to the axis of rotation of the camshaft adjuster, and / or the pressure fluid return line extends in the radial direction spaced from the central valve in the rotor and / or the pressure fluid return line extends in the axial direction continuously through the rotor. As a result, the central valve is fixed centrally and the pressure chambers formed between the rotor and the stator can be supplied with pressurized fluid / fluid as short as possible. Due to the centric arrangement, the pressure chambers are also supplied uniformly with the fluid. If the pressurized fluid return line is further offset from the central valve, the pressurized fluid return line can be guided to the tank at a different (eccentric) point of the camshaft adjuster, essentially parallel to the central valve, independently of the design and constructional dimensions of the central valve. As a result, the adjustment actuator facing side of the Camshaft adjuster free of outlets or inlet holes for connecting the Druckfluidrück- or Druckfluidzuführleitungen be configured. This further reduces the likelihood of leakage in the region between the Verstellaktuator and the camshaft adjuster.

It is also expedient if the pressurized fluid return line runs in the axial direction through a radial bearing provided for receiving the camshaft, such as a plain bearing or a roller bearing, and / or the pressurized fluid return line terminates in an opening which can be connected to a tank and which extends in the radial direction is that it extends in the installation position of the camshaft adjuster up / a direction opposite to the acting gravity. Due to the course of the pressurized fluid return line in the axial direction by a radial bearing can be saved significantly space and omitted in particular in the radial bearing on additional fluid channels. As a result, the production costs are further reduced. For example, could be used in the rolling bearing already existing between the arranged in a cage rolling elements existing space for fluid passage.

The embodiments for the pressurized fluid return line also apply to the pressurized fluid supply line.

If the pressurized fluid return line is further provided with an opening directed upwards / against the acting gravity and, for example, mounted in a component fixed to the cylinder head housing, pressurized fluid from the system is avoided in every position of the camshaft adjuster, for example when the internal combustion engine is at a standstill the central valve runs out and possibly air, or other gases are introduced into the system. In addition, the pressure fluid return line can also be used simultaneously as a vent line, by means of the pressure fluid in the circuit located gases, such as air, can be discharged.

It is also advantageous if the Druckfluidverteilraum is sealed from the environment of the camshaft adjuster. The environment, which is, for example, a receiving space of the camshaft adjuster / the stator of the camshaft adjuster driving (dry / dry running) traction drive can thus be securely sealed and is independent of the fluid delivery circuit. An undesirable filling of the receiving space of the dry running traction drive is avoided.

It is a further advantage if the central valve has at least one pressure chamber line which extends in the radial direction and which can be fluid-conductively connected to at least one pressure chamber arranged between the rotor and the stator, wherein a cover reservoir is preferably connected to the central valve and is in the operating state the camshaft adjuster compensates in the pressure chamber occurring pressure fluctuations. In particular, by the overlap memory negative pressure phenomena are avoided at high dynamic loads of the camshaft adjuster and thus the pressure chambers. These negative pressure phenomena occur, for example, in the case of rapid actuations or changes in the motion of the camshaft adjuster, which may cause the system to swing up undesirably. Through the overlap memory is always enough pressure fluid with the required pressure available to quickly resolve these fluctuations and compensate for the disadvantages.

According to a further advantageous variant, it is also advantageous if there is a bearing component connected to a combustion engine housing fixed, such as a cylinder housing or tensioning drive housing fixed, wherein the bearing component is designed at least for the radial mounting of a camshaft and wherein the traction drive as a dry running traction drive, such is designed as a belt / belt drive and preferably the bearing member is disposed on a side facing away from the Verstellaktuator or facing the camshaft adjuster. This allows a particularly efficient storage of the camshaft to the camshaft adjuster.

It is also advantageous if a seal is arranged between the bearing component and a camshaft adjuster-fixed component, which seals the pressure fluid distribution to the surroundings of the camshaft adjuster. In this context, a particularly efficient storage-seal combination is then provided, which allows the seal separately from the storage and thus enables a particularly leak-proof distribution of pressurized fluid.

It is also advantageous if a circumferential surface of the bearing member is configured as a can be brought into contact with the camshaft slide bearing surface for configuring a sliding bearing of the camshaft on the bearing member and / or arranged to form a roller bearing on the bearing member a rolling bearing, which is arranged for radial mounting the camshaft to the bearing member can be pushed onto the camshaft. As a result, in an operating state of the camshaft adjuster, the bearing component can either be connected directly to the camshaft by means of a sliding bearing surface or be regarded as a bearing possibility accommodating a roller bearing, the respective advantages of these bearing arrangements can also be used for the camshaft adjuster according to the invention.

In addition, it is also possible for the bearing component to have at least one pressure fluid channel extending substantially in the radial direction, through which pressure fluid can be supplied to the central valve or can be discharged from the central valve by the pressure fluid. As a result, a supply line or a discharge line can be integrated into the storage component; alternatively, both lines can also be integrated without having to arrange additional components which supply or discharge the pressurized fluid. As a result, the number of components can be further reduced.

It is also advantageous if the bearing component has at least one pressure fluid channel extending essentially in the radial direction and configured as a pressure fluid supply channel and / or as a pressure fluid discharge channel. On the one hand, a pressurized fluid supply system, which is connected, for example, to a pump, can be placed directly on the mounting component by means of the radially extending pressure fluid ducts, whereby the component complexity is further reduced. In addition, if the Druckfluidabführkanal extends substantially axially, it is possible to remove the pressure fluid in another radial region of the camshaft adjuster again from the central valve, thus ensuring a clear separation between the feed and discharge channels. As a result, a particularly efficient pressure fluid conveying system can be implemented.

It is also possible for the bearing component to have at least one stop flank extending in the radial direction for the axial bearing of the camshaft, wherein a stop region of the camshaft can be brought into contact with this stop flank. As a result, not only a radial bearing of the camshaft, but also an axial bearing with the same bearing component is possible. The number of components is thereby further reduced.

Also, the support member may be rotatably connected to the Verstellaktuator. For example, these two components could be mounted together on a combustion engine housing fixed component, such as a cylinder head housing or a belt box, which in particular the installation and the application of the camshaft adjuster are significantly facilitated.

