DE102009014338A1 - Arrangement for use with hydraulic camshaft adjuster for internal combustion engine, has drive component, and another drive component connected with camshaft in drive connection - Google Patents

Abstract

The arrangement (1) has a drive component (3), and another drive component (4) connected with a camshaft in drive connection. Three pressurizing medium paths (20,33,40) are provided, of which the former pressurizing medium path is connected with a pressure chamber, where the latter pressurizing medium path is connected with another pressure chamber and the third pressurizing medium path is connected with the hydraulic locking unit in fluidic manner.

Description

Field of the invention

The Invention is in the technical field of internal combustion engines and relates to its genus an arrangement with a hydraulic camshaft adjuster for one Internal combustion engine according to the preamble of claim 1.

State of the art

In Internal combustion engines with mechanical valve control become gas exchange valves through the cams of a camshaft driven by a crankshaft actuated, being over Arrangement and shape of the cam, the timing of the valves fixed are. about a change The phase angle between the crankshaft and camshaft can vary depending on the momentary operating state of the internal combustion engine targeted influence be taken on the timing of the valves, thereby advantageous Effects, such as a reduction in fuel consumption and the Pollutant production can be achieved.

Well known is the use of special devices for adjusting the phase position between crankshaft and camshaft, which is usually referred to as "camshaft adjuster" become.

Generally Include camshaft adjuster via a drive wheel with the Crankshaft in drive connection standing drive part and a Camshaft-fixed output part, as well as between input and output part switched adjusting mechanism, which the torque from arrival to transmits the output part and a Adjustment and fixation of the phase position between these two allows.

In a common one Construction as a hydraulic rotary piston adjuster is the drive part as outer rotor and the output member formed as an inner rotor, wherein outer and Internal rotor rotatable and concentric about a common axis of rotation are arranged. In the radial gap between the outer and inner rotor is at least one hydraulic chamber is formed by one of the two rotors, into which a wing connected to the other rotor extends, whereby the hydraulic chamber in a pair of opposing pressure chambers is shared. By targeted pressurization of the pressure chambers can Outdoor and Inner rotor are adjusted relative to each other, thereby changing To cause the phase angle between the crankshaft and camshaft.

During the Operating the internal combustion engine, alternating torques occur at the camshaft, the inadequate Pressure medium supply, as for example during the starting phase or in Idling the case is an uncontrolled movement of the inner rotor can effect. This can result in the wings within the pressure chambers hitting back and forth, thereby promoting premature wear and tear unpleasant noises caused. In addition, the phase angle varies in this case between crankshaft and camshaft strong, so that the internal combustion engine is not starts or runs restless.

Around To avoid this, are hydraulic rotary piston adjuster usually with a locking device for non-rotatable locking of Outside- and inner rotor in a base position, for launch the engine thermodynamically favorable phase position equipped. The Choice of base position depends from the specific design of the internal combustion engine and can be a Early-, Late or Be intermediate position, wherein, based on the direction of rotation of the camshaft, the late position a maximum adjustment of the inner rotor in the wake direction, the early position a maximum adjustment of the inner rotor in the forward direction and the intermediate position of a rotational angle position between these two Ending positions corresponds. The middle position denotes a position at least approximately in the middle between early and late position located.

A Such locking device for non-rotatable locking of Outer and inner rotor in Base position typically includes at least one in one the two rotors recorded locking pin, the base position in form-fitting Engagement with the other rotor can be brought and Hydraulically unlocked by frontal pressurization can be.

Rotationskolbenversteller with a hydraulically unlockable locking device for non-rotatable locking of outer and inner rotor in base position are widely described in the patent literature. With reference to the 4A and 4B Now, a conventional Rotationskolbenversteller will be described in more detail.

4A shows an axial sectional view along section line AA of a 4B in a radial section view shown Rotationskolbenverstellers. Accordingly, the includes on the front side of a camshaft 204 attached rotary piston adjuster 201 a external rotor in drive connection with a crankshaft (not shown) 202 and one with the camshaft 204 rotatably connected inner rotor 203 , which are mutually adjustable in rotation, concentrically arranged about a common axis of rotation. The one with the crankshaft via a drive wheel 205 drive-connected external rotor 202 has an outer ring 206 on, on the inside catch radial partitions 207 are arranged, which together with a first and second side plate 208 . 209 and a rotor hub 210 of the inner rotor 203 distributed in the circumferential direction arranged hydraulic chambers 211 limit. The two side plates 208 . 209 and the outer ring 206 are by axial screws 212 clamped together, with the rotor hub 210 of the inner rotor 203 through a into a threaded bore of the camshaft 204 screwed in tension screw 213 together with a jack 214 and an oil rotary union 215 with the camshaft 204 is tense. At the rotor hub 210 are a plurality of wings 216 attached to each hydraulic chamber 211 divided into a pair of mutually acting pressure chambers A, B. A supply of the pressure chambers A, B with pressure medium, usually pressure oil from the lubricating oil circuit of the internal combustion engine, is effected by a control valve, not shown, wherein the pressure medium via a camshaft bearing 217 and the oil rotary union 215 , as well as their first radial channels 218 and their second radial channels 219 in an inner ring channel 220 and a first outer annular channel 221 arrives. The two ring channels 220 . 221 be through a into a cavity of the oil rotary union 215 used oil separation sleeve 222 shaped, being between the clamping screw 213 and the oil separation sleeve 222 the inner ring channel 220 and between the oil separation sleeve 222 and the oil rotary union 215 the first outer annular channel 221 is shaped. From the inner ring channel 220 the pressure medium passes through first radial bores 223 in a second outer annular channel 224 and from there via second radial bores 225 into the pressure chambers A. From the first outer annular channel 221 the pressure medium passes through third radial bores 226 into the pressure chambers B.

The rotary piston adjuster 201 is equipped with a locking device for non-rotatable locking of inner and outer rotor 202 . 203 equipped in basic position, which in a first blind hole 228 the rotor hub 210 recorded, axial locking pin 227 includes. The locking pin 227 is by a compression spring 229 in a second blind hole 230 the second side plate 209 urged, whereby the inner and outer rotor are locked in basic position. By frontal loading with pressure medium of the locking pin 227 in the first blind hole 228 be pushed back. For this purpose there is an end face 231 of the locking pin 227 via a radial connecting channel 232 with the second outer annular channel 224 in fluidic connection.

Thus, in the conventional rotary piston adjuster 201 the locking pin 227 connected to the pressure medium supply of the pressure chambers A, so that the locking device can only be hydraulically unlocked when the pressure chambers A are acted upon with pressure medium, but what the control options for the Rotationskolbenversteller 201 limits. For example, a lock in the base position is not possible if a hydraulic advance (ie, pressurizing the pressure chambers A) is required to reach the base position. In this. In this case, special measures must be taken to mechanically adjust the inner rotor in the direction of "early" to reach the base position, such as, for example, a spiral spring interconnecting the inner and outer rotors 233 , which the inner rotor 203 against the outer rotor 202 in the direction of "early".

Object of the invention

In contrast, the object of the present invention is to provide an arrangement with a hydraulic camshaft adjuster for an internal combustion engine, by which in particular the above in connection with the 4A and 4B explained disadvantage can be avoided.

Solution of the task

These and further objects are according to the proposal of the invention an arrangement with a hydraulic camshaft adjuster for an internal combustion engine with the characteristics of the independent Patent claim solved. Advantageous embodiments of the invention are characterized by the features the dependent claims specified.

According to the invention is a Arrangement with a hydraulic camshaft adjuster, in particular Rotary piston adjuster, for adjusting the angular position (phase position) shown crankshaft and camshaft of an internal combustion engine.

To In their genus, the arrangement comprises a camshaft phaser, the one with a crankshaft in drive connection engageable or crankshaft-resistant drive part (for example, outer rotor) and a camshaft rotatably connected to a camshaft or fixed Stripping part (for example, inner rotor), which in concentric Arrangement re a common axis of rotation rotatably mounted to the drive part is and its angular position to the drive part by means of a hydraulic adjusting mechanism is adjustable, includes. The hydraulic Actuating mechanism comprises at least one oppositely acting pressure chamber pair, consisting of a first pressure chamber, which, for example, in Drive direction of the camshaft leads vorse, and a second pressure chamber, which lags, for example, in the drive direction of the camshaft.

