WO2015169295A1

WO2015169295A1 - Camshaft adjuster with adjustable locking pin bearing

Info

Publication number: WO2015169295A1
Application number: PCT/DE2015/200061
Authority: WO
Inventors: Olaf Boese
Original assignee: Schaeffler Technologies AG & Co. KG
Priority date: 2014-05-07
Filing date: 2015-02-04
Publication date: 2015-11-12
Also published as: DE102014208483A1

Abstract

The invention relates to a vane cell-type hydraulic camshaft adjuster (1) comprising a stator (2) and a rotor (3). The rotor (3) is mounted in a rotatable manner relative to the stator (2), and at least one locking pin (16) is provided in order to separate the rotor (3) from the stator (2) at least in a rotational direction when the locking pin comes into contact with a slotted guide (19). A bearing element (14) which guides the locking pin (16) can be adjusted such that an outer contour of the locking pin (16) can be brought into contact with the slotted guide (19).

Description

Camshaft adjuster with adjustable locking pin bearing

The invention relates to a hydraulic camshaft adjuster of the vane type, with a stator and a rotor, wherein the rotor is rotatably mounted relative to the stator, and wherein at least one locking bolt is provided to limit the contact rotor with a backdrop the rotor to the stator at least in one direction of rotation , wherein the gate is preferably formed by a statorfestes component or a rotorfestes component, such as the stator or the rotor and more preferably the locking pin in the respective counter element to the statorfesten or rotorfesten component, so for example. The rotor or stator axially movable but inserted set out in a movable is.

A camshaft adjuster of the aforementioned type is known, for example, from DE 10 2012 209 027 A1. This describes a camshaft adjuster with a first component, with a relative to the first component about an axis of rotation within an angular range rotatable second component and with a locking device for locking the first component relative to the second component. In this case, the locking device comprises on the first component, a first locking bolt and a second locking bolt and on the second component at least one Mittenkulisse. The two locking bars are each movably guided between a locking position and an unlocking position and engage in a central angular position of the components to each other in their locking position at least in the middle a backdrop. In this case, at least one Endkulisse is provided on the second component, engages in a deviating from the average angular position of the components Endwinkellage the first locking bolt or the second locking bolt in its locking position. Gas exchange valves of internal combustion engines can be actuated by cams of a camshaft. By means of the arrangement and shape of the cams, the opening and closing times of the gas exchange valves can be specifically defined. The camshaft is usually actuated, driven and / or driven by a crankshaft of the internal combustion engine. The opening and closing times of the gas exchange valves of the internal combustion engine are usually predetermined by a relative rotational position or phase position or angular position between the cam and the crankshaft. By a relative change of this relative rotational position between the Camshaft and the crankshaft, a variable adjustment of the opening and closing times of the gas exchange valves can be achieved. The variable adjustment of the opening and closing times of the gas exchange valves, depending on the current operating state of the internal combustion engine, for example, the exhaust behavior can be positively influenced, the fuel consumption can be reduced, the efficiency can be increased, and / or the maximum torque and / or Maximum power of the internal combustion engine can be increased.

This variable adjustment of the opening and closing times of the gas exchange valves can be made or made possible by a camshaft adjusting device or camshaft adjuster provided between the crankshaft and the camshaft.

For this purpose, a camshaft adjuster is conventionally provided in the kinematic chain between the crankshaft and the camshaft. A part of the camshaft adjuster, hereinafter referred to as stator, is preferably connected in a rotationally fixed manner to the crankshaft. Another part of the camshaft adjuster, hereinafter referred to as rotor, is preferably non-rotatably connected to the camshaft. A gear is conventionally provided between the stator and the rotor. This transmission is conventionally provided as a hydraulically operated vane cell, or as a plurality thereof, in a vane-type hydraulic camshaft adjuster. By acting on the vane with hydraulic pressure, for example by means of a controller and / or valves, the variable adjustment of the opening and closing times of the gas exchange valves can be achieved. This embodiment can also be referred to as Rotationskolbenversteller.