In further advantageous embodiments, it is also possible to design a drive train for a motor vehicle, such as a car, a truck or a bus with a Nockenwellenvertstellsystem or a kit at least one of the above variants. This drive train then preferably also has a camshaft, which is connected at least in the operating state with the rotor of the camshaft adjuster. Also, the drive train may have a dry running traction drive, such as a belt drive, wherein the Zugmittetrieb drives at least in the operating state, the stator of the camshaft adjuster. The camshaft is in this context preferably a camshaft of an internal combustion engine, such as a gasoline or diesel engine and the traction drive is preferably connected to a crankshaft of this internal combustion engine. The drive train may also have a component that is fixed to the combustion engine housing, such as a cylinder head housing or a traction mechanism box enclosing the traction mechanism drive, wherein the adjustment actuator is attached to the component that is fixed to the combustion engine housing. The internal combustion engine housing-fixed component is preferably generally a component mounted in an internal combustion engine or on the housing of this internal combustion engine. Preferably, the camshaft is rotatably received and / or stored in the bearing component. The camshaft preferably further comprises a tubular portion which is formed as a pressure fluid delivery channel and fluidly connected to the central valve. Thus, a particularly efficient design of a drive train is possible.

The invention will now be explained in more detail by means of various embodiments with reference to drawings.

Show it:

1 a longitudinal section through a camshaft adjusting system in an operating state according to a first embodiment, which section along a sectional plane in which the axis of rotation of the camshaft adjuster is carried out, the Verstellaktuator is fixed to a combustion engine housing fixed component and with a arranged between it and the camshaft adjuster seal means an adjusting actuator housing component is in abutment,

2 a longitudinal section of a further variant, wherein the longitudinal section according to the in 1 performed longitudinal section, and is the same range of camshaft adjustment system as 1 in which the seal on the part of the adjusting actuator is in contact with the adjusting actuator by means of a guide sleeve guiding an adjusting tappet of the adjusting actuator,

3 a longitudinal section through a camshaft adjusting system of a further variant, which section according to the longitudinal sections of the 1 and 2 is performed, with a alternatively configured seal, which is arranged between the Verstellaktuator and the camshaft adjuster is executed, wherein the seal with respect to the number of their density bumps, which abut the Verstellaktuator, from the in 2 distinguished seal,

4 a longitudinal section through a camshaft adjusting system of a further variant, which section is performed according to the longitudinal sections of the previous figures, wherein the kit substantially according to the camshaft adjusting system according to 1 is executed, however, in the area of the seal from the variant 1 differs, and arranged between the Verstellaktuator and the camshaft adjuster seal is fitted with a side on a camshaft adjuster / fixed stator component in the radial direction and is applied with their adjusting actuator side facing the Verstellaktuator,

5 a longitudinal section through a camshaft adjusting system of a further variant, which section is performed according to the longitudinal sections of the previous figures, wherein the camshaft adjusting system substantially according to the variant of 4 is designed, however, in the field of sealing of the variant 4 differs, wherein in the seal a reinforcing member is integrated,

6 a longitudinal section through a camshaft adjusting system of another variant, which section is performed according to the longitudinal sections of the previous figures, wherein the arranged between the Verstellaktuator and the camshaft adjuster seal is not directly with the Verstellaktuator, but on a fixedly connected to the Verstellaktuator combustion engine housing component in Appendix,

7 a longitudinal section through a camshaft adjusting system of a further variant, which section is performed according to the longitudinal sections of the previous figures, wherein the camshaft adjusting system substantially according to the camshaft adjusting system according to 1 is executed, however, in the area of the seal from the variant 1 differs, and the voltage applied to the sealing region of the Verstellaktuators is arranged in the radial direction outside to the gasket contacting area of the statorfesten component,

8th a longitudinal section through a camshaft adjusting system of a further variant, which section is performed according to the longitudinal sections of the previous figures, wherein the camshaft connected to the rotor is designed as a tubular camshaft at least in one end, which extends completely through the rotor in its axial length,

9 a longitudinal section through a camshaft adjusting according to 4 in which the pressurized fluid line is shown here in the operating state of the camshaft adjusting system,

10 a longitudinal section through a camshaft adjusting system of a further variant, which section is performed according to the longitudinal sections of the previous figures, wherein the pressure fluid flow is illustrated and a bearing member which in 9 sliding bearing is connected to the camshaft, is connected by means of a rolling bearing with the camshaft, wherein the pressure fluid flow in the axial direction passes through this bearing,

11 a longitudinal section through a camshaft adjusting system of a further variant, which section is performed according to the longitudinal sections of the previous figures, wherein the pressurized fluid, as already in 10 , not by the bearing member, which is directly connected to the camshaft adjuster, but is passed through a rear mounted in internal combustion engine position bearing,

12 a longitudinal section through a camshaft adjusting according to 10 but without the arrow lines representing the pressure fluid flow.

13 a longitudinal section through a camshaft adjusting a further variant, which section is carried out according to the longitudinal sections of the previous figures, wherein between the Verstellaktuator and the camshaft adjuster a coupling element is present, which includes a rolling bearing and a seal and the Verstellaktuator relative to the cylinder head housing fixed component play in radial and axial direction is arranged

14 a longitudinal section through a camshaft adjusting system of a further variant, which section is performed according to the longitudinal sections of the previous figures, wherein a tubular cam shaft end completely through the camshaft adjuster, and this camshaft end is slidably mounted to a axially disposed between the Verstellaktuator and the camshaft adjuster mounting member,

15 a longitudinal section through a camshaft adjusting system of a further variant, which section is performed according to the longitudinal sections of the previous figures, wherein the camshaft adjusting substantially in accordance with the Nockenwellenverstellsystems 14 designed is, however, having a Fluidleitring formed at least one axially extending fluid passage on the outer side of the camshaft, and

16 a longitudinal section through a camshaft adjusting system of a further variant, which section is performed according to the longitudinal sections of the previous figures, wherein the camshaft adjusting system substantially like the camshaft adjusting the 15 is executed, the bearing between the camshaft and the cylinder head fixed component but via a roller bearing instead of the sliding bearing 15 , namely a roller / needle roller bearing is executed.