He further comprises a hydraulically unlockable locking device, through which input and output part in a locking rotational position (Base position) are rotatably locked. The locking device generally includes at least one pair of engagement with a in Input or output part received latch (eg locking pin) and a bolt gate formed in the corresponding other part, wherein the bolt, for example, by the spring force of a compression spring pushed into the bar scenery which he can reach into locking rotary position and through Frontal pressurization be pushed back with pressure medium in his recording can to inner and outer rotor to unlock. The locking device can in particular a A plurality of such engagement pairs include, for example, in Circumferential distribution evenly are arranged.

Draws according to the invention the arrangement with camshaft adjuster in a significant way characterized in that at least three separately acted upon with pressure medium Pressure medium paths are set up, of which a first pressure medium path with the at least one first pressure chamber, a second pressure medium path with the at least one second pressure chamber of the at least one opposing pressure chamber pair and a third pressure medium path with the hydraulic locking device fluidically connected is. Contains this one of these pressure medium paths a the camshaft (for example in the form of an annular channel) surrounding pressure medium channel, using a disposed between the inner rotor and a camshaft outer peripheral surface Insert is shaped. The insert may for this purpose, for example axially between the inner rotor and the camshaft outer peripheral surface be tense. The surrounding the camshaft pressure medium channel is used in particular for the transfer of Pressure medium between the camshaft and the inner rotor and is in his pressure medium path accordingly each to a pressure medium line the camshaft and the inner rotor fluidly connected.

By with the help of the insert for forming the camshaft surrounding Pressure medium channel shaped pressure medium path, the arrangement advantageously with a relatively small axial space will be realized. In particular, this can apply to one in the inner rotor or in the camshaft shaped annular channel for transferring the pressure medium between Internal rotor and camshaft are omitted. Similarly, in case that camshaft and inner rotor are aligned with each other Holes are provided, a relatively large timing error between Inner and outer rotor due to an unavoidable tolerance chain during the assembly of Drive and driven part of the camshaft adjuster are avoided.

at a technically easy to implement first embodiment of inventive arrangement If the insert is in one with the camshaft adjuster, in particular stripping section, connected insert section from an axial sleeve section, which with a the inner rotor facing, radial first sleeve end face of a radial first Abtriebsteilanlagefläche the stripping section is applied. It may be advantageous if the insert has a radial Distance from the drive part has to radial mounting tolerances compensate for the centering of the output part on the camshaft.

at another, technically easy to implement second embodiment the inventive arrangement If the insert is in one with the camshaft adjuster, in particular stripping section, connected insert section from an axial sleeve section, which with an axial sleeve outer peripheral surface of a axial second driven part abutment surface of the driven part abuts. in this connection It may be advantageous if the second Abtriebsteilanlagefläche and the sleeve outer peripheral surface at least in the adjacent sections in fit each cone-shaped are (cone connection), thereby the pressing force of the connection at an axial distortion of the output part, insert and camshaft to increase. Furthermore, it may be advantageous if the insert part has an axial Distance to the driven part and / or a radial distance to the drive part, to thereby compensate for axial and / or radial mounting tolerances.

In a further, technically simple to implement third embodiment of the arrangement according to the invention, the insert consists in an affiliated with the camshaft adjuster, in particular stripping section insert portion of an axial sleeve portion which abuts an axial third Abtriebsteilanlagefläche the stripping member with an axial sleeve inner peripheral surface. It may be advantageous if the third Abtriebsteilsanlagefläche and the axial sleeve inner peripheral surface at least in the abutting portions are in each case in a tapered conical shape (cone connection) to increase the pressing force of the connection during axial clamping of the driven part, insert part and camshaft. Furthermore, it may be advantageous if the insert part has an axial distance to the driven part and / or a radial distance to the drive part in order to compensate for axial and / or radial assembly tolerances. In a further, technically easy to implement fourth embodiment of the arrangement according to the invention, the insert part consists in a with the camshaft adjuster, insbesonde Re driven part, connected insert portion of an axial sleeve portion which is received with an edge portion in an axial groove of the driven part. It may be advantageous if an axial groove wall and an axial groove wall opposite arranged sleeve inner peripheral surface at least in the adjacent sections in a fit each cone (cone connection) and / or an axial groove wall and the axial groove wall opposite arranged sleeve outer peripheral surface at least in the adjacent sections in fit each have a conical shape (cone connection) to increase the pressing force of the compound during axial clamping of the driven part, insert and camshaft.

According to one another, fifth Embodiment of the arrangement according to the invention is between the axial sleeve portion and the output part, a sealing means is arranged to the pressure fluid tightness to improve the arrangement.

at another, technically easy to implement sixth embodiment the inventive arrangement If the insert is in one with the camshaft adjuster, in particular stripping section, connected insert section from an axial sleeve section, to the radially outwardly directed first radial board to a the inner rotor facing radial first Sleeve end face molded is. Here, the first radial board in a radial recording of the drive part and is from the radial recording held. It may be advantageous if the first radial board taken up with radial play in the radial receptacle of the drive part is to compensate for radial mounting tolerances.

at another, technically easy to implement seventh embodiment the arrangement according to the invention, which in particular can be combined with the first to sixth embodiments is, the insert is in a connected to the camshaft Insert portion of an axial sleeve portion to which an inwardly directed second Radial board facing away from the inner rotor, radial second Sleeve end face molded. Here, the second radial board is located with a radial board contact surface of a Radial first camshaft bearing surface, which from one to the outer peripheral surface of the Camshaft molded camshaft paragraph is formed. In this Case, it may be advantageous if an edge of the radial board one radial distance from the camshaft outer peripheral surface, to compensate for radial assembly tolerances.

at another, technically easy to implement eighth embodiment the arrangement according to the invention, which in particular can be combined with the first to sixth embodiments is, the insert is in a connected to the camshaft Insert portion of an axial sleeve portion, wherein a sleeve inner peripheral surface of a axial second camshaft bearing surface is applied, of a formed on the camshaft outer peripheral surface Camshaft heel is formed. In this case, it may be beneficial if between the sleeve inner peripheral surface and the second camshaft bearing surface a sealant is arranged. In this case it can continue be advantageous if the sleeve inner peripheral surface and the second camshaft contact surface at least in the adjacent sections in fit respectively conically are formed (cone connection) to the pressing force of the connection during axial clamping of output part, insert part and camshaft to increase. In addition, it may still be beneficial if in juxtaposition to a radial Nockenwellenabsatzfläche the camshaft paragraph an inward directed inner ring to the sleeve section is formed. In this case, it may be particularly advantageous if between the inner ring and the radial camshaft landing surface of the Camshaft sales a sealant is arranged to the fluid seal to increase the arrangement.

The Invention further extends to an internal combustion engine, provided with at least one arrangement as described above is.

Brief description of the drawings

The Invention will now be explained in more detail with reference to embodiments, wherein Reference to the attached Drawings is taken. Same or equivalent elements are denoted in the drawings by the same reference numerals. It demonstrate:

1 a schematic axial view for illustrating a first embodiment of the camshaft adjuster according to the invention;

2A -C schematic axial views to illustrate other embodiments of the camshaft adjuster according to the invention with reference to various variants of the rotary piston of 1 ;

3 an overview of advantageous combination options of in 2A -C illustrated variants of the rotary piston of the invention of 1 ;

4A B is an axial and a radial sectional view illustrating a herkömmli chen rotary piston adjuster.

Detailed description of the drawings

The one concerning conventional rotary piston adjuster 4A and 4B were already explained in detail in the introduction, so that there is no need for further description here.

In 1 is as a first embodiment of the arrangement according to the invention 1 one on a camshaft 5 fixed rotary piston adjuster 2 illustrated in an axial section view. The rotary piston adjuster 2 serves as usual for transmitting torque and for adjusting and fixing a rotational angle position between the crankshaft and camshaft of an internal combustion engine.