In a hydraulic camshaft adjuster operating conditions may occur during which this hydraulic actuation or hydraulic control is not possible or not ensured or not economical or undesirable. For example, during starting of the internal combustion engine, the rotational position is usually not specified hydraulically. By an uncontrolled rotational position or an uncontrolled changing the rotational position, for example, increased wear of the camshaft adjuster, the camshaft, the gas exchange valves or generally the internal combustion engine can be caused. To the To avoid uncontrolled rotational position or uncontrolled changing the rotational position, a releasable or releasable locking of the rotor to the stator is desired. With regard to the rotational position of the gas exchange valves, an "early" lock, a "middle" lock or a "late" lock may be desired, these being referred to as early lock, center lock, late lock or the like.

For this purpose, for example, from the aforementioned prior art known to provide a blocking element or locking element, such as a locking bolt. The blocking element may also be provided as a bolt, a pin or a pin. The blocking element may for example be received or mounted or fastened in the rotor. The blocking element can be actuated for example by a spring bias. The blocking element can be hydraulically released or ventilated, for example. The blocking element can, for example, come into contact with a locking link of the stator. Due to economic considerations (Tolerierung) an engagement of a bolt-like locking element is in a locking slide game. This is also referred to as locking clearance or locking clearance tolerance. This locking game leads to an undesirable noise or unwanted wear of the bolt and / or the backdrop. It is therefore the object of the present invention to provide a camshaft adjuster with a possibility for adjusting the locking clearance. In particular, a suitability of the camshaft adjuster for use in center locking is desirable.

This object is achieved in a generic camshaft adjuster in that a locking bolt leading, preferably provided by the rotor and / or the stator separate bearing element is adjustable so that an outer contour of the locking bolt in contact with the backdrop, which is approximately from the stator / is formed, can be brought. It is advantageous if the outer contour of the locking bolt without play in contact with the backdrop can be brought. In particular, it can be provided that the outer contour of the locking bolt can be brought into contact with a contour of the backdrop. By providing a locking bolt leading bearing element with the described adjustability, the locking game can be reduced / reduced or canceled.

Advantageous embodiments are claimed in the subclaims and are explained in more detail below. For reasons of a simpler installation and / or a reduced storage, it is advantageous if the bearing element and the locking bolt are provided ready for assembly as an assembly. In that regard, it can be provided that the bearing element is formed as a sleeve, within which the locking bolt is mounted axially movable. With regard to the object of the invention, it is particularly advantageous if the locking bolt is mounted axially movable and free of play within the sleeve. Alternatively, the locking bolt can also be moved in the axial direction of the rotational movement of the rotor relative to the stator, It may be particularly advantageous, the central axis of the locking bolt parallel to the axis of rotation of the relative rotation of the rotor to the stator provided.

In order to simplify the mounting of the bearing element in the rotor, it can be provided that the bearing element is rotatably inserted into the rotor, or that the bearing element is rotatably mounted in the rotor.

It should be noted at this point that it is subordinate to the function of this invention whether the locking bolt is provided on the rotor and the link on the stator, or whether the locking bolt is provided on the stator and the link on the rotor. In this respect, the terms "stator" and "rotor" can be interchanged in the claims, for example, for reasons of design considerations, ie a kinematic reversal must be included. It is advantageous to support the bearing element without play in the rotor. For the purpose of facilitated adjustability can be provided to guide the locking bolt in the bearing element eccentric. In this context, the term "eccentric" refers to a distance between adjusting the adjustment and an effect of the adjustment. In other words, the term "eccentric" refers to a distance between a bearing element longitudinal direction and a locking bolt longitudinal direction. A bearing element with eccentrically guided locking bolt is also referred to as "eccentric bearing element". In order to limit the rotational freedom of rotation of the rotor to the stator in both directions of rotation structurally simple, a second locking bolt can be provided to limit the rotor to the stator at least in a second direction of rotation when Inkontaktgelangen with a second link. For example, in order to achieve a rapid meshing of the locking bolt or the locking bolt, it can be provided that the camshaft adjuster can be locked in a center locking position.

The adjustment of the bearing element in the rotor (or in the stator) can be provided in various ways. For example, the adjustment of the bearing element in the rotor can be automatically provided, for example, by a spring. It can also be provided that the adjustment of the bearing element in the rotor is made manually. In particular, in manual adjustment of the adjustment element in the rotor during assembly, it is expedient to maintain the adjusted adjustment of the bearing element in the rotor. In this respect, it can be provided that the bearing element can be fixed in the rotor in different positions.