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

In the 1 to 16 are different embodiments of a camshaft adjusting system / kit according to the invention 1 shown, this system is also denoted as a camshaft adjustment kit or Nockenwellenverstellanordnung. The camshaft adjusting system or the kit 1 is shown in all these figures in a longitudinal section, wherein in the sectional plane, the axis of rotation 11 of the camshaft adjusting system 1 lies around which axis of rotation 11 the camshaft adjusting system 1 rotates at least in one operating state. The camshaft adjustment system 1 is in a drive train of a motor vehicle, such as a car, truck, or bus, used and with a camshaft 13 and a crankshaft of an internal combustion engine, such as a gasoline or diesel engine, connectable. The camshaft adjustment system 1 includes a camshaft adjuster 2 essentially in accordance with the camshaft adjuster / device for changing the timing of gas exchange valves of an internal combustion engine, as known from WO 03/085238 A1 known is built and works. The camshaft adjuster 2 The type of the invention is therefore a camshaft adjuster 2 of the wing cell type. In the camshaft adjuster 2 is centrally a pressure fluid distributing central valve 3 present / disposed. The central valve 3 is designed as a screw / screw, wherein in a cavity of the screw designed as a central valve 3 a valve mechanism for separating or connecting an input-side Druckfluidzuführleitung 53 with in the camshaft adjuster 2 configured (not shown here) pressure chambers, is arranged.

Furthermore, one is the central valve 3 controlling adjusting actuator 4 available. The adjusting actuator 4 is with its longitudinal axis substantially coaxial with the axis of rotation 11 and also coaxial with the longitudinal axes of the camshaft adjuster 2 and the central valve 3 arranged. The camshaft adjuster 2 has a rotatable in a stator 5 mounted rotor 6 on. At the stator 5 of the camshaft adjuster 2 engages for reasons of clarity not shown dry running traction mechanism, such as a belt drive, positive or non-positive on the outside of the stator 5 one. The stator 5 Preferably takes a dry-running belt drive and is driven by this.

Between the camshaft adjuster 2 and a Verstellaktuatorgehäuse 7 of the adjusting actuator 4 , below only as a housing 7 is one above the central valve 3 with Druckfluid fillable Druckfluidverteilraum 8th present / disposed. The pressure fluid distribution space 8th is about a seal 9 that is between the phaser 2 and the Verstellaktuator 4 is arranged to the environment, ie to an outdoor area 10 of the camshaft adjuster 2 is sealed off. This outdoor space 10 is a space that faces outward through a belt box or an internal combustion engine housing 22 as a cylinder head housing, is wrapped and preferably fluid-tightly sealed or sealable to all Be.

As also generally seen in the figures, the central valve is 3 with its longitudinal axis always coaxial with the axis of rotation 11 of the camshaft adjuster 2 arranged. A valve position changing valve piston 12 of the central valve 3 is along the axis of rotation 11 Slidably mounted in the axial direction. The central valve 3 , which is designed as a Schaub element is in the illustrated operating state of the camshaft adjustment system 1 in which the camshaft adjustment system 1 assembled and at least with a camshaft 13 rotatably connected, (rotating) fixed to the rotor 5 connected. At one the adjusting actuator 4 (in the operating state) facing side is the valve piston 12 of the central valve 3 freely accessible / exposed.

In the in 1 variant shown is a threaded portion of the central valve 3 in a female threaded portion of the camshaft 13 screwed. The camshaft 13 lies with a front side 14 at a radially extending first counter-holding surface 15 of the rotor 6 on and is with this front page 14 axially against the first counter-holding surface 15 pressed. To apply one of these pressing force counteracting counterforce is the central valve 3 again with a side elevation extending in the radial direction 16 on a second counter-surface 17 of the rotor 6 at. Also the second counterhold area 17 extends in the radial direction. Thus, the camshaft 13 in the axial direction fixed to the rotor 6 and to the central valve 3 secured / maintained.

The adjusting actuator 4 is basically designed as an electrically actuated / electromechanically actuated central magnet (adjustable) actuator. The adjusting actuator 4 has a substantially concentric with the axis of rotation 11 arranged actuating tappet 18 on, at the level of the valve piston 12 is arranged and with the valve piston 12 interacts. Next to the actuating tappet 18 has the Verstellaktuator 4 at least one guide sleeve 19 on that the actuating tappet 18 secures in the radial direction and axially displaceable supports. The guide sleeve 19 lies for this purpose with sliding surfaces on the outer circumference of the actuating plunger 18 , wherein the actuating plunger 18 in the axial direction to the central valve 3 to or from the central valve 3 can be moved away. For axially moving the actuating tappet 18 is in a simple way an electrically controllable coil 20 present in the housing 7 of the adjusting actuator 4 is held and at least in a valve position, the position of the actuating plunger 18 provides influencing magnetic field. The sink 20 is in the radial direction between the guide sleeve 19 (radially inside) and the housing 7 (radially outboard) arranged and enclosed by these two parts. An outer wall of the housing 7 thus surrounds the coil 20 at least in sections. The housing runs, such as in 1 shown in cross-section, both in the axial direction along an outer peripheral region of the coil 20 as well as in the radial direction from this outer peripheral region inwards, to the guide sleeve 19 out.

The housing 7 is in turn with at least one fastening screw 21 with a combustion engine housing fixed component 22 , here a cylinder-head-proof component 22 firmly connected. The cylinder head resistant component 22 is shown here only in sections and runs preferably, the camshaft adjuster 2 enclosing around the camshaft adjuster, so that the belt drive not shown here directly through this cylinder head fixed component 22 is enclosed in a fluid-tight manner.

At one of the camshaft adjuster 2 / the stator 5 facing side of the Verstellaktuators 4 is to the case 7 , according to the embodiment of the 1 , an annular, coaxial along the axis of rotation 11 extending (actuator side) ring element 23 formed. This actuator-side ring element 23 is takes on a radial outside, ie one of the axis of rotation 11 opposite side / an outer peripheral surface of the seal 9 on. The seal 9 lies with a first sealing lip 24 that the actuator-side ring element 23 facing the entire circumference of the actuator-side ring element 23 sealing on the actuator-side ring element 23 at. The outer peripheral surface of the actuator-side ring element 23 thus formed a first side of the sealing side, at which the seal 9 the pressure fluid distribution space 8th opposite the outside space 10 of the camshaft adjuster 2 seals.

