DE102008020892A1 - Adjusting device for adjusting variable-lift valve drive of internal combustion engine, has controlling mechanism controllably transferring stop valve in retracting direction of actuating pin to release actuating pin from holding position - Google Patents

Abstract

The device (1) has a retaining element (23) i.e. ball, movably arranged in a cross-hole that intersects a longitudinal hole (20) and clamped in a holding position of an actuating pin (9) between a set of supporting surfaces (22) due to self-locking. The supporting surfaces are provided at constant distance with each other in a retracting direction of the actuating pin. A controlling mechanism (26) controllably transfers a stop valve (17) in retracting direction of the actuating pin to release the actuating pin from the holding position.

Description

Field of the invention

The The invention relates to an adjusting device with a housing and a housing mounted in the housing, relative to the housing from a retracted stop position in a working position extendable and from a spring means in the extension direction kraftbeaufschlagten actuator pin for adjusting a cooperating with the adjusting device Machine part. This has one with a first end of the actuator pin in its working position cooperating sliding groove, the the actuator pin shifted back into its holding position. The adjusting device has a controllable holding and releasing device for holding the actuator pin in the holding position and for releasing of the actuator pin from the stop position.

Background of the invention

Such a control device is considered from the considered generic WO 03/021612 A1 out. Their holding and releasing device for the Aktuatorstift based on the interaction of an electromagnet with a permanent magnet attached to the actuator pin whose magnetic attraction holds the Aktuatorstift against the force of the spring means in the holding position on the de-energized electromagnet. To release the actuator pin from the holding position, only a pulse-shaped current application of the electromagnet to overcome the magnetic attraction of the permanent magnet is required, the Aktuatorstift not only by the force of the spring means but also by the force of a magnetic Ab shock effect between the permanent magnet and the energized electromagnet in Direction of the working position is accelerated.

Such, with low power consumption quickly and time exactly switching actuator is particularly suitable for adjusting a variable-stroke valve train, as he, for example, from DE 10 2004 021 376 A1 evident. The stroke variability of the valve drive proposed there is based on a cam piece designed as a machine part with adjacently arranged cams whose different opening curves are selectively transmitted by means of a conventionally rigid cam follower on a gas exchange valve. For operating point-dependent adjustment of these opening courses, the cam piece rotatably, but longitudinally displaceable on a support shaft and has two spiral and oppositely extending sliding grooves, in which the end portions of the actuator pins of two adjusting devices of the type mentioned are alternately coupled. While the axial course of the sliding groove engaged with the associated actuator pin causes the cam piece to move from one cam position to the other camshaft in self-control and camshaft angle, the radial course of each slide groove is designed to increase towards the end of the shifting operation shallower and actively shifts the currently engaged actuator pin from its working position back to the holding position.

Even though also this active reset function of the sliding grooves an essential requirement for the low power consumption the proposed in the first cited document actuator is, can the operating principle of their holding and releasing device nevertheless be associated with various disadvantages. To these counts first and foremost the size of producing one sufficient attractive force required effective area between the electromagnet and the permanent magnet. The interpretation However, the attraction / effective surface is not only below the point of view even under dynamic influences secure holding function of the actuator pin in the stop position respectively. Rather, the size of the attraction / effective surface Also to be dimensioned so that in the immediate following to the Displacement of the cam piece at both lowest Speeds of the internal combustion engine as well as in the limit case in their Stand still not inertial forces, but only from the magnetic attraction generated residual stroke of the Aktuatorstifts between the then radially no longer rising Move groove and the stop surface on the electromagnet can be guaranteed. This requirement, in the case their non-fulfillment to a sliding contact of the actuator pin on the cam piece with undesirable, subsequent Fall back of the actuator pin in the sliding groove would, in view of the exponentially decreasing, Magnetic remote action of the permanent magnet due to component tolerances difficult, which leads to a considerable residual stroke of the actuator pin in the Millimeter range. Due to the size resulting from these design considerations the effective area between the electromagnet and the permanent magnet and thus the considerable space requirement of the adjusting device consists in the case of the illustrated variable-stroke valve drive always the increased risk that exists in an already existing one Architecture of the internal combustion engine to be integrated actuator collided incompatible with the existing environment construction.

This is especially true in a variable stroke valve train of the same genus, as in the DE 196 11 641 C1 is proposed. Because the cam piece proposed there has three adjacent cams with different opening curves and is displaced by a pair of adjacently arranged adjusting devices in the two displacement directions. Since each pair of actuators has a distance of the actuator pins corresponding to a cam width and this is to be kept comparatively small, taking into account the freedom of movement of the cam piece to adjacent camshaft bearing points, it would come in this case to an inadmissible penetration of the actuators in the magnet.

One Another disadvantage of said adjusting device is the high Manufacturing and thus cost, the known from the complex production-technical handling of the permanent magnet with its magnetic properties results.

Object of the invention

Of the The present invention is therefore based on the object, an adjusting device of the aforementioned type so that the indicated Disadvantages are avoided. Accordingly, the holding and releasing device the least possible additional need for radial space relative to the Aktuatorstift and simultaneously Secure the actuator pin securely in the stop position. Furthermore should the actuator as simple as possible and under high-volume conditions be inexpensive to produce.