The rotary piston adjuster 2 includes a crankshaft (not shown) via a sprocket 6 and a chain drive (not shown) in drive connection outer rotor 3 and one with the camshaft 5 rotatably connected inner rotor 4 , wherein outer and inner rotor concentrically about a common axis of rotation 7 the camshaft 5 are arranged rotationally adjustable to each other.

In the radial space between the outer and inner rotor are by an outer ring 11 of the outer rotor 3 a plurality of (not shown) formed hydraulic chambers, in each case one with the inner rotor 4 connected wing 18 extending, whereby each hydraulic chamber is divided into a pair of opposing pressure chambers. By selective pressurization of the oppositely acting pressure chambers, a rotational angle position of the inner rotor 4 to the outer rotor 3 be adjusted. This forms the outer rotor 3 a pressure-tight housing for the inner rotor 4 wherein the pressure chambers through a first and second end face side plate 12 . 13 are sealed axially pressure-tight. The two side plates 12 . 13 are arranged by a plurality of circumferentially uniformly distributed, axial mounting screws with the outer ring 11 braced, what in 1 not shown in detail. The rotary piston adjuster 2 is similar in terms of the structure of the two rotatably mounted rotors 3 . 4 and the hydraulic adjusting mechanism for changing the rotational angle position between the rotors 3 . 4 a conventional Rotationskolbenversteller as in the beginning in connection with 4A and 4B already described. To avoid unnecessary repetition, reference is made to the statements made there.

The rotary piston adjuster 2 is with a central axial opening 17 provided, resulting from a central rotor opening 14 a rotor hub 8th of the inner rotor 4 , as well as a first plate opening 15 the first side plate 12 and a second plate opening 16 the second side plate 13 composed. About the central axial opening 17 penetrating clamping screw 10 is the inner rotor 4 at a radially inwardly directed annular rotor shoulder 26 with a camshaft end face 9 rotatably connected, with the clamping screw 10 in a threaded bore, not shown, a central camshaft opening 27 is screwed.

For non-rotatable locking of outer and inner rotor 3 . 4 in the middle position, for example, a conventional, not shown locking device is provided with at least one axial locking pin, for example, in a receptacle in the inner rotor 4 is received and by a compression spring in the axial direction in one of the first side plate 12 shaped latch backdrop is crowded. In order to unlock the locking pin, this can be subjected to pressure on the front side and into its receptacle in the inner rotor 4 be pushed back. Since the basic structure of such a locking device is known in the art and in conjunction with 4A and 4B has been described in detail, it is not necessary to go into detail here.

The camshaft 5 is as usual in a formed in the cylinder head or a cylinder head fixed component camshaft bearing 19 rotatably mounted.

In the in 1 illustrated rotary piston adjuster 2 are provided for the pressure medium supply of the hydraulically counteracting pressure chambers and the locking device respectively separate or separately acted upon with pressure medium pressure medium paths. For pressure medium supply pressure medium of the lubricating oil circuit of the internal combustion engine is used, for example. For better clarity are in 1 illustrates the various pressure medium paths only in a schematic manner by dashed lines.

This includes a first pressure medium path 20 a to a (not shown) conventional control valve for controlling pressure medium flows of a Rotationskolbenverstellers, which is well known to those skilled in particular from the patent literature and need not be further explained here, connected first radial line 21 of the camshaft bearing 19 , in an unspecified, in a bearing inner surface 28 integrated ring groove of the camshaft bearing 19 empties. This annular groove is in turn connected to a second radial line 22 the camshaft 5 fluidly connected, which with one end in a camshaft outer peripheral surface 29 empties.

Alternatively, it would be equally possible that in the bearing inner surface 28 incorporated annular groove in the camshaft outer peripheral surface 29 is incorporated and the second radial line 22 opens into the annular groove.

At its other end opens the second radial line 22 in a the axis of rotation 7 surrounding first annular channel 23 which extends in the axial direction. The first ring channel 23 is between a shaft outer surface 25 one outside the threaded hole of the camshaft 5 located shaft portion 24 and a rotor shoulder inner circumferential surface 30 of the rotor paragraph 26 and a camshaft inner peripheral surface 31 the camshaft opening 27 shaped as a recessed annulus. To the first ring channel 23 is a first group of third radial lines 32 fluidly connected, each in a same side of the wing 18 arranged pressure chambers (for example, in the direction of rotation of the camshaft trailing pressure chambers A) of the hydraulic chambers open. About the first print medium path 20 can thus pressure medium to each on one side of the wing 18 arranged directed pressure chambers or derived from these.

One from the first pressure medium path 20 separately acted upon with pressure medium second pressure medium path 33 includes a fourth radial line connected to the same control valve for controlling pressure medium flows 34 of the camshaft bearing 19 , in a non-illustrated annular groove of the cam shaft bearing 19 which, in turn, on the camshaft outer peripheral surface 29 with a fifth radial line 35 the camshaft 5 fluidically connected, which with its one end to the camshaft outer peripheral surface 29 empties.

Alternatively, it would be equally possible that in the bearing inner surface 28 incorporated annular groove in the camshaft outer peripheral surface 29 is incorporated and the fifth radial line 35 opens into the annular groove.

At the other end is the fifth radial line 35 in a first axial line 36 the camshaft 5 over which on the camshaft end face 9 in one, the axis of rotation 7 surrounding second annular channel 37 empties. The second ring channel 37 is in the form of an Axialringnut in one of the camshaft 5 facing radial rotor hub end face 38 of the rotor paragraph 26 incorporated.

Alternatively it would be equally possible that the second annular channel 37 in the form of a rotation axis 7 surrounding Axialringnut in the camshaft end face 9 is incorporated.

To the second ring channel 37 is a second group of sixth radial lines 39 fluidly connected, in each case on the other side of the wing 18 arranged pressure chambers (for example, in the direction of rotation of the camshaft vorseilende pressure chambers B) of the hydraulic chambers open. Via the second pressure medium path 33 can thus pressure medium to each on the other side of the wing 18 located pressure chambers are passed or derived from these.

One from both the first print medium path 20 as well as the second pressure medium path 33 separately acted upon with pressure medium third pressure medium path 40 includes a seventh radial conduit connected to the same control valve for controlling fluid flows 41 of the camshaft bearing 19 , in a not shown, the axis of rotation 7 circumferential annular groove of the camshaft bearing 19 which, in turn, on the camshaft outer peripheral surface 29 with an on the camshaft outer peripheral surface 29 opening eighth radial line 42 the camshaft 5 fluidically connected.

Alternatively, it would be equally possible that in the bearing inner surface 28 incorporated annular groove in the camshaft outer peripheral surface 29 is incorporated and the eighth radial line 42 opens into the annular groove.

The eighth radial line 42 goes into a second axial line 43 the camshaft 5 which, in turn, into a ninth radial line 44 transferred to the camshaft outer peripheral surface 29 in a third ring channel 45 empties. To the third ring channel 45 is an axially or radially oblique slanted line 46 (or in the case of several locking pins, a third group of inclined lines 46 ) fluidly connected, which open into the locking gate for the locking pin to apply the locking pin end face with pressure medium. About the third pressure medium path 40 Thus pressure medium can be directed to the (or the) Verrieglungspin (s) regardless of an application of pressure to the pressure chambers or derived therefrom.

The third ring channel 45 serves to transfer pressure medium between the camshaft 5 and the inner rotor 4 , It is defined by a radial first and second boundary surface 48 . 49 which are spaced apart in the axial direction, and a radial third and fourth boundary surface 50 . 51 , which are arranged in the radial direction at a distance from each other, bounded. For this purpose, one is the camshaft 5 radially widening first camshaft paragraph 47 on the camshaft outer peripheral surface 29 formed in the form of a collar, whose the inner rotor 4 to facing, radial second camshaft heel surface 94 the first boundary surface 48 forms.