For the purpose of facilitating assembly of the bearing element can be provided that a movement for adjusting the adjustment of the bearing element and a movement for fixing or fixing the adjustment of the bearing element are separated from each other or independent. In other words, it can be provided that a movement for adjusting the position of the bearing element in the rotor and a movement for fixing or fixing the position of the bearing element in the rotor are separated from each other or independent from each other. Insofar it can be provided that the bearing element is designed so that it is adjustable by rotation with respect to its position in the rotor, and that the bearing element or the adjustment of the bearing element / the position of the bearing element in the rotor by a movement in the axial direction of the bearing element is determinable.

Furthermore, various ways of setting the adjusted adjustment of the bearing element may be provided. Thus, it can be provided that the adjustment of the bearing element is firmly bonded, in particular by means of gluing or soldering or welding. Thus, it can further be provided that the adjustment of the bearing element is non-positively fixed, for example. By means of longitudinal compression or transverse pressing. Furthermore, it can be provided that the adjustment of the bearing element can be fixed in a form-fitting manner, for example by means of a fixing section of the bearing element and / or the rotor (or stator). Furthermore, it can be provided that the bearing element and / or the rotor (or stator) is designed so that the bearing element is cohesively, non-positively and / or positively locked in its position on the rotor. The position of the bearing element on the rotor can be fixable, for example, by means of the shape of the bearing element and / or the shape of the rotor (or the stator) and / or by means of the choice of material of the bearing element and / or the rotor (or the stator). The adjustment of the bearing element can be determined or fixed by a combination of the aforementioned possibilities. It may be inexpensive that the fixing portion of the bearing element is geometrically and / or materially prepared for being pressed into the rotor (or stator), and that a portion of the rotor (or stator) is geometrically and / or materially prepared for press-fitting the fixing portion is designed. For example, the fixing portion may include hardened metal. For example, the fixing portion may include at least one protrusion, such as at least one tooth. For example, the area of the rotor (or stator) prepared for press-fitting the securement portion may include a soft or relatively ductile metal. For example, the area of the rotor (or stator) prepared for press-fitting the securement portion may provide a recess which receives plastically deformed or "bulging" material by the press-fitting or function of the camshaft adjuster impaired, still has to be removed in the course of assembly.

It makes economic sense to use for the purpose of setting the adjustment of an otherwise conventional construction element. It is particularly easy to install when an external toothing is provided on the bearing element, and on the rotor an internal toothing is provided, which are prepared for meshing. The two gears are suitably sized. It should be noted at this point that the terms external teeth and internal teeth are not intended to imply a complete toothed ring, but that it may be sufficient if one of these teeth a plurality of teeth, corresponding to the usual adjustment range, and the other teeth only a single tooth are provided comprehensively. Will the adjustment, for example By turning the bearing member at most 180 ° (the usual range of adjustment assumed for this example), it may be sufficient to provide a semicircle of teeth (corresponding to the usual adjustment range) and a single tooth on the rotor on the bearing member. In order to allow setting and / or setting the adjustment of the bearing element inexpensively with conventional means of assembly, a Werkzeugingreifkontur may be provided on the bearing element (or on the bearing elements respectively). As a tool-engaging contour is in particular a screwdriver contour such as a slot-shaped recess, a cross-shaped recess, a multi-or hexagonal recess or a star-shaped recess into consideration.

A spring may be kinematically provided between the bearing element and the locking bolt, which is designed and dimensioned such that it can extend the locking bolt (repeatedly) into a locking position out of the bearing element. As a result, a safety function of the locking bolt can be ensured, since a prestressed spring can automatically act to extend the locking bolt in the absence of, for example, a hydraulic restraining force.

In particular, a bottom may be provided on the optionally sleeve-shaped or bush-shaped bearing element, in which the tool-engaging contour is introduced or from which the tool-engaging contour is excluded. Such a floor also has the advantage that the optionally provided spring for extending the locking bolt in the locking position on the ground can be supported.

Since tight tolerances usually require high manufacturing costs, it may be advantageous to allow a particularly wide adjustment range of the adjustment. In this respect, a two-stage eccentricity can be provided. A two-stage eccentricity means that the locking bolt is guided eccentrically in an inner bearing element, and that the inner bearing element is guided eccentrically in an outer bearing element. In this case, it can be provided that an adjustment of the inner bearing element is independent of an adjustment of the outer bearing element adjustable and / or fixable. In general terms, it can thus be provided that a first bearing element guiding the locking bolt as a second bearing element supporting the first bearing element are each provided so adjustable that an outer contour of the locking bolt can be brought into contact with the backdrop. For such a multi-stage principle of two bearing elements, all the aforementioned developments (or a selection thereof) can be provided on one or in each case one or more of the bearing elements.