The seal 9 to 1 is substantially, viewed in cross section, U-shaped, wherein the first sealing lip 24 forms the first arm of the Us. The seal 9 lies on the part of the first sealing lip 24 with a first, circumferentially extending survey on the Verstellaktuator 4 at. The second arm of the US, is located on an actuator side ring element 23 side facing away from a camshaft-fixed component, hereinafter as a stator fixed cover component 25 referred to. The seal 9 points to the second sealing lip 26 a plurality of elevations, which are arranged axially adjacent to each other and all in the circumferential direction of an annular ring member of the cover component 25 , hereinafter referred to as cover-side ring element 27 designated, abut. The cover-side ring element 27 Therefore, has an inner peripheral surface on which the second sealing lip 26 the seal 9 with the surveys. The second sealing lip 26 lies along the entire circumference of the cover component 25 on the inner peripheral surface of the lid-side ring element 27 and seals this against the environment, ie the outside space 10 , from. The lid component 25 , whose inner peripheral surface with the seal 9 cooperates, thus represents a second side edge seal.

According to the 1 is the outer peripheral surface of the actuator-side ring element 23 smaller in diameter than the inner peripheral surface of the cover-side ring member 27 designed. The two ring elements 23 and 27 are pushed into each other in the axial direction, wherein in the radial gap, the seal 9 is arranged. The pressure fluid distribution space 8th that is from the central valve 3 outflowing pressure fluid is further distributed / forwarded, is about the seal 9 / the two sealing lips 24 and 26 to the outside space 10 sealed. As continues in 1 is recognizable, is in the second sealing lip 26 a reinforcing ring 32 integrated. This reinforcement ring 32 runs along the circumferential direction, preferably around the entire circumference of the seal 9 around. The reinforcement ring 32 is preferably made of a metal, such as a metal sheet. The reinforcement ring 32 is preferably complete in both radial directions of an elastomeric base material of the second sealing lip 26 surround.

The lid component 25 as well as in 1 Illustrated particularly vividly, is still statorfest with the camshaft adjuster 2 connected. For this purpose, the lid member extends 25 , viewed in cross-section, from the cover-side ring element 27 away in the radial direction and in the axial direction to the stator 5 one Statorseitenwand 28 , go. The lid component 25 then lies with a flange-shaped section 29 preferably along its (entire) circumference surface with its the stator 5 facing side on a stator 5 opposite side of the stator side wall 28 at. This attachment point between the cover component 25 and the stator 5 is designed fluid-tight. For this purpose, as a seal, a (sheet metal) bead seal between the cover component 25 and the stator sidewall 28 executed, with an annular, on the stator 5 facing side of the cover component 25 extending elevation into a depression, which is at the stator 5 opposite side of the stator side wall 28 is introduced, is pressed. This results in a positive and non-positive connection, which also the Druckfluidverteilraum 8th opposite the outside space 10 seals.

Between the lid component 25 and the side wall 28 is one with the Druckfluidverteilraum 8th fluid-conducting connected cavity 31 designed. In this cavity is a common for the camshaft adjuster 2 the vane type used spring element / a return spring 30 added. The spring element / the return spring 30 is designed as a spiral spring. The spring element / the return spring 30 is in a known manner with one end to the stator 5 , with the other end to the rotor 6 connected and provides this, in an unloaded state of the camshaft adjuster 2 back to a starting position. The cavity 31 in which the spring element 30 is, is fluid-conducting with the Druckfluidverteilraum 8th connected to pressurized fluid around the spring element / the return spring 30 to pass around immediately.

In the 2 is now another variant of the camshaft adjustment system 1 shown, wherein the camshaft adjuster 2 on which the lid component 25 is attached, as well as the central valve 3 equal to the execution 1 are designed. Also the adjusting actuator 4 is largely the same design. The actuator-side ring element 23 is contrary to 1 not integral with the housing 7 of the adjusting actuator 4 but integrally connected to the guide sleeve 19 molded, which guide sleeve 19 as already mentioned, the axially displaceable actuating tappet 18 Positioned in the radial direction. The cover-side ring element 27 extends in the axial position of a central valve 3 facing end face of the guide sleeve 19 to the central valve 3 also lies with its outer peripheral surface at the first sealing lip 24 the seal 9 at. The diameter of the outer peripheral surface of the actuator-side ring element 23 is in turn chosen smaller than the inner peripheral surface of the cover-side ring element 27 ,

In 3 is another variant of the camshaft adjustment system 1 illustrated, wherein the Verstellaktuator 4 , the camshaft adjuster 2 as well as the central valve 3 equal to the execution 2 are designed. Across from 2 is just the seal 9 namely, its second sealing lip 26 executed in a different way. While the first lip of the seal 9 after the 1 and 2 on the part of the system in contact with the actuator-side ring element 23 located side only have a survey, so has the first sealing lip 24 the seal 9 , in the 3 is shown, a plurality of elevations, which are arranged in the axial direction next to each other and are separated by a plurality of grooves, which are also continuous surveys around the entire circumference of the seal 9 extend around. The first sealing lip 24 is therefore with several elevations on the outer peripheral surface of the actuator side ring element 23 at.

Also 4 represents a further variant of the camshaft adjusting system 1 wherein the Verstellaktuator 4 according to the adjusting actuator 4 to 1 is executed and also the camshaft adjuster 2 and the central valve 3 essentially after the camshaft adjuster 2 and the central valve 3 of the 1 are designed. Only the cover component 25 and the seal 9 are designed differently in this embodiment. Thus, according to this embodiment variant, the cover component 25 a differently configured cover-side ring element 27 on. While the lid-side ring element 27 the versions of the 1 to 3 extends substantially in the axial direction, the cover-side ring member extends 27 according to the 4 essentially in the radial direction. On an end face of the cover-side ring element 27 , the axis of rotation 11 is facing, is the seal 9 (non-rotatable) attached. For this purpose, the seal points 9 on the part of its second lip 26 a recess machined in the radial direction along the entire circumference of the seal 9 runs. In this recess is then the front side of the cover-side ring element 27 inserted. The first sealing lip 24 this embodiment corresponds to the first sealing lip of the 1 and is substantially with a protrusion on the outer peripheral surface of the actuator side ring member 23 fitting.