Furthermore, an insert 52 arranged, which is formed in the axial section in the form of a corner angle or in the perspective view of an axial sleeve portion 53 with a radially outwardly directed first radial board 54 standing at one of the rotor hub 8th facing the end of the sleeve section 53 is formed having. With a sleeve inner circumferential surface 55 lies the sleeve section 53 of the insert part 52 an axial first camshaft landing surface 57 the first camshaft paragraph 47 at. A radial first Bordstirnfläche 56 of the first radial shelf 54 lies the rotor hub end face 38 at. This becomes the second boundary surface 49 of the third ring channel 45 through between the first radial board 54 and the camshaft outer peripheral surface 29 shaped rotor hub end face 38 educated. Which is between the first camshaft heel 47 and the rotor hub end face 38 extending sleeve inner circumferential surface 55 forms the third boundary surface 50 of the third ring channel 45 , Which is between the first camshaft heel 47 and the rotor hub end face 38 extending camshaft outer peripheral surface 29 forms the fourth boundary surface 51 ,

How out 1 can be seen, is a diameter of the camshaft 5 in the area of the fourth boundary surface 51 against a diameter of the camshaft 5 on the axially opposite side of the camshaft paragraph 47 decreases, reducing the volume of the third ring channel 45 is enlarged.

The insert part 52 is over the first radial board 54 in a radially extending axial plate recess 58 the second plate opening 16 the second side plate 13 recorded and held in it.

For mounting the rotary piston adjuster 2 on the camshaft 5 For example, first the rotary piston adjuster 2 pre-assembled, in particular the insert 52 in the plate recess 58 the second side plate 13 is placed. Here, the insert part 52 not from the plate recess 58 fall out. Subsequently, the inner rotor 4 centered to the camshaft 5 attached. The insert part 52 is with a certain degree of radial tolerance provided by a radial first annulus 80 , in the plate recess 58 recorded so that the inner rotor 4 to the camshaft 5 can be centered without this centering through the insert part 52 is impaired (radial tolerance compensation). Due to the free positioning tion of the sleeve section 53 on the first camshaft heel 47 In addition, a radial tolerance compensation is possible. Because the insert part 52 during pre-assembly of the rotary piston adjuster 2 Already attached to this is in industrial mass production no additional installation work for the insert 52 required on the assembly line. The insert part is used during assembly of the inner rotor 4 on the camshaft 5 axially not braced, so possibly with the outer rotor 3 can turn. Over a sufficient axial length of the sleeve portion 53 it is possible to ensure sufficient leak-tightness.

Only for the sake of completeness it should be noted that the first camshaft paragraph 47 also part of the camshaft bearing 19 can be.

With reference to the 2A - 2C Now different variants of the rotary piston adjuster 1 from 1 explained. To avoid unnecessary repetition, only the differences to those in 1 illustrated embodiment and otherwise reference is made to the statements made there.

Be the first 2A and 2 B considered, wherein in respective Axialschnittanschichten fifteen variants for the design and connection of a with the Rotationskolbenversteller 2 connected insert portion of the insert 52 are shown. The fifteen variants are designated by the letters "A" - "O" for ease of reference. The variants are each circularly symmetrical about the axis of rotation 7 the camshaft 5 educated. With the exception of the variant "L", which the embodiment of 1 corresponds, becomes the insert part 52 for its attachment during assembly of the inner rotor 4 on the camshaft 5 between the rotor hub 8th and the camshaft outer surface 29 the camshaft 5 axially braced.

In variant "A" has the insert 52 in the area of the inner rotor 4 only the sleeve section 53 on, with a radial first sleeve end face 60 the rotor hub end face 38 is applied. Between an axial edge surface 59 the second plate opening 16 the second side plate 13 and the sleeve section 53 is a radial first annular gap 61 before, the radial tolerance compensation at the camshaft 5 Centered assembly of Rotationskolbenverstellers 2 on the camshaft 5 can serve. An axial tolerance compensation can in the axial compression of the insert 52 respectively. This variant does not allow pre-assembly of the insert 52 on the rotary piston adjuster 2 ,

Variant "B" differs from variant "A" only in that the first annular gap 61 has a much smaller radial dimension, with a radial clearance tolerance radial compensation is possible and a centering of the insert part by a small radial clearance 52 over the second side plate 13 he follows. An axial tolerance compensation takes place during the axial compression of the insert 52 between the rotor hub 8th and the camshaft 5 , This variant does not allow pre-assembly of the insert 52 on the rotary piston adjuster 2 ,

The variant "C" differs from variant "A" in that the inner rotor 4 with a rotor hub recess 62 is provided, which has an axial recess surface 63 for conditioning a sleeve outer peripheral surface 64 of the sleeve section 53 shaped. The insert part 52 can through the rotor hub 8th over the sleeve outer peripheral surface 64 be centered. The insert part 52 is between the rotor hub 8th and the camshaft 5 axially compressed. Through a second annular gap 65 can be done an axial tolerance compensation. By axial compression, a radial tolerance compensation can take place. The insert part 52 Already at the pre-assembly of the camshaft adjuster 2 at the rotor hub 8th be attached. The insert part 52 is through the rotor hub 8th over the sleeve outer peripheral surface 64 centered.

The variant "D" differs from the variant "C" in that the axial recess surface 63 tapered conically in the axial direction and a first inclined surface 66 shaped. Similarly, the sleeve outer peripheral surface 64 through a second inclined surface 67 provided with a conically tapered fit, whereby a cone connection is created in the axially clamped state. An axial tolerance compensation takes place by axial compression during assembly of the rotary piston adjuster 2 on the camshaft 5 , Similarly, a radial tolerance compensation by axial compression in the assembly of Rotationskolbenverstellers 2 on the camshaft 5 respectively. Due to the cone connection can during axial distortion during assembly of the rotary piston adjuster 2 on the camshaft 5 a pressing pressure between the inner rotor 4 and the sleeve section 53 increase. This variant does not allow pre-assembly of the insert 52 on the rotary piston adjuster 2 , The insert part 52 is through the rotor hub 8th over the sleeve outer peripheral surface 64 centered.

In variant "E", unlike variant "C", there is no rotor hub recess 62 but an annular first axial rib 68 to the rotor hub 8th molded, whose the camshaft 5 facing first axial rib surface 69 as a contact surface for the sleeve outer peripheral surface 64 of the sleeve section 53 serves. Between a radial first sleeve end face 60 and the rotor hub end face 38 is an axial third annular gap 70 shaped as an axial tolerance compensation during assembly of the rotary piston adjuster 2 on the camshaft 5 serves. A radial tolerance compensation can during the axial compression during assembly of the rotary piston adjuster 2 on the camshaft 5 respectively. The insert part 52 can during the pre-assembly of the camshaft adjuster 2 attached to this. The insert part 52 is through the first axial rib 68 the rotor hub 8th over the sleeve outer peripheral surface 64 centered.

In variant "F" is to the rotor hub 8th an axial rotor hub projection 71 formed, which has an axial projection surface 72 for conditioning the sleeve inner peripheral surface 55 of the sleeve section 53 forms. Between the radial sleeve end face 60 and the rotor hub end face 38 is an axial fourth annular gap 73 shaped as an axial tolerance compensation during assembly of the rotary piston adjuster 2 on the camshaft 5 serves. A radial tolerance compensation can be achieved by the axial compression during assembly of the rotary piston adjuster 2 on the camshaft 5 respectively. The insert part 52 Already at the pre-assembly of the camshaft adjuster 2 at the rotor hub 8th be attached. The insert part 52 is through the rotor hub projection 71 over the sleeve inner peripheral surface 55 centered.

The variant "G" differs from the variant "F" only in that the axial projection surface 72 a third inclined surface 74 has, which tapers conically in the axial direction. Similarly, the sleeve inner peripheral surface 55 with a fourth inclined surface 75 provided, whereby a cone connection between the sleeve portion 53 and the rotor hub projection 71 is created. By this measure, during axial distortion during assembly of the rotary piston adjuster 2 on the camshaft 5 a pressing pressure between the inner rotor 4 and the sleeve section 53 increase. A radial and axial tolerance compensation can be achieved by the axial compression during assembly of Rotationskolbenverstellers 2 on the camshaft 5 respectively. This variant does not allow pre-assembly of the insert 52 on the rotary piston adjuster 2 , The insert part 52 is through the rotor hub projection 71 over the sleeve inner peripheral surface 55 centered.