It may be advantageous, for example, for space reasons and / or for lighter weight, a fluidic force for unlocking or ventilation or generally for moving the locking bolt in the bearing element be advantageous in / on the bearing element, a fluidic connection between a Locking bolt at least partially receiving (inner) region of the bearing element and the rotor (or stator) design provide. It can therefore be provided, for example, a recess in a Lagerelementwandung or sleeve wall. Furthermore, a multiplicity of recesses of the bearing element wall or sleeve wall, as far as a latticed section of the bearing element wall or sleeve wall, may be provided. This recess can also be designed as a transverse opening, hydraulic medium passage opening or as a hydraulic medium through-channel. In other words, such a recess is advantageous, for example, for an oil feedthrough, for instance in order to act when a center lock is implemented, or to act efficiently when a chamber supply is switched on / off.

It can also be provided in / on the rotor (or in / on the stator) a channel in the circumferential direction of the bearing element, wherein the channel is open to the bearing element. In this way, it can be ensured in a structurally simple manner that a fluid in the channel can be fed to the bearing element independently of a position of the bearing element.

Furthermore, this invention relates to a timing drive with a phaser as described above.

Moreover, this invention relates to an internal combustion engine with a timing drive as described above. In other words, the object is achieved by making it possible to use the locking clearance by using a bushing which has an eccentricity between its outer diameter and its inner diameter (eccentric bushing). to deliver. For this purpose, the locking piston in the socket and the socket can be provided in a locking bore. By rotating the bush, the position of the locking piston can be adjusted to a locking link. After adjusting the locking clearance, the position of the bushing can be fixed. The socket is thus guided in the rotor (or stator). The locking piston is thus guided in the socket. The position of the locking piston to a backdrop can be changed by turning the socket. The bush can be fixed by adjusting the locking clearance, for example, by means of a press fit, a form fit, gluing or the like. It may also be possible to connect the eccentric bush together with the locking piston and a locking spring to a locking unit, which can be supplied as an assembly of the (camshaft) Verstellermontage. According to one embodiment of the invention, it is also possible to use two eccentric bushings to allow an even greater locking clearance compensation. The invention will be described in more detail below with the help of several embodiments. Show it:

Fig. 1 is a plan view of a camshaft adjuster according to a first

2 shows a cross-sectional view of the camshaft adjuster in the direction of the II-marked line in FIG. 1, FIG.

3 is a cross-sectional view of the camshaft adjuster in the direction of the III marked line in Fig. 1,

4 is an enlarged view of the area designated IV in FIG. 3, FIG. 5 is a cross-sectional view of the camshaft adjuster along the line V in FIG. 1,

Fig. 6 is an enlarged view of the area marked VI

Fig. 5,

7 is a perspective view of a sleeve of the camshaft adjuster,

8 is a perspective view of the sleeve of the camshaft adjuster, 9 is a bottom view of the sleeve of the camshaft adjuster,

10 is a cross-sectional view of the camshaft adjuster along the line marked X in FIG. 1,

Fig. 1 1 is an enlarged view of the area marked XI

Fig. 10,

12 is a cross-sectional view taken along the XII line of FIG. 1,

13 is an enlarged view of the area marked XIII

Fig. 12,

14 is a perspective view of a second, which now has Hydraulikmit- teldurchgangskanäle in its side wall,

Fig. 15 shows the sleeve of Fig. 14 in a perspective view from the other

Side, and

16 is a cross-sectional view of the camshaft adjuster according to the second embodiment along a section line corresponding to the line V in FIG. 1 according to the first embodiment.