Another variant of the camshaft adjustment system 1 is in 5 shown, this camshaft adjustment system 1 basically according to the camshaft adjustment system 1 of the 4 is shown, but only in terms of the design of the seal 9 something from the camshaft phasing system 4 different. The second sealing lip 26 the seal 9 turn the reinforcing ring 32 , This reinforcement ring 32 is now essentially a cross-sectionally U-shaped shaped circumferential ring element. Also this reinforcement ring 32 may again be made of a metallic material. Also the reinforcement ring 32 is circumferentially in the second sealing lip viewed in the circumferential direction 26 integrated and of an elastomeric base material of the second sealing lip 26 surrounded / enclosed. The legs of the Us run substantially parallel to the side edges of the cover-side ring element 27 , on both sides of the end face of the cover-side ring element 27 and substantially in the radial direction. Thus surround / reinforce the legs of the reinforcing ring 32 the recess of the seal 9 ,

In 6 is another variant of the camshaft adjustment system 1 shown. According to 6 it is also possible the actuator-side ring element 23 no longer with a component of the Verstellaktuators 4 direct / one-piece / integral (as in the 1 to 5 ), but with an internal combustion engine housing fixed / cylinder head fixed component 22 connect to. An inner peripheral surface of the cylinder head fixed component 22 now forms the actuator-side ring element 23 out. The adjusting actuator 4 is substantially equal to the previous Verstellaktuator previously described 4 configured (fixed / rotationally fixed with the cylinder head fixed component 22 connected) and also the components of the camshaft adjuster 2 and the central valve 3 are executed according to the previous embodiments. The lid component 25 is essentially according to the embodiment according to 1 designed. The cover-side ring element 27 the lid component 25 is radially inside the inner peripheral surface of the cylinder head fixed component 22 arranged and therefore no longer by means of an inner peripheral surface of the seal 9 fitting but with an outer circumferential surface on the seal 9 fitting. The seal 9 lies with its the outer peripheral surface of the lid-side ring member 27 facing second sealing lip 26 by means of two elevations on the cover-side ring element 27 at. The cylinder head resistant component 22 thus extends in the axial and radial directions along the housing 7 of the adjusting actuator 4 to the lid-side ring element 27 towards, that the inner peripheral surface of the cylinder head fixed component 22 a sealing inner peripheral surface 33 forms at which sealing inner peripheral surface 33 the first sealing lip 24 the seal 9 sealingly rests. The first (the actuator-side ring element 27 facing) sealing lip 24 the seal 9 is preferably located over a relatively wide, large-scale survey on the inner sealing peripheral surface 33 of the cylinder head fixed component 22 at.

In 7 is another variant of the camshaft adjustment system 1 shown, wherein the camshaft adjustment system 1 is executed according to the embodiments of the previous figures, but in turn in the seal 9 and their gasket positioning is different. The adjusting actuator points to a housing 7 the actuator-side ring element 23 on, wherein the actuator-side ring element 23 again integral to the housing 7 is formed. In contrast to 1 is the ring element 23 now configured slightly larger in the radial direction and takes the cover-side ring element 27 in its inside. The cover-side ring element 27 thus extends in the radial direction offset from the actuator-side ring element 23 within the through the actuator-side ring element 23 designed interior. The seal 9 lies with her second sealing lip 26 again on an outer peripheral surface of the lid-side ring element 27 an elevation of this second sealing lip 26 in a recess in the outer peripheral surface of the lid-side ring member 27 is snapped. The first sealing lip 24 again has a plurality of elevations and is located on the inner peripheral surface of the actuator-side ring element 23 at.

In 8th is shown a further embodiment, wherein the camshaft adjusting system 1 again essentially as the previous versions, for example. The execution according to 1 is designed. In contrast to the previous figures, however, lies the camshaft 13 not with her face anymore 14 on a first counter-surface 15 but is through the rotor 6 stuck through it. It passes through the rotor 6 with one end / camshaft end. To the camshaft 13 rotatably with the rotor 6 To connect is preferably the rotor 6 connected with its inner peripheral surface with an outer peripheral surface of the camshaft force and / or positive and / or cohesive, for example. Via a press-fit connection and / or a welded joint. The central valve 3 is in the embodiment according to 8th not directly on the rotor 6 fitting, but in an internal bore 34 the camshaft 13 attached. This attachment can be realized in the form of a screw, but it can also be designed in the form of a press fit, wherein always an outer peripheral surface of the central valve 3 on an inner circumferential surface of the camshaft 13 is attached. The positioning of the central valve 3 relative to Verstellaktuator and to the other components of the camshaft adjuster 3 corresponds to the comments of the 1 ,

In 9 that the variant of 4 shown again, wherein the pressure fluid circuit in the camshaft adjusting system according to the invention 1 is illustrated in the operating state. The camshaft 13 is in the variants after the 1 to 9 at a the Verstellaktuator 4 facing away from the camshaft adjuster 2 plain bearing. For this purpose, the camshaft adjusting system 1 a storage component 35 on. The storage component 35 is with a (sliding) inner peripheral surface 33 with a counter surface 37 the camshaft 13 , the one Peripheral surface of the camshaft 13 represents, rotatable fitting. The storage component 35 is in turn, as not shown here for clarity, also with the cylinder head / internal combustion engine housing fixed component 22 at least rotatably connected.

For introducing the pressurized fluid whose flow / fluid flow in 9 is shown as a black arrow lines, through a radial channel 38 in the storage component 35 is introduced, the pressurized fluid by means of a pump (P) in the direction of the central valve 3 promoted. The radial canal 38 extends in the radial direction from an outer peripheral surface of the support member 35 consistently up to one the camshaft 13 sliding bearing receiving sliding (-lager-) inner peripheral surface 36 , The radial canal 38 is flush / aligned with one in the camshaft 13 introduced camshaft fluid channel 39 arranged. The camshaft fluid channel 39 initially extends in a first section also substantially in the radial direction to the axis of rotation 11 and in a second section in an axial bore to the central valve 3 out. The pressurized fluid, for example a hydraulic fluid, such as an oil, passes after passing through the bearing member 35 and its radial channel 38 the camshaft fluid channel 39 , Subsequently, the pressure fluid is deflected so that it is centric to the axis of rotation 11 is passed, namely in the axial portion of the camshaft fluid channel 39 and centric in a central bore of the central valve 3 the central valve 3 is supplied. These sections therefore form the pressurized fluid supply line 53 , In the central valve 3 arrived, divides the pressurized fluid, depending on the position of the central valve 3 or its valve piston 12 into several partial streams. Are those between the stator 5 and the rotor 6 arranged pressure chambers in a first position of the central valve 3 Open on the input side, at least a partial flow of the supplied pressure fluid in the radial direction passes through radial bores / radial pressure fluid lines in the central valve 3 and the rotor 6 into the pressure chambers between the rotor 6 and the stator 5 , In the after 9 illustrated embodiment, the pressure chambers are pressurized fluid when the valve piston 12 is in an unactuated position, ie in a position in which the actuating plunger 18 not against the valve piston 12 is pressed.