The variant "H" differs from the variant "E" in that an annular second axial rib 76 to the rotor hub 8th is molded, whose from the camshaft 5 remote second axial rib surface 77 as a contact surface for the sleeve inner peripheral surface 55 of the sleeve section 53 serves. Between the radial sleeve end face 60 and the rotor hub end face 38 is a fifth annular gap 78 shaped as an axial tolerance compensation during assembly of the rotary piston adjuster 2 on the camshaft 5 serves. A radial tolerance compensation can during the axial compression during assembly of the rotary piston adjuster 2 on the camshaft 5 respectively. The insert part 52 can during the pre-assembly of the camshaft adjuster 2 attached to this. The insert part 52 is through the second axial rib 76 over the sleeve inner peripheral surface 55 centered.

In the variant "I" is in the rotor hub end face 38 an axial ring groove 79 incorporated, in which an end portion of the sleeve portion 53 is received positively and / or non-positively. Between the radial sleeve end face 60 and the rotor hub end face 38 is an axial second annulus 81 shaped as an axial tolerance compensation during assembly of the rotary piston adjuster 2 on the camshaft 5 serves. A radial tolerance compensation takes place during the axial compression during the assembly of the rotary piston adjuster 2 on the camshaft 5 , The insert part 52 can during the pre-assembly of the camshaft adjuster 2 attached to this. The insert part 52 is through the Axialringnut 79 centered.

The variant "J" differs from the variant "1" in that the radially outer first annular groove surface 82 a fifth inclined surface 83 has, which tapers conically in the axial direction. Similarly, the sleeve outer peripheral surface 64 with a conically tapered sixth bevel 84 provided, whereby a cone connection between the sleeve portion 53 and the Axialringnut 79 is created. By this measure, during axial distortion during assembly of the rotary piston adjuster 2 on the camshaft 5 a pressing pressure between the inner rotor 4 and the sleeve section 53 increase. Through the second annulus 81 is an axial tolerance compensation during assembly of the rotary piston adjuster 2 on the camshaft 5 possible. A radial tolerance compensation takes place during the axial compression during the assembly of the rotary piston adjuster 2 on the camshaft 5 , The insert part 52 can during the pre-assembly of the camshaft adjuster 2 not be attached to this. The insert part 52 is through the Axialringnut 79 centered.

In contrast, in the variant "K" has a radially inner second annular groove surface 85 a seventh bevel 86 on, which tapers conically in the axial direction. Similarly, the sleeve inner peripheral surface 55 with a conically tapered eighth bevel 87 provided, whereby a cone connection between the sleeve portion 53 and the Axialringnut 79 is created. Through the second annulus 81 is an axial tolerance compensation during assembly of the rotary piston adjuster 2 on the camshaft 5 possible. A radial tolerance compensation can during the axial compression during assembly of the rotary piston adjuster 2 on the camshaft 5 respectively. The insert part 52 can during the pre-assembly of the camshaft adjuster 2 not be attached to this. The insert part 52 is through the Axialringnut 79 centered.

The variant "L" in the 1 shown embodiment, so that there is no need to go into detail here.

The variant "M" differs from variant "A" in that between the rotor hub end face 38 and the radial first sleeve end face 60 of the sleeve section 53 a trained here, for example in the form of an O-ring first ring seal 88 is arranged to prevent the leakage of the arrangement 1 to improve. An axial tolerance compensation during the assembly of the rotary piston adjuster 2 on the camshaft 5 can through the first ring seal 88 respectively. This variant does not allow pre-assembly of the insert 52 on the rotary piston adjuster 2 ,

In variant "N" is the sleeve section 53 with a first ring seal 88 encompassing sleeve end section 89 provided, wherein the sleeve portion 53 with the radial first sleeve end face 60 the rotor hub end face 38 is applied. Also in this case, an axial tolerance compensation during assembly of Rotationskolbenverstellers 2 on the camshaft 5 through the first ring seal 88 respectively. This variant does not allow pre-assembly of the insert 52 on the rotary piston adjuster 2 ,

The variant "O" differs from the variant "F" only in that between the axial projection surface 72 and the sleeve inner peripheral surface 55 of the sleeve section 53 a second ring seal 90 is arranged to prevent the leakage of the arrangement 1 to improve. In this case, a radial tolerance compensation in the assembly of Rotationskolbenverstellers 2 at. the camshaft 5 through the second ring seal 90 respectively. This variant allows a pre-assembly of the insert 52 on the rotary piston adjuster 2 , The insert part 52 is through the rotor hub projection 71 centered.

Be now 2C considered, wherein in each Axialschnittanschichten eight variants for the design and connection of one with the camshaft 5 connected insert portion of the insert 52 are shown. The eight variants are designated by numbers "1" - "8" for ease of reference. The variants are each circularly symmetrical about the axis of rotation 6 educated. The inserts are used for attachment between the rotor hub 8th and the camshaft outer surface 29 the camshaft 5 axially compressed. The eight variants for the design and connection of one with the camshaft 5 connected insert portion of the insert 52 Can with the above in conjunction with the 2A and 2 B described fifteen Va for designing and connecting one with the rotary piston adjuster 2 connected insert portion of the insert 52 be combined.

In variant "1" includes the insert 52 an axial sleeve section 53 , at the from the inner rotor 4 remote, radial second sleeve end face 91 a radially inwardly directed second radial board 92 is formed. The second radial board 92 lies with a second Bordstirnfläche 93 a radial second camshaft landing surface 94 the first camshaft paragraph 47 at. This allows the insert part 52 during assembly of the rotary piston adjuster 2 on the camshaft 5 between the rotor hub 8th and the camshaft heel 47 be tense. A radial tolerance compensation is by axial clamping during assembly of the rotary piston adjuster 2 on the camshaft 5 possible. This variant allows a pre-assembly of the insert 52 on the rotary piston adjuster 2 , The insert part 52 gets through the second radial board 92 on the camshaft 5 centered.

The variant "2" differs from the variant "1" only in that between the second radial board 92 and that of the camshaft outer peripheral surface 29 the camshaft 5 shaped fourth boundary surface 51 a sixth annular gap 95 is shaped. The sixth annular gap 95 allows for the centering of the inner rotor 4 with respect to the camshaft 5 a tolerance compensation of the insert 52 in the radial direction. This variant does not allow pre-assembly of the insert 52 on the rotary piston adjuster 2 , The insert part 52 does not get through the second radial board 92 on the camshaft 5 centered.

In variant "3" includes the insert 52 on the side of the camshaft 5 an axial sleeve section 53 , An on the camshaft outer peripheral surface 29 molded second camshaft heel 96 is stepped twice, with one the first bounding surface 48 forming the first stage, which the axial first camshaft landing surface 57 and the radial second camshaft landing surface 94 includes, and a second stage, which has an axial third camshaft heel surface 97 and a radial fourth camshaft landing surface 98 includes. This is the sleeve inner peripheral surface 55 of the sleeve section 53 the axial first camshaft landing surface 57 at. Between the radial second sleeve end face 91 and the radial fourth camshaft landing surface 98 is an axial seventh annular gap 99 before, by the axial tolerance compensation during assembly of the rotary piston adjuster 2 on the camshaft 5 is possible. A radial tolerance compensation can during the axial compression of the insert 52 between the inner rotor 4 and the camshaft 5 respectively. This variant allows pre-assembly of the insert 52 on the rotary piston adjuster 2 , The insert part 52 is through the sleeve section 53 on the camshaft 5 centered.

The variant "4" differs from the variant "3" in that between the sleeve section 53 and the axial first camshaft landing surface 57 the second camshaft paragraph 96 a trained example in the form of an O-ring third ring seal 100 is arranged to prevent the leakage of the arrangement 1 to improve. A radial tolerance compensation can in this variant by the third ring seal 100 respectively. Through the seventh annular gap 99 is an axial tolerance compensation during assembly of the rotary piston adjuster 2 on the camshaft 5 possible. This variant allows pre-assembly of the insert 52 on the rotary piston adjuster 2 , The insert part 52 is through the sleeve section 53 on the camshaft 5 centered.