In other words, FIG. 1 shows an overview of the positions of the individual sectional views of a camshaft adjuster for FIGS. 2 to 6 and 10 to 13. In other words, FIGS. 2 to 4 show a contact position of a locking piston to a locking link, wherein the locking piston rests against the locking link. In other words, FIGS. 5 and 6 show an eccentric bush inserted in a rotor, in which a locking piston is guided, the bushing protruding axially over the rotor in order to allow the bushing to be rotated. In other words, FIGS. 7 to 9 show an eccentric bush, in which a bottom, a slot-shaped tool-engaging contour for a twisting and a tooth-ring-shaped rotation lock are formed. At this point, it should be mentioned that the bush can also be designed as a through bush without bottom and / or without sprocket as anti-rotation. In this connection, attention is drawn to the possibility of anti-rotation by means of a press fit. In other words, FIGS. 10 and 11 show a state before adjusting the locking mechanism. , game. In other words, Figs. 12 and 13 show a state after setting the locking clearance, wherein the eccentric bushing is completely received in the rotor to be secured by means of the toothing against rotation. In other words, Fig. 14 shows a variant of the sleeve in a similar to Fig. 8 representation, wherein the sleeve has hydraulic medium passageways in its side wall. In other words, Fig. 14 shows the sleeve shown in Fig. 13 from another side. In other words, FIG. 16 shows the sleeve of FIGS. 14 and 15 in an installed state.

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. Elements of the individual embodiments can be interchanged.

In the illustration shown in FIG. 1 of a camshaft adjuster 1 according to a first embodiment of the invention with a stator / stator device 2, a rotor / rotor device / device 3, a single locking device 4 and an eccentric locking device 5, FIGS with II, III, V, X and XII lines, sectional views with view in the respective direction of the arrow. The single locking device 4 and the eccentric locking device 5 are mounted in the rotor 3.

As can be seen from FIGS. 2, 3, 5, 10 and 12, the stator 2 comprises a stator base plate 6 and a stator base body 7. The stator base plate 6 and the stator base body 7 represent a plurality of stator-fixed components which are not specified in more detail here. For the purpose of this invention, it is also conceivable that the stator 2 is formed in one piece.

The rotor 3 comprises a rotor base body 8. The rotor base body 8 is representative of a plurality of rotor-fixed components which are not specified in greater detail here. For the purpose of this invention, it is also conceivable that the rotor 3 is formed in one piece. The stator 2 and the rotor 3 are rotatable about a common central axis of rotation, which can be referred to as the main axis and perpendicular to the plane of the Figure 1. The single locking device 4 shown in FIGS. 2, 3 and 4 comprises a locking pin 9, a locking spring 10 and a locking holder 1 1. The single locking device 4 is in a recess of the rotor third formed Verhegelungsaufnahme 12 completely absorbable. By a spring force of the locking spring 10, the locking pin 9 from the Verhegelungsaufnahme 12 as shown in particular in Fig. 4 protrude. In the stator base plate 6, a locking slot 13 realized as a locking recess recess is formed. The locking link 13 can also be referred to briefly as a link 13. As can be seen in particular from the enlarged view of FIG. 4, an outer contour of the locking bolt 9 in the circumferential direction of the camshaft adjuster 1 in a locking position on the locking link 13 or a contour of the link 13 abut, ie be brought backlash with this in Appendix , As a result, a direction of rotation of the rotor 3 to the stator 2 is limited.

As can be seen from FIGS. 5, 10, 11, 12, 13 and in particular from FIG. 6, the eccentric locking device 5 comprises an eccentric sleeve 14, a locking spring 15 and a locking bolt 16. The eccentric locking device 5 is in a recess of the rotor 3 formed locking receptacle 25 completely receivable. In particular, the locking spring 15 and the locking pin 16 in the eccentric sleeve 14 are receivable. The eccentric sleeve 14 thus supports the locking pin 16 and thus represents the bearing element 14 according to the invention. The eccentric sleeve 14 may also be referred to as a locking bolt bearing element 14, as an eccentric bush 14, as a sleeve 14 or as a bush 14. The eccentric sleeve 14 is dimensioned such that a length 17 of the eccentric sleeve 14 is not greater than a thickness 18 of the rotor main body 8. Alternatively, it is also possible that the length 17 is less than the thickness 18. If the length 17 is less than the thickness 18, then it is not necessary that the locking spring 15 and the locking pin 16 are fully accommodated in the eccentric sleeve 14, however, it is provided that the locking pin 16 so far in the rotor 3 is receivable that the locking bolt 16 does not protrude beyond the rotor base body 8 or the rotor 3 when the lock is released. In the stator base plate 6 realized as Verriegelungseinspurausnehmung locking slot 19 similar to the locking link 13 formed. The locking link 19 can also be referred to briefly as a link 19.