Will the actuating tappet 18 finally activated and moved (through the coil 20 ), it comes to a contact between the actuating plunger 18 and the valve piston 12 and the valve piston 12 is in the direction of the camshaft 13 from the adjusting actuator 4 pushed away until a second position of the central valve 3 is reached. In this second position then the outlet openings of the central valve 3 opened and the pressure chambers previously supplied pressurized fluid can from the central valve 3 into the pressurized fluid return line / discharge line 54 be dissipated. The pressurized fluid return line 54 thus begins at the Verstellaktuator 4 facing side of the central valve 3 , with the pressure fluid distribution space 8th that is axially between the Verstellaktuator 4 and the central valve 3 is arranged.

From this Druckfluidverteilraum 8th The pressurized fluid surrounds the guide sleeve in the circumferential direction 19 and acts in particular for the sliding surface between the actuating plunger 18 and he inner peripheral surface of the guide sleeve 19 lubricating. Through the coil near the line of the pressurized fluid is also the coil 20 to a certain extent by the pressurized fluid flows around and is cooled during operation. From the Druckfluidverteilraum 8th Then, the pressurized fluid is returned to a tank T.

For this pressurized fluid return, the pressurized fluid is first passed through the cavity 31 between the lid component 25 and the stator sidewall 28 passed. Following, after flushing the spring element 30 enters the pressurized fluid, spaced from the central valve 3 , ie offset in the radial direction to the central valve 3 , By a return channel back to the Verstellaktuator 4 facing away from the camshaft adjuster 2 by. For this purpose, first the stator side wall 28 an axial through-hole between the central valve 3 and the radially outer end of the stator sidewall 28 on. At this through hole includes a through hole / at least one through hole of the rotor 6 , hereinafter referred to as Fluidleitkanal 40 of the rotor 6 referred to. This Fluidleitkanal 40 penetrates the rotor 6 axially in its entire axial length and thus extends from the stator sidewall 28 facing side of the rotor 6 to the stator sidewall 28 opposite side of the rotor. At the stator side wall 28 opposite side is the Fluidleitkanal 40 then turn into another axial bore channel between the camshaft 13 and the outside space 10 a statorfesten, designed substantially flange-shaped guide flange 41 above. Between the guide flange 41 and the subsequent thereto in the axial direction bearing member 35 is a circumferentially extending peripheral channel 42 in the guide flange 41 incorporated, at least from one point of the circumference of the bearing component 35 in a through the storage component 35 extending discharge channel 43 passes. The discharge channel 43 is offset in the circumferential direction to the radial channel / the first radial channel 38 of the storage component 35 arranged. Druckfluidverteilraum 8th , Cavity 31 , Fluidleitkanal 40 , Circumferential channel 42 and discharge channel 43 are thus fluidly connected to one another and form the Druckfluidabführleitung 54 through which the pressurized fluid from the central valve 3 is returned to a tank (T).

As can further be seen, the discharge channel 43 that is through the storage component 35 extending portion of the Druckfluidabführleitung 54 extending in the radial direction, that its outer opening is arranged towards the outer peripheral surface in position of the internal combustion engine below. The discharge channel 43 therefore extends in the radial direction both from the central valve 3 away, as well as downwards / in the direction of the acting gravity. Alternatively to this embodiment, however, it is also possible the discharge channel 43 offset in the circumferential direction. So it is possible according to an alternative variant, the discharge channel 43 / by the storage component 35 extending portion of the Druckfluidabführleitung 54 in the storage component 35 to arrange so that the outer opening on the outer peripheral surface of the bearing component 35 is arranged in the installed position above. The discharge channel 43 then extends in the radial direction both from the central valve 3 away, as well as up / contrary to the direction of the acting gravity / against gravity. This is the pressure distribution space 8th and the central valve 3 always filled with pressurized fluid and the pressurized fluid does not run out of these areas when the engine is stationary / stationary internal combustion engine.

In 10 is a variant of the camshaft adjustment system 1 shown, wherein the camshaft adjustment system 1 essentially according to the in 5 illustrated camshaft adjusting system is configured, the storage component 35 but now in another way stocked with the camshaft 13 connected is. Contrary to the 9 has the storage component 35 not a Gleitinnenumfangsfläche 36 but a rolling bearing receiving bearing inner surface 44 on, which is rotatably connected to a partial ring of a rolling bearing. For example. is an outer ring of a rolling bearing such as a ball bearing, a barrel, roller, needle or double roller bearing rotation on the bearing inner surface 44 connected by a press fit. The inner ring of the rolling bearing 45 on the other hand sits on the outer peripheral surface of the camshaft, namely the counter surface 37 rotatable on. Also, this inner ring is preferably by means of a press fit on the counter surface 37 held. Thus, the storage component 35 in the usual way roller bearings to the camshaft 13 positioned.

At the camshaft adjuster 2 facing side of the storage component 35 is the storage component 35 by means of a seal, subsequently as a second seal 46 referred to, with the guide flange 41 tightly connected. This is the second seal 46 on the one hand on an outer peripheral surface of the guide flange 41 on the one hand and on an inner peripheral surface of the support member on the other hand 35 , The fluid recycling in 10 differs in the area of the rolling bearing 45 from the execution to 9 , From one of the stator 5 opposite side of the guide flange 41 the pressure fluid enters a free space in the storage component 35 what then in the axial direction through the rolling bearing 45 penetrates. The rolling elements held by a cage are spaced in a defined manner in the circumferential direction and the pressurized fluid can in the spaces between the spaced rolling elements of the rolling bearing 45 flow through. From a camshaft adjuster 2 facing away from the rolling bearing 45 Then, the pressurized fluid is further passed to a tank, which is not shown here, from which tank then turn the pump can take the pressure fluid for re-feeding. The fluid supply differs slightly in this variant of the execution of the 9 , The fluid supply does not happen directly through the storage component 35 but in a storage component distant portion of the camshaft 13 , The radial fluid supply takes over another storage part, which is installed in the installation position of the internal combustion engine / internal combustion engine position further back. As an alternative to the pressure fluid return through the rolling bearing, the pressure fluid return to the tank (T) in another variant rolling bearing variant also outside of the rolling bearing 45 through a separate bore spaced from the rolling bearing 45 is arranged to take place.