In variant "5" includes the insert 52 on the camshaft 5 facing side an axial sleeve portion 53 to the one radially inwardly directed inner ring 101 is formed. The first camshaft heel 47 is single-stage. The sleeve section 53 lies with its sleeve inner circumferential surface 55 the axial first camshaft landing surface 57 at. The inner ring 101 is in the radial direction of the fourth boundary surface 51 spaced, so that the possibility of radial tolerance compensation by the axial compression in the assembly of Rotationskolbenverstellers 2 on the camshaft 5 consists. The inner ring 101 is also in the axial direction of the radial second Nockenwellenabsatzfläche 94 spaced, so that the possibility of axial tolerance compensation by axial compression in the assembly of Rotationskolbenverstellers 2 on the camshaft 5 consists. This variant allows pre-assembly of the insert 52 on the rotary piston adjuster 2 , The insert part 52 is through the sleeve section 53 on the camshaft 5 centered.

The variant "6" differs from the variant "5" in that between the sleeve inner peripheral surface 55 and the axial first camshaft landing surface 57 a trained example in the form of an O-ring fourth ring seal 102 is arranged to prevent the leakage of the arrangement 1 to improve. The inner ring 101 is also in the axial direction of the radial second Nockenwellenabsatzfläche 94 spaced, so that the possibility of axial tolerance compensation by axial compression in the assembly of Rotationskolbenverstellers 2 on the camshaft 5 consists. A radial tolerance compensation can by the fourth ring seal 102 respectively. This variant allows pre-assembly of the insert 52 on the rotary piston adjuster 2 , The insert part 52 becomes through the sleeve section 53 on the camshaft 5 centered.

The variant "7" differs from the variant "6" in that instead of a fourth ring seal 102 between the inner ring 101 and the radial second camshaft landing surface 94 a trained example in the form of a vulcanized flat gasket fifth ring seal 103 is arranged to the leak-tightness of the arrangement 1 to improve. In this case, both a radial and an axial tolerance compensation in the assembly of Rotationskolbenverstellers 2 on the camshaft 5 through the fifth ring seal 103 respectively. This variant allows pre-assembly of the insert 52 on the rotary piston adjuster 2 , The insert part 52 is through the sleeve section 53 on the camshaft 5 centered.

In variant "8" includes the insert 52 on the side of the camshaft 4 only a sleeve section 53 , The first camshaft heel 47 is simply stepped and with a ninth bevel 104 provided, which tapers conically in the axial direction. The sleeve inner peripheral surface 55 is for forming a cone connection with a tapered tapered tenth oblique surface in fit 105 Mistake. In this variant, both a radial and an axial tolerance compensation in the assembly of Rotationskolbenverstellers 2 on the camshaft 5 possible by axial compression. A pre-assembly of the insert 52 on the rotary piston adjuster 2 can not. The insert part 52 is through the sleeve section 53 on the camshaft 5 centered.

In 3 are in an overview designed as a matrix different advantageous combinations of in the 2A - 2 B shown variants with the in 2C shown variants. Here are the variants AO the 2A and 2 B each as lines and variants 1-8 of 2C each entered as columns. An advantageous combination is indicated by an "X".

Therefore can variant "A" with the Variants "1", "2" and "5" - "8" advantageous be combined. The variant "B" can be advantageous with the variants "2" - "8" be combined. The variant "C" can be advantageous with the variants "3" - "8" be combined. Variant "D" can be advantageous with variants "2" - "8" be combined. The variant "E" can be advantageous with the variants "3" - "8" be combined. The variant "F" can be advantageous with the variants "3" - "8" be combined. The variant "G" can be advantageous with the variants "2" - "8" be combined. The variant "H" can advantageously be combined with the variants "3" - "8" become. The variant "I" can with the Variants "3" - "8" advantageous be combined. The variant "J" can be advantageous with the variants "2" - "8" be combined. The variant "K" can be advantageous with the variants "2" - "8" be combined. The variant "L" can be advantageous with the variants "3" - "8" be combined. The variant "M" can be advantageous with the variants "1", "2" and "5" - "8" be combined. The variant "N" can be advantageous with the variants "1", "2" and "5" - "8" be combined. The variant "O" can be advantageously combined with the variants "1" - "8" become.

In the embodiments shown above for the Design of the rotor side or camshaft side sections of the insert part, the third pressure medium path, including the using the third insert between the inner rotor and the Camshaft outer peripheral surface shaped third Ring channels, alike used for pressure medium supply of the first or second pressure chambers become.

Of the independently from the other two pressure fluid paths acted upon with pressure medium third Pressure medium path allows in an advantageous manner that the arrangement with a relatively small axial Space can be realized. In particular, this can be a in the inner rotor or in the camshaft shaped annular channel for transfer the pressure medium between inner rotor and camshaft omitted become. Likewise, for the case that the camshaft and inner rotor are aligned with each other arranged holes are provided, a relatively large timing error between inner and outer rotor due to an unavoidable tolerance chain during pre-assembly of Rotationskolbenverstellers be avoided. Between the pressure medium paths occurs no or at least a slight leakage. Furthermore is the Rotationskolbenversteller easily on the camshaft mountable.

The Insert can, for example, plastic or a metallic Be made of material such as aluminum or steel. It can be on the inner rotor or centered on the camshaft. Is on the inner rotor Formed shoulder, so this can on the one hand for centering the inner rotor for Camshaft and on the other hand serve to receive the insert.

For a montage the arrangement can first the insert pre-mounted on Rotationskolbenversteller and the Rotary piston adjuster then mounted on the camshaft become. Alternatively, the insert can be pushed onto the camshaft and subsequently the pre-assembled rotary piston adjuster are mounted on the camshaft.