As can be seen, in particular, from the enlarged view of FIG. 13, an outer contour of the locking bolt 16 in the circumferential direction of the camshaft adjuster 1 in a locking position on the locking link 19 or an rest against the contour of the gate 19, ie be brought backlash with this in Appendix. As a result, a direction of rotation of the rotor 3 is limited to the stator 2. A respective outer surface of the locking bolts 9 and 16 or at least a portion of the respective outer surface thus forms the respective outer contour of the locking bolts 9 and 16.

As can be seen from Fig. 1, the positions of the scenes 13 and 19 in the stator 2 and the positions of the locking receptacles 12 and 25 are selected in the rotor 3 so that the camshaft adjuster 1 can be locked in the center lock. Conveniently, the locking latches 13 and 19 are connected so that a hydraulic means can flow between them.

5 and 10 and in particular in their enlarged detail illustrations Fig. 6 and 1 1, a gap between the locking pin 16 and the locking link 19 can be seen. This gap represents the locking game, which is to reduce or cancel tasks. In the following, the design of the sleeve 14 and the adjustment of the lock will be discussed.

The sleeve 14 is shown in Figs. 7 to 9. The eccentric sleeve 14 has an outer periphery 20 having an outer circumferential center 21, an inner circumference 22 having an inner circumferential center 23, and an eccentricity 24 between the outer circumferential center 21 and the inner circumferential center 23. Thus, the thickness of the wall of the eccentric sleeve 14 changes continuously. If the locking bolt 16 is guided in the eccentric bushing 14 to the inner circumference 22, as shown in this embodiment, the position of the locking bolt 16 is fixed relative to the outer circumference 20 by the eccentricity 24. In this case, the locking bolt 16 is guided without play in the eccentric sleeve 14. The eccentric sleeve 14 is received in the rotor 3 with the outer circumference 20 in the locking receptacle 25, which is formed as a recess of the rotor base body 8. Thus, the position of the locking bolt 16 via the eccentricity 24 in the locking receptacle 25 by rotating the eccentric sleeve 14 relative to the Rotorgrund- body 8 is continuously adjustable.

At the eccentric sleeve 14, a sleeve bottom 26 is further formed. More precisely, the sleeve bottom 26 is not formed on the side or location of the eccentric sleeve 14, at which is the locking bolt from the eccentric sleeve 14 in the locked position extendable. In the sleeve bottom 26, a recess 27 is formed. The recess 27 may also be referred to as a tool-engaging contour 27. On the outer periphery 20, an external toothing 28 is further formed in the region of the sleeve bottom 26. In the rotor base body 8, an internal toothing 29 is further formed, which corresponds to the external toothing 28.

When mounting the camshaft adjuster 1, the locking clearance between the link 19 and the locking pin 16 is adjustable as follows. The rotor 3 is rotated to the stator 2, that the locking receptacle 25 is aligned with the recess of the link 19. Then the eccentric locking device 5 is partially inserted into the locking receptacle 25. In this case, the thick side of the wall of the eccentric sleeve 14 in the direction of the locking link 19, so that there is a gap between the locking link 19 and the locking pin 16. In addition, the eccentric locking device 5 is pushed into the locking receptacle 25 so far that the locking bolt 16 protrudes beyond the rotor main body 8 into the region of the locking link 19, but only so far that the external toothing 28 does not come into contact with the internal toothing 29 , With the help of the tool-engaging contour 27 and a suitable tool (not shown) such as a screwdriver, the eccentric sleeve 14 is rotated so far until the locking pin 16 comes into abutment with the locking link 19. At the same time the locking pin 9 with the locking link 13 in Appendix, the locking game is just canceled. Now, the eccentric sleeve 14 is just turned back until the external toothing 28 can be inserted into the internal toothing 29 and then the eccentric sleeve 14 is pushed completely into the rotor base body 8, so that the external toothing 28 with the internal toothing 29 settles in a set adjustment Gear contact arrives. The rotational movement for adjusting the adjustment and the insertion movement for setting the adjustment are mechanically independent of each other.

