EP3158173B1 - Oscillating motor-type phaser for a camshaft - Google Patents

Description

The invention relates to a Schwenkmotorversteller for a camshaft according to the preamble of patent claim 1.

Swivel engine timing adjusters for internal combustion engine camshafts are well known. In a typical swing motor phaser, a controllably adjustable latch bolt is slidably disposed in a bore in a rotor vane of the swing motor phaser to permit rotation of the rotor to the stator under certain operating conditions of the phaser and motor. One known bolt locking mechanism includes a compression spring to tension one end of the bolt in a conventionally hardened seat disposed in the pulley or sprocket of the swing motor adjuster so that the rotor locks with respect to the stator fixedly connected to the pulley or sprocket becomes.

The rotor may for example consist of aluminum, and a steel bushing is pressed and inserted at a certain axial point in the bore, so that the bolt can be guided.

From the publication DE 10 2010 060 263 A1 goes a Schwenkmotorversteller for a camshaft, which has a largely hollow-cylindrical pin which receives a compression spring in the hollow cylindrical portion. In the course of assembly of the Schwenkmotorverstellers there is a so-called active setting, wherein the stator or the stator housing against a locking disc, in which the bolt is engageable, is rotated and thus a corresponding locking clearance is set. The stator is doing so with the help of in Generally four to five screws positioned to the locking disc. For positioning of the rotor during assembly of the stator is provided as a stop of the rotor.

In principle, a specific locking clearance between a web of the stator and a wing of the rotor must be maintained in a locking position. This locking clearance is necessary so that when locking or unlocking a jamming of the locking bolt and the locking disc excluded or the noise behavior can be minimized.

The problem, however, is that this locking game can be faulty due to a forming during the assembly of Schwenkmotorverstellers tolerance chain, so that thereby jamming of the locking bolt and the locking disc during operation of the Schwenkmotorverstellers can quite occur.

The object of the present invention is to provide a Schwenkmotorversteller for a camshaft having improved reliability.

The object is achieved by a Schwenkmotorversteller for a camshaft with the features of claim 1. Advantageous embodiments with expedient and non-trivial developments of the invention are specified in the respective subclaims.

The Schwenkmotorversteller for a camshaft according to the invention comprises a rotor and a stator, wherein the rotor is rotatable against the stator via a rotation axis of the Schwenkmotorverstellers. In each case between two webs of the stator, a wing of the rotor is positionable, wherein with the aid of the wing formed between the two webs intermediate space is divided into a first pressure chamber and a second pressure chamber. To lock the stator and the rotor is coaxial with the stator and the rotor arranged locking device is provided which comprises a spring-loaded locking bolt and a locking disc with a locking hole for at least partially receiving the connecting bolt for locking the stator to the rotor in an end position. The locking bolt is received in one of the wings. During the locking, a locking clearance is formed between the locking bolt bearing wings and the adjacent web, so that the rotor relative to the stator slightly, in the order of the locking clearance is movable. The stator is provided fixed by means of connecting elements on the locking disc.
To set the locking clearance and fixing the locked end position, the locking disc on a stop element.

The locking clearance determines a functionally reliable operation of the Schwenkmotorverstellers so that quickly and effectively the camshaft can be adjusted relative to the crankshaft. This adjustment serves to achieve the best possible operating points of the internal combustion engine. If the best possible operating points are set, the internal combustion engine can achieve high outputs with low fuel consumption, so that predefined exhaust gas standards can be achieved.

Decisive for maintaining the exact game clearance is the inclusion of tolerances of certain components of the Schwenkmotorverstellers, in other words of locking game relevant components during assembly. That is, in addition to the desired locking game, the corresponding tolerances of the locking game relevant components are added up and form a tolerance chain. In the tolerance chain flow all production-related diameter, length and angle tolerances and geometric tolerances, such as position tolerances of the locking game relevant components. This means that the fewer component tolerances enter into this tolerance chain, the more accurate or precise is the locking clearance can be adjusted.