• – das Einsatzteil ist am Außendurchmesser der Nockenwelle platziert;
• – Druckmittel für die einen Druckkammern der gegeneinander wirkenden Druckkammerpaare fließt zum Beispiel in einer umlaufenden Nut entlang der Zentralschraube von der Nockenwelle in den Innenrotor;
• – Druckmittel für die anderen Druckkammern der gegeneinander wirkenden Druckkammerpaare fließt zum Beispiel von axialen Druckmittelbohrungen in der Nockenwelle in eine radiale Druckmittelnut im Innenrotor (alternativ: radiale Druckmittelnut in der Nockenwelle und axiale Druckmittelbohrungen im Innenrotor möglich);
• – das Einsatzteil ermöglicht in Verbindung mit der Nockenwelle und dem Innenrotor eine dritte radial umlaufende Druckmittelnut für eine Druckmittelübergabe zwischen der Nockenwelle und den Innenrotor;
• – mögliche Querschnittsformen des Einsatzteils: balkenförmig oder rechtwinklig;
• – Zentrierungsmöglichkeiten des Einsatzteils: Zentrierung auf Nockenwelle, Zentrierung am Innen- oder Außendurchmesser eines Zentrierrings am Innenrotor, Zentrierung im Rotorabsatz, Zentrierung im Dichtdeckelinnendurchmesser (zweite Seitenplatte);
• – Zentrierung des Einsatzteils im Innenrotor mittels eines Absatzes, auf welchem gleichzeitig das Einsatzteil aufgenommen wird;
• – nach Montage des Nockenwellenverstellers auf der Nockenwelle wird das Einsatzteil durch den Nockenwellenaußendurchmesser radial und durch einen Außendurchmesserabsatz (Anschlag) auf der Nockenwelle axial fixiert;
• – kein Druckmittelaustausch (Druckmittelleckage) zwischen den einzelnen Druckmittelleitungen möglich, da die Nockenwelle mittels einer Zentralschraubenverbindung axial gegen den Innenrotor gepresst wird;
• – mögliche Druckmittelleckage zwischen radial umlaufender Druckmittelnut unter dem Einsatzteil eingegrenzt durch Überdeckung des Einsatzteils von Rotorabsatz axial und Nockenwellenabsatz radial (Spielausgleich);
• – Ausführung des Einsatzteils als Kunststoff-(Gewichts- und Kostenvorteil), Aluminium- oder Stahlbauteil;
• – Montagereihenfolge am Motor: axiales Aufschieben des Einsatzteils auf Nockenwelle (keine Ausrichtung im Winkel erforderlich); Montage des Nockenwellenverstellers auf Nockenwelle mittels Zentralschraube (alternativ: Einsatzteil an Zentrierung am Innenrotor vormontiert);
• – Vorteil: Innenrotorbreite zwischen Zentralschraubenkopf und Nockenwelle kann auf eine minimal erforderliche Baubreite reduziert werden; Baubreite nur noch von vorhandener Bauteilbelastung abhängig;
• – Vorteil: kein Timing-Pin erforderlich, dadurch nur geringer Steuerzeitenfehler der Gaswechselventile;
• – neue radial umlaufende Druckmittelnut am Außendurchmesser der Nockenwelle auch für die Druckmittelpfade zu den Druckkammern als Druckmittelübergabestelle verwendbar;
• – Erfindung ist nicht beschränkt auf drei Druckmittelpfade zwischen eingestecktem Steuerventil im Zylinderkopf und Nockenwellenversteller auf Nockenwelle; Anzahl der Druckmittelpfade kann kleiner oder größer sein;
• – Erfindung ist nicht beschränkt auf ein hydraulisches Nockenwellenverstellsystem mit mechanischer Mittenverriegelung; mechanische Verriegelung kann auch Endanschlagsverriegelung in Spät- oder Frühstellung sein;
• – Erfindung ist nicht beschränkt auf Einsteckventil im Zylinderkopf; auch bei Zentralventillösungen anwendbar; Vorteil: Innenrotor kann bei mehreren vom Zentralventil aus in den Innenrotor mündenden Druckmittelkanälen in der Baubreite reduziert werden;
• – alternativ kann anstelle eines Absatzes am Innenrotor auch der Innendurchmesser des Dichtdeckels (zweite Seitenplatte) als Zentrierung und gleichzeitig als Überdeckung zur Reduzierung der Druckmittelleckage an die Umgebung genutzt werden;
• – bei Verwendung eines Einsatzteils mit einem balkenförmigen Querschnitt kann der Außendurchmesser der Nockenwelle im Bereich der radial umlaufenden Druckmittelnut im Vergleich zum Außendurchmesser der restlichen Nockenwelle gleich, kleiner oder größer sein;
• – bei Verwendung eines Einsatzteils mit einem balkenförmigen Querschnitt kann anstelle eines Einsatzteils auch der Dichtdeckel zum Abdichten verwendet werden.

Further possible features of the invention will become apparent from the following description:

• - The insert is placed on the outer diameter of the camshaft;
• - Pressure means for the one pressure chambers of the oppositely acting pressure chamber pairs flows, for example in a circumferential groove along the central screw of the camshaft in the inner rotor;
• - Pressure medium for the other pressure chambers of the oppositely acting pressure chamber pairs flows, for example, from axial pressure medium holes in the camshaft in a radial pressure center groove in the inner rotor (alternatively: radial pressure center groove in the camshaft and axial fluid holes in the inner rotor possible);
• - The insert allows in conjunction with the camshaft and the inner rotor, a third radially surrounding pressure center for a pressure medium transfer between the camshaft and the inner rotor;
• - Possible cross-sectional shapes of the insert: bar-shaped or rectangular;
• - Centering possibilities of the insert: centering on camshaft, centering on the inner or outer diameter of a centering ring on the inner rotor, centering in the rotor shoulder, centering in the inner sealing lid inner diameter (second side plate);
• - Centering of the insert part in the inner rotor by means of a paragraph, on which the insert is taken at the same time;
• - After installation of the camshaft adjuster on the camshaft, the insert is fixed axially by the camshaft outer diameter and axially by an outer diameter shoulder (stop) on the camshaft;
• - No pressure medium exchange (pressure medium leakage) between the individual pressure medium lines possible because the camshaft is pressed by means of a central screw connection axially against the inner rotor;
• - Possible pressure medium leakage between radially encircling pressure medium groove under the insert limited by overlapping the insert part of the rotor and axially axial camshaft sales (clearance compensation);
• - Implementation of the insert as plastic (weight and cost advantage), aluminum or steel component;
• - Assembly sequence on the engine: axial sliding of the insert on the camshaft (no angular alignment required); Mounting the camshaft adjuster on the camshaft by means of a central screw (alternatively: insert pre-assembled to centering on the inner rotor);
• - Advantage: Inner rotor width between central screw head and camshaft can be reduced to a minimum required width; Width only dependent on existing component load;
• - Advantage: no timing pin required, thus only small timing error of the gas exchange valves;
• - New radially circulating pressure center groove on the outer diameter of the camshaft also for the pressure medium paths to the pressure chambers as pressure medium transfer point used;
• The invention is not limited to three pressure medium paths between the inserted control valve in the cylinder head and camshaft adjuster on the camshaft; Number of pressure medium paths can be smaller or larger;
• - The invention is not limited to a hydraulic camshaft adjustment system with mechanical center lock; mechanical locking can also be end stop lock in late or early position;
• - Invention is not limited to plug valve in the cylinder head; also applicable to central valve solutions; Advantage: Inner rotor can be reduced in width of several widths from the central valve into the inner rotor.
• - Alternatively, instead of a shoulder on the inner rotor and the inner diameter of the sealing cover (second side plate) can be used as centering and at the same time as an overlap to reduce the pressure medium leakage to the environment;
• - When using an insert with a bar-shaped cross-section, the outer diameter of the camshaft in the region of the radially circumferential pressure center groove compared to the outer diameter of the remaining camshaft be equal to, smaller or larger;
• - When using an insert with a bar-shaped cross-section, instead of an insert and the sealing cover can be used for sealing.

1

arrangement

2

Rotary piston adjuster

3

outer rotor

4

inner rotor

5

camshaft

6

Sprocket

7

axis of rotation

8th

rotor hub

9

Camshafts face

10

clamping screw

11

outer ring

12

first side plate

13

second side plate

14

rotor opening

15

first plate opening

16

second plate opening

17

axial opening

18

wing

19

camshaft bearings

20

first Pressure fluid conduit

21

first radial line

22

second radial line

23

first annular channel

24

shank portion

25

Shank exterior

26

rotor paragraph

27

camshafts opening

28

Bearing inner surface

29

Cam outer circumferential surface

30

Rotor paragraph inner circumferential surface

31

Camshafts inner circumferential surface

32

third radial line

33

second Pressure fluid conduit

34

fourth radial line

35

fifth radial line

36

first axial duct

37

second annular channel

38

Rotor hub face

39

sixth radial line

40

third Pressure fluid conduit

41

seventh radial line

42

eighth radial line

43

second axial duct

44

ninth radial line

45

third annular channel

46

oblique line

47

first camshafts paragraph

48

first boundary surface

49

second boundary surface

50

third boundary surface

51

fourth boundary surface

52

insert

53

sleeve section

54

first radial board

55

Sleeve inner circumferential surface

56

first Board face

57

first Camshafts shoulder surface

58

plate recess

59

edge surface

60

first Sleeve face

61

first annular gap

62

Rotornabenausnehmung

63

recess surface

64

Sleeve outer peripheral surface

65

second annular gap

66

first sloping surface

67

second sloping surface

68

first axial rib

69

first Axialrippenfläche

70

third annular gap

71

Rotor hub projection

72

projection face

73

fourth annular gap

74

third sloping surface

75

fourth sloping surface

76

second axial rib

77

second Axialrippenfläche

78

fifth ring gap

79

axial annular groove

80

first annulus

81

second annulus

82

first Ringnutfläche

83

fifth bevel

84

sixth sloping surface

85

second Ringnutfläche

86

seventh sloping surface

87

eighth sloping surface

88

first ring seal

89

sleeve end

90

second ring seal

91

second Sleeve face

92

second radial board

93

second Board face

94

second Camshafts shoulder surface

95

sixth annular gap

96

second camshafts paragraph

97

third Camshafts shoulder surface

98

fourth Camshafts shoulder surface

99

seventh annular gap

100

third ring seal

101

inner ring

102

fourth ring seal

103

fifth ring seal

104

ninth sloping surface

105

tenth sloping surface

201

Rotary piston adjuster

202

outer rotor

203

inner rotor

204

camshaft

205

drive wheel

206

outer ring

207

partition wall

208

first side plate

209

second side plate

210

rotor hub

211

hydraulic chamber

212

screw

213

clamping screw

214

Rifle

215

Rotary oil joint

216

wing

217

camshaft bearings

218

first radial channel

219

second radial channel

220

internal annular channel

221

first outer ring channel

222

Oil separation sleeve

223

first radial bore

224

second outer ring channel

225

second radial bore

226

third radial bore

227

locking pin

228

first Blind hole

229

compression spring

230

second Blind hole

231

face

232

connecting channel

233

spiral spring

Claims (24)