11 represents yet another variant, wherein the camshaft adjustment system 1 essentially like the camshaft adjustment system 1 in 10 is executed, but the storage component 35 now no longer has a rolling bearing, the camshaft 13 receives, but again a sliding bearing according to the 9 , The pressure fluid supply to the central valve 3 not done by a radial bore through the Gleitinnenumfangsfläche 36 of the storage component 35 through, but through an outside of the storage component 35 located insertion channel, which is not shown here.

In 12 is another variant of the camshaft adjustment system 1 illustrated, this variant is essentially the variant according to 10 equivalent. The adjusting actuator 4 is at the junction 47 by means of the fixing screw 21 on the cylinder head fixed component 22 firmly connected, ie both in the axial direction, fixed in the radial direction and rotationally fixed. Due to the dynamic stresses on the stator during operation 5 /Camshaft 13 / Phaser 2 These parts are excited to wobble in the radial direction, that is, there is a shift of the camshaft 13 and its longitudinal axis and the camshaft adjuster 2 and its longitudinal axis in the radial direction, comes, whereby an axial offset between the camshaft adjuster 2 and the Verstellaktuator 4 comes. Around Decoupling wobbling is the seal 9 configured such that it also in larger tumbling movements, ie, when in a first circumferential region of the radial gap between the actuator-side ring element 23 and the lid-side ring member 27 reduced and increased relative to this first point of the radial gap at a second location of the radial gap that they despite the axial offset / the radial wobbling the Druckfluidverteilraum 8th opposite the outside space 10 seals.

In addition to the mounting screws 21 are also dowel pins providable and, for example, on the cylinder head fixed component 22 attachable to the Verstellaktuator 4 relative to the cylinder head fixed component 22 to center.

In the 13 an alternative embodiment is shown. Because alternative to the rigid connection at the junction 47 between the adjusting actuator 4 and the cylinder head fixed component 22 ( 12 ), can also be the adjusting actuator 4 by means of his housing 7 play with the cylinder head resistant component 22 be connected. For example, specially designed Spielpassschrauben 48 used. These clearance screws 48 then have a threaded portion fixedly in the cylinder head fixed component 22 is screwed, as well as a fitting portion, the game-afflicted in the radial direction in a bore in the housing 7 the Verstellaktuators is inserted. The screw head of this clearance screw 48 is formed and the length of the fitting portion selected so that the axial length of the fitting portion is greater than the axial width of the housing 7 in the area of the junction 47 , Thus, at the junction 47 the adjusting actuator 4 on the side of his case 7 both play in the radial direction and in the axial direction. In return to this is the previous seal 9 between the lid-side ring member 47 and the actuator side ring member 23 through a coupling element 49 replaced. This coupling element 49 In addition to the function of a seal, also the function of a rigid, at least in the radial direction unyielding storage, in particular a radial bearing, for example. In the form of a rolling bearing. The coupling element 49 is therefore a combination component of seal and radial bearing / roller bearing. The adjusting actuator 4 is therefore in the radial direction by means of the coupling element 49 on the lid component 25 held. A decoupling in the radial direction decoupling point is thus of the area between the cover component 25 and adjusting actuator 4 ( 12 ) in the area between Verstellaktuator 4 and cylinder head resistant component 22 ( 13 ) relocated.

Alternatively to the in 13 illustrated play afflicted connection of the Verstellaktuators 4 to the cylinder head resistant component 22 by means of clearance screws 48 It is also possible, another positive rotation, which engages a certain angle of rotation between Verstellaktuators 4 and cylinder head resistant component 22 implement. For example, this rotation can also be executed fork-groove-like, where, for example, two projections on the Verstellaktuator 4 are tethered, play afflicted with two recesses in the cylinder head fixed component 22 interact.

As in the 1 to 13 can be seen, the storage component 35 on one side of the camshaft adjuster 2 connect the adjusting actuator 4 turned away. 14 shows in this context a further embodiment variant, the camshaft adjustment system 1 shows, which is again constructed substantially in accordance with the previous embodiments, but differs with respect to the camshaft bearing and the camshaft design. On the adjustment actuator side facing away from the camshaft adjuster 2 is now a Fluidleitring 50 immediately next to the camshaft adjuster 2 / Leitflansch 41 arranged, wherein the inner peripheral surface of the Fluidleitrings 50 from the outer circumferential surface / the counter surface 37 the camshaft 13 is spaced in the radial direction and therefore no radial bearing of the camshaft 13 implements. The fluid guide ring 50 serves exclusively for the conduction of the pressurized fluid 41 , The fluid guide ring 50 is by means of a second seal 46 with the guide flange 41 tightly connected. For pressure medium fluid supply also has the Fluidleitring 50 a radial channel 38 on, through which radial channel 38 Pressurized fluid from the exterior 10 in the camshaft 13 is directed into it. Also this radial channel 38 is with the substantially axially extending camshaft fluid channel 39 inside the outer wall of the camshaft 13 connected. In the axial direction then the pressurized fluid in the center of the camshaft 13 , the central valve 3 fed.

As in 14 It can also be seen, is the camshaft 13 through the rotor 6 stuck through and protrudes on a Verstellaktuator 4 facing side of the camshaft adjuster 2 from the camshaft adjuster 2 out. At this end of storage 51 the camshaft 13 , So that camshaft end, the camshaft adjuster 2 in the direction of the adjusting actuator 4 protrudes out, then in turn is the storage component 35 arranged / formed. The storage component 35 is in the cylinder head resistant component 22 integrated and one-piece / integrally designed with this. The storage component 35 extends again, this time in the axial direction between the camshaft adjuster 2 and the Verstellaktuator 4 , in the radial direction to the outer peripheral surface / the counter surface 37 the camshaft 13 go and take the opposite surface 37 stocked up. On an outer peripheral surface of cylinder head resistant component 22 is the actuator-side ring element 23 intigriert, on which in turn the seal 9 sealingly abuts, and in a known manner sealingly with an inner peripheral surface of the cover-side ring member 27 interacts. Thus, in this variant, an actuator-side ring element 23 provided integral to the cylinder head fixed component 22 is arranged and not just the seal 9 receives on an outer peripheral surface, but also by means disposed on the inner peripheral surface bearing member 35 the storage end area 51 the camshaft 13 receives.