The locking disc of the Schwenkmotorverstellers invention has a stop pin. By using the stop pin, an active setting is no longer necessary, and the stator is eliminated from the tolerance chain, since all necessary tolerances are only in the locking disc.

During assembly of the Schwenkmotorverstellers the rotor is positioned coaxially on the locking disc, wherein a wing of the rotor is guided against the stop pin to the stop of the wing on the stop pin. The rotor and the locking disc are held in this position by means of the locking device.

Preferably, the locking bolt is positioned on the wing of the rotor, wherein the locking bolt is formed completely receivable in a receiving opening of the wing, so that even with an unlocking due to the complete inclusion of the locking bolt in the wing an unimpeded relative movement of the rotor relative to the stator is possible.

In a further embodiment of the invention, the locking disc has a locking bore for at least partially receiving the locking bolt. Thus, for locking and thus for relative positioning of the rotor and the locking disc of the locking bolt to be inserted into the locking hole, so that the rotor is not movably connected to the locking disc.

Finally, the stator is positioned coaxially with the rotor and the locking disc locked to the rotor and, by means of a connecting element, generally a screw, fixed to the locking disc, in other words, non-movably connected to the locking disc during operation.

Since the Schwenkmotorversteller invention has the stop pin for positioning of the rotor in an end position, eliminates the stator as a locking game relevant component in the tolerance chain, so that in particular Tolerances with respect to diameter and angle and the positioning of the stator omitted. Thus, a much more precise locking clearance during assembly is set, whereby a much improved performance and thus improved reliability is to bring about.

In a further embodiment, the stop element is designed in the form of a pin. This serves for a simple production of the stop element, which is received in a form-fitting and / or cohesive manner on the locking disc.

Since the stop pin serves as a stop of the rotor, the stop element is preferably made of a first material which is harder and / or impact resistant than a second material of which the stator and / or which is harder and / or impact resistant than a third material from which the locking disc is made. This leads to a reduction of wear of the stop pin and thus in addition to an improved operational safety of Schwenkmotorverstellers invention.

In a further embodiment of the Schwenkmotorverstellers invention, the locking disc for setting two different locking games on a further stop pin. The original stop pin, which is positioned near the locking hole, limited in a first direction of rotation, for example. Counterclockwise, a twist angle of the rotor. In other words, this original stop pin represents a limit in a first end position. The further stop pin is positioned farther from the locking hole. However, with respect to the rotation in a second rotation opposite to the first rotation, for example in a clockwise direction, it represents a second end position. Furthermore, the two stop pins are positioned in such a way that with respect to a wing, in particular the wing, which has the locking bolt, are a Verdrehbegrenzung. The advantage of this embodiment is that ever a backlash related to the corresponding direction of rotation can be adjusted can, whereby a further improved reliability is realized, since depending on the direction of rotation slightly different torques act on the camshaft and thus different pressures in the hub bores.

To reduce components and thus to reduce weight, the connecting element corresponds to a screw by means of which a drive wheel of the camshaft is rotationally connected to the stator.

The assembly of the Schwenkmotorverstellers is simplified by the arrangement of the stop member in the region of the locking hole, in which the locking pin can be accommodated. If the stop element, for example, arranged in another wing of the rotor, a deposition of the rotor could occur from the stop on the stop pin out at a locking of the rotor with the locking disc upon insertion of the locking bolt in the locking hole. This deposition can still be so low but considering a summation of the corresponding tolerances and with the inclusion of an exemplary locking clearance of 0.4 ° even a very small Depositionierung or rotation of the rotor relative to the locking disc can lead to a change in the locking game. Therefore, the stopper pin is preferably to be positioned in the region of the locking hole.

According to another advantageous embodiment of the invention, a radial distance of the stop element to a rotational axis of the rotor is greater than a radial distance of the locking bolt to the axis of rotation. Hereby it can be ensured that a stop of the wing to the stop element no deformation in the region of the lock result Has.

Preferably, the stop element can be provided for adjusting a displacement angle of the rotor relative to the stator, whereby similar rotors or stators can be used for different applications with different adjustment angles.