Arrangement ( 1 ) with hydraulic camshaft adjuster ( 2 ) for an internal combustion engine, which comprises: - a drive part which can be brought into driving connection with a crankshaft ( 3 ), - one with a camshaft ( 5 ) rotatably connected output member ( 4 ), wherein driving and driven part rotatable about a common axis of rotation ( 7 ) and a rotational angular position of the Ab- to the drive part by means of at least one oppositely acting pressure chamber pair comprising hydraulic adjusting mechanism is adjustable, wherein the pressure chamber pair consists of a first pressure chamber and a second pressure chamber, - a hydraulically unlockable locking device, by which input and output part in a locking rotational position can be locked in a rotationally fixed manner, characterized by at least three pressure medium paths which can be acted upon separately with pressure medium ( 20 . 33 . 40 ), of which a first pressure medium path ( 20 ) with the at least one first pressure chamber, a second pressure medium path ( 33 ) with the at least one second pressure chamber, and a third pressure medium path ( 40 ) is fluidically connected to the hydraulic locking device, wherein a pressure medium path ( 40 ) a pressure medium channel surrounding the camshaft ( 45 ), which by means of a between the output part ( 4 ) and a camshaft outer peripheral surface ( 29 ) arranged insert part ( 52 ) is shaped. Arrangement ( 1 ) according to claim 1, characterized in that the insert part ( 52 ) one with the camshaft adjuster ( 2 ), in particular stripping section ( 4 ), connected axial sleeve section ( 53 ) which is connected to the inner rotor ( 4 ) facing, radial first sleeve end face ( 60 ) a radial first driven part abutment surface ( 38 ) of the stripping section ( 4 ) is present. Arrangement ( 1 ) according to claim 2, characterized in that the insert part ( 52 ) a radial distance to the drive part ( 3 ) having. Arrangement ( 1 ) according to claim 1, characterized in that the insert part ( 52 ) one with the camshaft adjuster ( 2 ), in particular stripping section ( 4 ), connected axial sleeve section ( 53 ) provided with an axial sleeve outer peripheral surface ( 64 ) an axial second driven part abutment surface ( 63 ) of the stripping section ( 4 ) is present. Arrangement ( 1 ) according to claim 4, characterized in that the second driven part abutment surface ( 63 ) and the sleeve outer peripheral surface ( 64 ) at least in the adjacent sections ( 66 . 67 ) are each in a cone shape in fit. Arrangement ( 1 ) according to one of claims 4 to 5, characterized in that the insert part ( 52 ) an axial distance to the output part ( 4 ) having. Arrangement ( 1 ) according to one of claims 4 to 6, characterized in that the insert part ( 52 ) a radial distance to the drive part ( 3 ) having. Arrangement ( 1 ) according to claim 1, characterized in that the insert part ( 52 ) one with the camshaft adjuster ( 2 ), in particular stripping section ( 4 ), connected axial sleeve section ( 53 ), which of an axial third driven part abutment surface ( 72 ; 77 ) of the stripping section ( 4 ) with an axial sleeve inner peripheral surface ( 55 ) is present. Arrangement ( 1 ) according to claim 8, characterized in that the third driven part abutment surface ( 72 ) and the axial sleeve inner peripheral surface ( 55 ) at least in the adjacent sections ( 74 . 75 ) are each in a cone shape in fit. Arrangement ( 1 ) according to one of claims 8 to 9, characterized in that the insert part ( 52 ) an axial distance to the output part ( 4 ) having. Arrangement ( 1 ) according to one of claims 8 to 10, characterized in that the insert part ( 52 ) a radial distance to the drive part ( 3 ) having. Arrangement ( 1 ) according to claim 1, characterized in that the insert part ( 52 ) one with the camshaft adjuster ( 2 ), in particular stripping section ( 4 ), connected axial sleeve section ( 53 ), which is provided with an edge portion ( 79 ) in an axial groove ( 79 ) of the stripping section ( 4 ) is recorded. Arrangement ( 1 ) according to claim 12, characterized in that an axial groove wall ( 85 ) and one of the axial groove wall opposite arranged sleeve inner peripheral surface ( 55 ) at least in the adjacent sections ( 86 . 87 ) are each in a cone shape in fit. Arrangement ( 1 ) according to one of claims 12 to 13, characterized in that an axial groove wall ( 82 ) and one of the axial groove wall opposite arranged sleeve outer peripheral surface ( 64 ) at least in the adjacent sections ( 83 . 84 ) are each in a cone shape in fit. Arrangement ( 1 ) according to one of claims 2 to 14, characterized in that between the axial sleeve portion ( 53 ) and the stripping section ( 4 ) a sealant ( 88 ; 89 ; 90 ) is arranged. Arrangement ( 1 ) according to claim 1, characterized in that the insert part ( 52 ) one with the camshaft adjuster ( 2 ), in particular stripping section ( 4 ), connected axial sleeve section ( 53 ) and a radially outwardly directed, first radial board ( 54 ), wherein the first radial board to a the output member facing radial first sleeve end face ( 60 ) is formed, and wherein the first radial board in a radial receptacle ( 58 ) of the drive part ( 3 ) is recorded. Arrangement ( 1 ) according to claim 16, characterized in that the first radial board ( 54 ) with radial play in the radial receptacle ( 58 ) of the drive part ( 3 ) is recorded. Arrangement ( 1 ) according to one of claims 2 to 17, characterized in that an inwardly directed second radial board ( 92 ) at one of the stripping section ( 4 ) facing away, radial second sleeve end face ( 91 ) to the axial sleeve portion ( 53 ), wherein the second radial board ( 92 ) with a radial Bordanlagefläche ( 93 ) a radial first camshaft bearing surface ( 94 ) abutting one of the camshaft outer peripheral surface ( 29 ) of the camshaft molded camshaft paragraph ( 47 ) is formed. Arrangement ( 1 ) according to claim 18, characterized in that an edge of the second radial board ( 92 ) a radial distance from the camshaft outer peripheral surface ( 29 ) of the camshaft. Arrangement ( 1 ) according to one of claims 2 to 17, characterized in that a sleeve inner peripheral surface ( 55 ) of the axial sleeve section ( 53 ) an axial second camshaft bearing surface ( 57 ) abutting one of the camshaft outer peripheral surface ( 29 ) of the camshaft molded camshaft paragraph ( 47 ) is formed. Arrangement ( 1 ) according to claim 20, characterized in that between the sleeve inner peripheral surface ( 55 ) of the sleeve section ( 53 ) and the second camshaft bearing surface ( 57 ) a sealant ( 100 ) is arranged. Arrangement ( 1 ) according to claim 20, characterized in that the sleeve inner peripheral surface ( 55 ) of the sleeve section ( 53 ) and the second camshaft bearing surface ( 57 ) at least in the adjacent sections ( 104 . 105 ) are each in a cone shape in fit. Arrangement ( 1 ) according to any one of claims 20-21, characterized in that in opposition to a radial camshaft landing surface ( 94 ) of the camshaft paragraph ( 47 ) an inwardly directed inner ring ( 101 ) to the sleeve section ( 53 ) is formed. Arrangement ( 1 ) according to claim 23, characterized in that between the inner ring ( 101 ) and the radial camshaft landing surface ( 94 ) of the camshaft paragraph ( 47 ) a sealant ( 103 ) is arranged.