In 15 a further embodiment variant is shown, which essentially according to the camshaft adjustment system 1 to 14 is constructed, but wherein the Fluidleitring 50 no radial canal 38 but only an axially extending channel, by means of which the pressurized fluid can be returned to the tank. Also the camshaft 13 is formed somewhat differently in this embodiment, wherein the camshaft, which also through the entire camshaft adjuster 2 protrudes through and a storage end area 51 having, with the storage component 35 is radially mounted, but in addition also has an extending in the radial direction Stirnerhebung, the end face 14 in the axial direction in contact with a first counter-holding surface 15 on the rotor 6 is held. This is the camshaft 13 in turn secured axially.

Also in 16 Yet another embodiment is shown, wherein storage component 35 not a plain bearing surface for sliding-bearing cooperation with the camshaft 13 has, as in the variants of the 14 and 15 executed, but serves as a receiving surface for a roller bearing, such as a roller or a needle bearing. In the embodiment according to 16 is on the storage component 35 an outer ring of a rolling bearing pressed against rotation, whereas the inner ring directly through the outer wall / outer peripheral surface of the camshaft 13 is trained. Thus, a rolling bearing as the camshaft 13 to the cylinder head fixed component 22 storable element ausgestaltbar.

LIST OF REFERENCE NUMBERS

1

Cam Phaser System / kit

2

Phaser

3

central valve

4

adjustment actuator

5

stator

6

rotor

7

Housing / Verstellaktuatorgehäuse

8th

Druckfluidverteilraum

9

poetry

10

outer space

11

axis of rotation

12

plunger

13

camshaft

14

front

15

first counterhold area

16

page survey

17

second counter-surface

18

actuating ram

19

guide sleeve

20

Kitchen sink

21

fixing screw

22

Cylinder head fixed component / internal combustion engine housing fixed component

23

actuator-side ring element

24

first sealing lip

25

cover component

26

second sealing lip

27

cover-side ring element

28

Statorseitenwand

29

flange-shaped section

30

Bungee / return spring

31

cavity

32

reinforcement ring

33

Sealing inner circumferential surface

34

internal bore

35

storage component

36

Gleitinnenumfangsfläche

37

counter surface

38

radial channel

39

Camshafts fluid channel

40

Fluidleitkanal

41

Leitflansch

42

peripheral channel

43

discharge channel

44

Bearing inner surface

45

roller bearing

46

second seal

47

junction

48

Game Passschraube

49

coupling element

50

Fluidleitring

51

Storage end portion

53

Druckfluidzuführleitung

54

Druckfluidabführleitung

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• EP 1596040 A2 [0002]
• DE 102008051145 A1 [0004]
• DE 4209953 A1 [0005]
• WO 03/085238 A1 [0062]

Claims (10)

Camshaft adjusting system ( 1 ) with a camshaft adjuster ( 2 ) of the vane type, in which a pressure fluid distributing central valve ( 3 ) is present, and with a Verstellaktuator ( 4 ), which points to the central valve ( 3 ) controlling the pressure fluid distribution, the camshaft adjuster ( 2 ) is driven or driven by means of a dry running traction drive, wherein the Verstellaktuator ( 4 ) at a connection point ( 47 ) on an internal combustion engine housing fixed component ( 22 ) is attached or attachable, and with a component of the camshaft adjuster ( 2 ) via a coupling element ( 49 ) is in communication with the coupling element ( 49 ) is formed and arranged, and / or the connection point ( 47 ) is configured such that tumbling movements in the radial direction of the camshaft adjuster ( 2 ) of the internal combustion engine housing fixed component ( 22 ) are decoupled, wherein a statorfestes cover component ( 25 ) in the form of a cavity enclosing spring cover for receiving a return spring ( 30 ) is configured and arranged. Camshaft adjusting system ( 1 ) according to claim 1, characterized in that the coupling element ( 49 ) as a combination component of a gasket ( 9 ) and a rolling bearing or as a sliding, at least in the radial direction compressible seal ( 9 ) is trained. Camshaft adjusting system ( 1 ) according to one of claims 1 and 2, characterized in that the coupling element ( 49 ) between a camshaft adjuster-fixed component ( 25 ) and the internal combustion engine housing fixed component ( 22 ) is arranged. Camshaft adjusting system ( 1 ) according to one of claims 1 to 3, characterized in that the coupling element ( 49 ) a pressurized fluid distribution space ( 8th ) of the camshaft adjuster ( 2 ) to the environment ( 10 ) of the camshaft adjuster ( 2 ) seals. Camshaft adjusting system ( 1 ) according to one of claims 1 to 4, characterized in that the Verstellaktuator ( 4 ) at its junction ( 47 ) with at least one screw element ( 21 ) on the internal combustion engine housing fixed component ( 22 ) is attached or attachable, and / or the at least one screw ( 21 ) is designed as a screw, for example as a threaded bolt, which, at least in the internal combustion engine housing fixed component ( 22 ) is firmly screwed or screwed with a first threaded portion. Camshaft adjusting system ( 1 ) according to one of claims 1 to 5, characterized in that the Verstellaktuator ( 4 ) at the junction ( 47 ) in the axial and / or radial play on the internal combustion engine housing fixed component ( 22 ) is attached or attachable. Camshaft adjusting system ( 1 ) according to one of claims 1 to 6, characterized in that the Verstellaktuator ( 4 ) at the junction ( 47 ) to the internal combustion engine housing fixed component ( 22 ) is centered or arrangeable. Camshaft adjusting system ( 1 ) according to one of claims 1 to 7, characterized in that the Verstellaktuator ( 4 ) at the junction ( 47 ) the internal combustion engine housing fixed component ( 22 ) engages positively in the circumferential direction. Drive train for a motor vehicle, with a camshaft adjusting system ( 1 ) according to one of claims 1 to 8, a dry running traction drive, such as a belt drive, the at least in the operating state, the stator ( 5 ) of the camshaft adjuster ( 2 ) and with an internal combustion engine housing fixed component ( 22 ), such as a cylinder head housing or a Zugmitteltrieb enclosing Zugmittelkasten, wherein the Verstellaktuator ( 4 ) on the internal combustion engine housing fixed component ( 22 ) is attached. Drive train according to claim 9, further comprising a camshaft ( 13 ) is present, which at least in the operating state with the camshaft adjuster ( 2 ) connected is.

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