Fig. 1

in einer Prinzipskizze ein Schwenkmotorversteller gemäß des Standes der Technik,

Fig. 2

in einer perspektivischen Ansicht eine Verriegelungsscheibe eines erfindungsgemäßen Schwenkmotorverstellers in einem ersten Ausführungsbeispiel,

Fig. 3

in einer perspektivischen Ansicht die Verriegelungsscheibe des Schwenkmotorverstellers in einem zweiten Ausführungsbeispiel,

Fig. 4

in einer Vorderansicht die Verriegelungsscheibe mit dem Rotor des Schwenkmotorverstellers gem. Fig. 2,

Fig. 5

in einer Vorderansicht den Schwenkmotorverstellers gem. Fig. 3, und

Fig. 6

in einer Vorderansicht einen Ausschnitt den erfindungsgemäßen Schwenkmotorversteller in einem dritten Ausführungsbeispiel.

Further advantages, features and details of the invention will become apparent from the following description of preferred embodiments and from the drawing. The features and feature combinations mentioned above in the description as well as the features and feature combinations mentioned below in the description of the figures and / or in the figures alone can be used not only in the respectively specified combination but also in other combinations or in isolation, without the scope of To leave invention. Identical or functionally identical elements are assigned identical reference numerals. For reasons of clarity, it is possible that the elements are not provided with reference numbers in all figures, but without losing their assignment. Show it:

Fig. 1

in a schematic diagram of a Schwenkmotorversteller according to the prior art,

Fig. 2

in a perspective view of a locking disc of a Schwenkmotorverstellers invention in a first embodiment,

Fig. 3

in a perspective view of the locking disc of the Schwenkmotorverstellers in a second embodiment,

Fig. 4

in a front view of the locking disc with the rotor of the Schwenkmotorverstellers gem. Fig. 2 .

Fig. 5

in a front view of the Schwenkmotorverstellers gem. Fig. 3 , and

Fig. 6

in a front view a section of the Schwenkmotorversteller invention in a third embodiment.

A Schwenkmotorversteller 1 of the prior art, s. Fig. 1 , allows during operation of an internal combustion engine, not shown, to bring about a change of opening and closing times of gas exchange valves of the internal combustion engine.
For this purpose, with the aid of the Schwenkmotorverstellers 1, a relative angular position of a camshaft, not shown, of the internal combustion engine with respect to a crankshaft, not shown, of the internal combustion engine continuously changed, wherein the camshaft is rotated relative to the crankshaft. By turning the camshaft, the opening and closing times of the gas exchange valves are shifted so that the internal combustion engine brings its optimum performance at the respective speed.

The Schwenkmotorversteller 1 has a cylindrical stator 2 which is rotatably connected to a non-illustrated drive wheel of the camshaft. The drive wheel can be designed as a sprocket, via which a chain, not shown, is guided as a drive element. Likewise, the drive wheel may also be a toothed belt wheel over which a drive belt is guided as a drive element. About this drive element and the drive wheel of the stator 2 is drivingly connected to the crankshaft.

The stator 2 has a cylindrical stator base 3, on which on its inside 4 radially inwardly extending webs 5 are formed at regular intervals, such that between each two adjacent webs 5, a gap 6 is formed. In this space 6, a pressure medium, generally a hydraulic fluid, introduced controlled by means of a hydraulic valve, not shown.

In the intermediate space 6 projecting a wing 7 is positioned, which is arranged on a rotor hub 8 of a rotor 9. The number of spaces 6 corresponding to the rotor hub 8 a number of wings 7. The rotor 9 has an axis of rotation 10.

With the help of the wings 7 thus the interstices 6 are each divided into a first pressure chamber 11 and a second pressure chamber 12. To reduce a pressure loss in the first pressure chamber 11 and the second pressure chamber 12, the webs 5 are formed with their first end faces 13 to an outer circumferential surface 14 of the rotor hub 8 sealingly fitting. Likewise, the wings are 7 with their second end faces 15 sealingly against one of the outer circumferential surface 14 oppositely positioned inner wall 16 of the stator main body 3 at.