In order to move the locking pins 16 and 9 axially into the locking receptacles 12 and 25, ie to move the locking bolts from the locking position into a (camshaft) adjustment position, a hydraulic means such as, for example, an oil is introduced into the locking slots 13 and 19 forming recesses introduced and pressurized as long or until the spring forces of the locking springs 10 and 15 are sufficiently overcome. The camshaft adjustment position of the locking pins 9 and 16 is a position along its extension direction, in which the locking pins 9 and 16 are received so far in the rotor 3, that they can not come into contact with the locking slots 13 and 19 of the stator 2. The camshaft adjustment position is also referred to as adjustment position, non-blocking position, release position or operating position.

If this pressurization ends with hydraulic pressure, then the locking bolts 9 and 16 are axially moved or extended into the recesses of the stator main body 7 which form the slotted links 13 and 19, ie. moved from the adjustment position into the locking position as soon as the locking receptacles 12 and 25 are sufficiently aligned with the said recesses. In order to improve a meshing behavior of the locking bolts 9 and 16, these locking bolts 9 and 16 are provided with a Einspurfase 30.

In this respect, a releasable locking between the stator 2 and the rotor 3 with reduced or canceled locking play can be realized.

FIGS. 14 to 16 show a variant of an eccentric sleeve 14 without a locking bolt located therein.

The sleeve / eccentric sleeve 14 has transverse openings / hydraulic medium passage openings or hydraulic medium passageways 31, as shown, for example, in US Pat. are advantageous for an oil passage, for instance in order to be effective in realizing a central locking or switching on / off of a chamber supply. The transverse openings can also be constructed like a grid of a plurality of rods, since no particularly large forces act.

Furthermore, the eccentric sleeve 14 may also be present in the stator 2, if, for example, the locking takes place in the radial direction in the rotor 3 as shown in DE19860025. The optional locking unit may also consist of the components piston, spring, eccentric sleeve 14 and cartridge. Depending on the design, the tooth contour on the eccentric sleeve 14 does not necessarily require a counter contour, but can also generate this itself by plastic deformation of the counterpart.

Designation of the camshaft adjuster

stator

rotor

Simply locking device

Exzenterverriegelungseinrichtung

stator base

Rotor body

locking bolt

locking spring

lock holder

locking receptacle

scenery

eccentric

locking spring

locking bolt

length

thickness

scenery

outer periphery

Outer circumference center

inner circumference

Inner circumferential center

eccentricity

locking receptacle

sleeve base

Werkzeugeingreifkontur

external teeth

internal gearing

chamfer

Hydraulic fluid passageway

Claims

claims

1 . A vane-type hydraulic camshaft adjuster (1) comprising a stator (2) and a rotor (3), the rotor (3) being rotatably supported relative to the stator (2), and at least one locking pin (16) being provided to engage the rotor

In contact with a link (19) to limit the rotor (3) to the stator (2) at least in one direction of rotation, characterized in that the locking bolt (16) leading bearing element (14) is adjustable so that an outer contour of the locking bolt (16) in contact with the backdrop (19) can be brought.

2. camshaft adjuster (1) according to claim 1, characterized in that the bearing element (14) is formed as a sleeve, within which the locking bolt (16) is mounted axially movable.

3. camshaft adjuster (1) according to one of claims 1 to 2, characterized in that the bearing element (14) is rotatably inserted in the rotor (3).

4. camshaft adjuster (1) according to one of claims 1 to 3, characterized in that the locking bolt (16) in the bearing element (14) is guided eccentrically.

5. camshaft adjuster (1) according to one of claims 1 to 4, characterized in that a second locking bolt (9) is provided to at

In contact with a second link (13) to limit the rotor (3) to the stator (2) at least in a second direction of rotation.

6. Camshaft adjuster (1) according to one of claims 1 to 5, characterized in that the camshaft adjuster (1) can be locked in a center locking position.

7. camshaft adjuster (1) according to one of claims 1 to 6, characterized in that the bearing element (14) in the rotor (3) is fixable in different positions.

8. camshaft adjuster (1) according to one of claims 1 to 7, characterized in that the bearing element (14) is designed so that this by rotation is adjustable, and the bearing element (14) can be fixed by a movement in the axial direction.

9. camshaft adjuster (1) according to one of claims 1 to 8, characterized in that the bearing element (14) cohesively, non-positively and / or positively in its position on the rotor (3) can be fixed.

10. camshaft adjuster (1) according to one of claims 1 to 9, characterized in that on the bearing element (14) has an external toothing (28) is provided, and on the rotor (3) an internal toothing (29) is provided, which engage with each other are prepared.