The rotor 9 is rotatably connected to the camshaft of the internal combustion engine. In order to change the angular position between the camshaft and the crankshaft, the rotor 9 is rotated relative to the stator 2 about the axis of rotation 10, wherein the stator 2 is arranged coaxially with the rotor 9. For this purpose, depending on the selected direction of rotation, the pressure medium in the first pressure chamber 11 or in the second pressure chamber 12 is pressurized, while the second pressure chamber 12 and the first pressure chamber 11 is relieved. The discharge takes place with the help of a tank access, which is open for relief.

In order that the rotor 9 is rotated counterclockwise relative to the stator 2, radial first hub bores 17 are pressurized by means of the hydraulic valve, which are distributed regularly over the circumference of the rotor hub 8. For rotation of the rotor 9 in the clockwise direction relative to the stator 2 radial second hub bores 18 are pressurized by means of the hydraulic valve, which are also distributed over the circumference of the rotor hub 8, said second hub bores 18 axially spaced from the first hub bores 17 are positioned.

For locking the stator 2 and the rotor 9, a locking device 36 is provided. The locking device 36 comprises, in addition to a locking disc 19 arranged coaxially with respect to the rotor 9 or stator 2, a locking bolt 23. The locking disc 19 is formed flush against a first rotor disc surface 20 of the rotor 9. At a second Rotor disk surface 21 of the rotor 9, which is remote from the first rotor disk surface 20, a cover not shown in detail for covering the rotor 9 and the stator 2 is positioned. The lid is designed as a plastic lid, but can also be made of a metallic material.

If the locking disc 19 gem. Fig. 2 associated with the Schwenkmotorversteller 1, the lid is pressed by means of a compression on an outer edge 22 of the locking disc 19. The locking disc 19 gem. Fig. 3 has a tooth rim-like outer edge 22, wherein the lid is inserted axially, thus in the direction of the axis of rotation 10, positionally accurate.

The Fig. 4 shows the Schwenkmotorversteller 1 according to the invention in a first embodiment with the rotor 9 and the locking disc 19 according to Fig. 2 , In Fig. 5 is the Schwenkmotorversteller 1 according to the invention in a second embodiment with the rotor 9, the stator 2 and the locking disc 19 gem. Fig. 3 shown.

Independently of the outer edge 22 of the locking disk 19, a wing 7 'of the wings 7 carries the locking bolt 23. This locking bolt 23 is accommodated axially displaceable along the axis of rotation 10 in a receiving opening 24 of the wing 7'. The locking pin 23 is formed like a hollow cylinder and has a recorded inside the hollow cylinder not shown coil spring. The helical spring is supported on a support element 28, which closes the receiving opening 24 on the second rotor disk surface 21, so that the axial displacement of the locking bolt 23 in the direction of the second rotor disk surface 21 is limited.

A second hub bore 18 'of the second hub bores 18 leads to a formed in the locking disc 19 loading channel 25. This loading channel 25 is hydraulically connected to a in the Locking disc 19 designed locking bore 26 into which the locking pin 23 can be inserted for locking. Furthermore, the locking disc 19 has a discharge channel 27, which is configured hydraulically separated from the loading channel 25 and the locking bore 26 in the locking disc 19.

The loading channel 25, the locking bore 26 and the discharge channel 27 are not completely penetrating the locking disc. This means that the loading channel 25, the locking hole 26 and the discharge channel 27, the Verrieglungsscheibe 19 are formed in its axial extent is not completely breakthrough, wherein the loading channel 25, the locking hole 26 and the discharge channel 27 facing the rotor 9 is open and in its axial Extension in the direction of the rotation axis 10 turned away from the rotor 9 are designed to be closed. The loading channel 25 and the discharge channel 27 are groove-like introduced into the locking disc 19, wherein the locking bore 26 is boring introduced into the locking disc 19.

The locking pin 23 has a pressure application surface, not shown, which is designed in the form of a bolt bottom of the locking bolt 23. This bolt bottom is arranged facing the locking bore 26. A not further illustrated further annular pressure application surface is formed on a jacket of the Verrieglungsbolzens 23. In a simple embodiment, the annular pressure-engaging surface is in the form of a step of the shell, in other words, the shell has a first diameter over a first axial extent and a second diameter smaller than the first diameter over a second axial extent , Due to the different diameters, a transition, which is embodied between a first lateral surface of the jacket formed on the basis of the first diameter and a second lateral surface of the jacket formed on the basis of the second diameter, is configured in the form of a step. The Receiving opening 24 is also designed corresponding to the jacket stepped.

Due to the hydraulic connection of the loading channel 25 with the locking bore 26, the locking bore 26 is also acted upon by the hydraulic fluid when the second hub bore 18 'is acted upon, and the locking bolt 23 is pressed out of the locking bore 26 so that an adjustment of the rotor 9 is made possible.

With the help of a further loading channel not shown, the further pressure application surface is pressurizable, wherein a direction of action of the pressurization corresponds to a direction of action of the pressurization of the bolt bottom. That is, both pressure application surfaces are pressurizable against a spring force of the coil spring. So that pressure equalization can be established when pressure is applied, the support element has at least one compensation opening, so that pressure equalization can take place in a space formed between the locking bolt 23 and the support element 28. Since this rests flat with drive wheel for pressure loss avoidance of the second rotor disc surface 21 and thus also flush against the axially flush with the second rotor disc surface 21 web surfaces of the webs 5, the pressure compensation takes place via a recess not shown in the radial inner region of the drive wheel. The drive wheel is fixedly connected to the webs 5 by means of screws 29.

The discharge channel 27 designed in the locking disk 19 is hydraulically connected to a supply groove 35 formed in the wing 7 '. The discharge channel 27 is arcuate and leads from the web 5 associated with the locking until shortly before a second pressure attack side surface of the wing 7'. Thus, the wing covers 7 'the discharge channel 27 from the direction of the first pressure chamber 11, whereas the discharge channel 27 from the side of second pressure chamber 12 is pressurizable. Without pressurization of the locking pin 23 is mounted in the locking bore 26.

The discharge channel 27 is formed over a relatively large angle section. This ensures that the locking pin 23 is then pressurized via the discharge channel 27 from the first end position associated pressure chamber when the rotor 9 is in a central position between the first end position and a second end position.

The locking bore 26 has a bevel 30 on its end facing the first rotor disk surface 20, over its circumference. The chamfer 30 is such that a large diameter of the chamfer 30 is formed at the end of the lock hole 26 and the chamfer 30 tapers in the axial direction from the end of the lock hole 26. A constant diameter corresponding to the smallest diameter of the chamfer 30 is configured over a relatively short axial extent of the locking bore 26, so that the locking bolt 23 is received in the locking bore 26 secured over a sufficiently long length of the locking bore 26.

With the help of the thus designed locking hole 26 ensures that the unlocking is done very quickly, since the locking pin 23 to overcome the short axial extent of the locking hole 26 only has to perform a short stroke. For complete removal of the locking bolt 19 from the locking hole 26 results in a supporting force component in the circumferential direction of the Verrieglungsbolzens 19 due to the chamfer 30th

For pinch-free unlocking and locking a certain locking clearance 31 between the stator 2 and the rotor 9 is to be kept clear. That is, even in the locked state, a rotatability of the rotor 9 relative to the stator 2 in the order of this locking clearance 31 is possible. For exact compliance with the locking game 31, which depends on the Requirements on the Schwenkmotorversteller 1 and the size of the Schwenkmotorverstellers 1 can vary, a stop pin 32 is formed on the locking disc 19. Depending on a first material from which the stator 2 is made, the stopper pin 32 is made of a second material which is harder and / or impact resistant than the first material. In one embodiment, not shown, the stopper pin 32 is made of the second material, this second material is harder and / or impact resistant than a third material from which the locking disc 19 is made.

The locking clearance 31 is, depending on the requirement of the Schwenkmotorversteller 1, i. For example, how great is the relative rotatability of the camshaft with respect to the crankshaft to be set, and the size of the swivel motor adjuster 1 different. With the help of the stop pin 32 of this locking game is set exactly during the assembly of the Schwenkmotorverstellers 1. The stop pin 32 represents an end stop of the rotor 9 and the rotor blade 7 '.

The stop pin 32 is fixed in the region of the receiving opening 24 on the locking disc 19. The exact position of the stop pin 32 is dependent on a wing shape of the wing 7 ', since the rotor 9 is rotated as far as on the locking disc 19 during assembly until the wing 7' abuts against the stopper pin 32 and abuts. Then, the locking pin 23 is inserted into the locking hole 26, so that the rotor 9 relative to the locking disc 19 has a fixed end position. The stator 2 is finally pushed onto the rotor 9 and rotated as far as the rotor 9 until a desired position of the stator 2 in the end position of the rotor 9 is established. In general, the position of the stator 2 to be set to the end position of the rotor 9 is achieved by striking the web 5 on the wing 7 '. To fix the stator 2 relative to the rotor 9, the stator 2 is fixed to the locking disc 19 by means of connecting elements 33, in general screws. For this purpose, the locking disc 19 a corresponding number of openings 34, in which the connecting elements 33 are to be positioned. For simplified assembly, the connecting elements 33 correspond to the screws 29, with which the drive wheel with stator 2 or at the webs 5 is rotatably connected.

For secure recording, the locking disc 19 has a receiving element in the form of a hole, in which the stop element 32 is inserted and thus positively received on the locking disc 19. In an embodiment not shown in detail, the stop element 32 is additionally secured by a weld on the locking disc 19. Likewise, the stop element 32 could also be received exclusively by means of a material connection to the locking disc. If the locking disc 19 is made of a plastic, it is also possible to produce the stop element 32 in one manufacturing step in one piece with the locking disc 19.

In the embodiment of the invention Schwenkmotorverstellers 1, which the stop plate 19 according to Fig. 2 has two stop pins 32, the stopper pin 32 and another stopper pin 32, formed on the locking disc 19. This means that the stop pin 32 positioned close to the locking hole 26 limits the end position when the rotor 9 rotates counterclockwise, whereas the stop pin 32 positioned away from the locking hole 26 limits clockwise rotation of the rotor 9. This makes it possible to set two different locking games 31. That is, that set for the rotation of the rotor 9 counterclockwise locking clearance 31 has a different value than the locking clearance 31, which is observed in the rotation of the rotor 9 in the clockwise direction.

Thus, the Schwenkmotorversteller 1 is not jammed during locking or unlocking a correspondingly accurate locking clearance 31. This Locking clearance 31 is dependent on manufacturing tolerances related positioning relevant components of the Schwenkmotorverstellers 1. That is, enter into the tolerance chain in any case, all diameter, length and angle tolerances and geometric tolerances, such as position tolerances of positioning relevant or related to the locking game 31 components , Since, as described above, the stator 2 from the positioning of the rotor 9 relative to the Verrieglungsscheibe 19 and thus to adjust the locking clearance 31 abdesbar, eliminates all relevant stator related tolerances.

An embodiment not shown provides, in contrast to the embodiments described above, that a radial distance of the stop element 32 to the axis of rotation 10 of the rotor 9 is greater than a radial distance of the locking pin 23 to the axis of rotation 10. Thus, the stop member 32 strikes outside of the range of the locking bolt 23 and the receiving opening 24, so that it can be ensured that the stop of the stop element 32 has no deformation of the wing 7 'in the region of the lock result.

Preferably, the stop element may be provided in addition to the adjustment of an adjustment angle of the rotor 9 with respect to the stator 2, whereby similar rotors or stators can be used for different applications with different adjustment angles.

LIST OF REFERENCE NUMBERS

1

Schwenkmotorversteller

2

stator

3

stator base

4

inside

5

web

6

gap

7, 7 '

wing

8th

rotor hub

9

rotor

10

axis of rotation

11

first pressure chamber

12

second pressure chamber

13

first faces

14

Outer casing surface

15

second end faces

16

inner wall

17

first hub bores

18, 18 '

second hub bores

19

locking disc

20

first rotor disk surface

21

second rotor disk surface

22

outer edge

23

locking bolt

24

receiving opening

25

load channel

26

locking hole

27

relief channel

28

supporting

29

screw

30

chamfer

31

locking play

32

stop pin

33

connecting element

34

opening

35

feeding groove

36

locking device

Claims (13)

1. Pivoting motor adjuster for a camshaft, having a rotor (9) and a stator (2), it being possible for the rotor (9) to be rotated with respect to the stator (2), it being possible for a blade (7') of the rotor (9) to be positioned in each case between two webs (5) of the stator (2), and an intermediate space (6) which is configured between the two webs (5) being divided with the aid of the blade (7') into a first pressure chamber (11) and into a second pressure chamber (12), a locking apparatus (36) comprising a spring force-loaded locking bolt (23) and a locking disc (19) which is arranged coaxially with respect to the stator (2) and the rotor (9) with a locking bore (26) for at least partially receiving the locking bolt (23) in order to lock the stator (2) to the rotor (9) in an end position being configured for locking the stator (2) and the rotor (9), and the locking bolt (23) being received in one of the blades (7'), and a locking play (31) for the movability of the rotor (9) with respect to the stator (2) being configured during the locking action between the blade (7') which carries the locking bolt (23) and the adjacent web (5), the stator (2) being provided in a fixed manner with the aid of connecting elements (33) on the locking disc (19), and the locking disc (19) having a stop element (32) for setting the locking play (31) and for fixing the locked end position.
2. Pivoting motor adjuster according to Claim 1, characterized in that the locking bolt (23) is configured such that it can be received completely in a receiving opening (24) of the blade (7').
3. Pivoting motor adjuster according to either of the preceding claims, characterized in that the locking disc (19) is positioned coaxially with respect to the stator (2) and the rotor (9) so as to bear in an axially planar manner against the rotor (2) and against the stator (2).
4. Pivoting motor adjuster according to one of the preceding claims, characterized in that the stop element (32) is configured in the form of a pin.
5. Pivoting motor adjuster according to one of the preceding claims, characterized in that the stop element (32) is produced from a first material which is harder and/or more shock-resistant than a second material, from which the stator (2) is produced, and/or is harder and/or more shock-resistant than a third material, from which the locking disc (19) is produced.
6. Pivoting motor adjuster according to one of the preceding claims, characterized in that the stop element (32) is received in a positively locking manner on the locking disc (19).
7. Pivoting motor adjuster according to one of the preceding claims, characterized in that the stop element (32) is fastened to the locking disc (19) with the aid of an integrally joined connection.
8. Pivoting motor adjuster according to one of the preceding claims, characterized in that the locking disc (19) has a further stop pin (32) for setting two different locking plays (31).
9. Pivoting motor adjuster according to one of the preceding claims, characterized in that the connecting elements (33) for connecting the stator (2) to the locking disc (19) are provided as screws (29), by means of which a drive gear of the camshaft is connected fixedly to the stator (2) so as to rotate with it.
10. Pivoting motor adjuster according to one of the preceding claims, characterized in that the stop element (32) is arranged in the region of the locking bore (26).
11. Pivoting motor adjuster according to one of the preceding Claims 1 to 9, characterized in that a radial spacing of the stop element (32) from a rotational axis (10) of the rotor (9) is greater than a radial spacing of the locking bolt (23) from the rotational axis (10).
12. Pivoting motor adjuster according to one of the preceding claims, characterized in that the stop element (32) is provided for setting an adjusting angle of the rotor (9) with regard to the stator (2).
13. Pivoting motor adjuster according to one of the preceding claims, characterized in that the locking play (31) can be set by means of the stop element (32) in a manner which is adapted to the relative rotatability to be set of the camshaft in relation to a crankshaft.

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