Summary of the invention

• – einen Sperrschieber, der in einer am zweiten Ende des Aktuatorstifts verlaufenden Längsbohrung relativ zu dieser verlagerbar angeordnet ist;
• – ein den Sperrschieber in Ausfahrrichtung des Aktuatorstifts kraftbeaufschlagendes weiteres Federmittel;
• – eine am Sperrschieber ausgebildete erste Stützfläche;
• – eine im Gehäuse ausgebildete zweite Stützfläche;
• – zumindest einen Sperrkörper, der in einer die Längsbohrung schneidenden Querbohrung beweglich angeordnet und in der Halteposition des Aktuatorstifts zwischen den Stützflächen infolge Selbsthemmung eingespannt ist, wobei die Stützflächen einen in Einfahrrichtung des Aktuatorstifts konstanten oder sich verkleinernden Abstand zueinander aufweisen;
• – und, zum Lösen des Aktuatorstifts aus der Halteposition, eine ansteuerbare und den Sperrschieber in Einfahrrichtung des Aktuatorstifts verlagernde Betätigungsvorrichtung.

The solution of this problem arises from the characterizing features of claim 1, while advantageous developments and refinements of the invention are the dependent claims can be removed. Accordingly, the object is achieved in that the holding and releasing device has at least the following features:

• - A locking slide which is arranged displaceable in a longitudinal bore extending at the second end of the actuator pin relative to this;
• - A further force-loading the locking slide in the extension direction of the actuator pin further spring means;
• - A formed on the locking slide first support surface;
• - A formed in the housing second support surface;
• - At least one locking body which is movably arranged in a transverse bore which cuts the longitudinal bore and is clamped in the holding position of the Aktuatorstifts between the support surfaces due to self-locking, wherein the support surfaces have a constant in the retraction direction of the Aktuatorstifts or decreasing distance from each other;
• - And, for releasing the actuator pin from the holding position, a controllable and the locking slide in the retraction of the actuator pin displacing actuator.

Therefore has the adjusting device according to the invention a Holding and releasing device, which does not over the actuator magnetic attractions with correspondingly large Active surface according to the cited state technology, but by clamping effect due to friction Self-locking of the locking body on the support surfaces against the force of the actuator pin acting in the extension direction Spring means fixed in the holding position. The radial space requirement the holding and releasing device is comparatively small, because the required holding force of the actuator pin as a clamping force between the support surfaces and the lock body is generated and one opposite a magnetic active surface requires considerably smaller contact area. The by a Such holding and releasing device generated clamping action prevents uncontrolled retraction of the actuator pin from the holding position in the direction of the working position, so that the Actuator pin the machine part or the cam piece directly Slipping after leaving the sliding groove worst case contacted, but without during subsequent work games to fall back into the displacement groove and, mechanically and acoustically unfavorable, again pushed out of this to become.

A essential property of the invention Adjusting device relates to the relative distance of the support surfaces with respect to the direction of travel of the actuator pin, wherein the distance the support surfaces in the retraction of the Aktuatorstifts constant is or diminishes. This causes the effort of the Actuating device for shifting the locking slide in the retraction direction of the Aktuatorstifts to solve the Actuator pin from the holding position a small fraction by the interaction of the locking body with the support surfaces generated clamping force for holding the actuator pin in the holding position equivalent. In the design of the support surfaces are of course both the forces of Spring means also as the friction conditions on the lock body support surface contacts to be considered, so that for a flawless Function of the holding and releasing device required area the self-inhibition at these contacts is not left.

With regard to the decreasing distance between the support surfaces to each other, it is provided in a more concrete embodiment of the invention that the first support surface tapers radially in the extension direction of the actuator pin and that the second support surface parallel to the direction of travel Actuator pin runs. This allows a particularly advantageous production of the housing, since the second support surface can be part of a continuous cylindrical guide bore for the actuator in the simplest case.

in the Regard to the constant distance of the support surfaces to each other it is in a more concrete embodiment of the invention provided that the first support surface in the extension direction of the actuator pin is radially tapered and that the support surfaces parallel to each other.

Furthermore the locking body should be designed as a ball, as they as an extremely cost-effective mass product of a Wälzkörperfertigung is removable. Here are advantageous three balls and three evenly over the periphery of the actuator pin distributed transverse bores in which the balls are arranged, provided. Opposite only one Ball this is advantageous in that either with identical dimensions the balls larger clamping forces generated or smaller dimensioning of the balls - accordingly a further reduced space requirement of the holding device - the if necessary, sufficient clamping force can only be generated by one ball. On the other hand, the arrangement of circumferentially distributed by 120 ° Balls for a mechanically favorable, centered support the locking slide in the longitudinal bore of the Ak tuatorstifts. Yet are of course also arrangements with only one, two, four or more balls possible.

Farther It is also in terms of cost manufacturability the adjusting device provided that at least one of the support surfaces rotationally symmetrical is designed for the direction of movement of the actuator. It can the first support surface or the second support surface or both be formed of a circular frustum. deviant However, there is also the possibility of the support surfaces to equip with raceways for the one or more locking bodies, in the case of the balls, for example, grooves with a circular segment-shaped cross section could act. In this connection it should also be mentioned that formed on the gate valve and in the housing Support surfaces of course not must run directly on these components, but also surfaces of separate components, such as the gate valve and in the housing attached rings or bushings may be.

In a particularly preferred embodiment of the invention, the actuator as Elektrohubmagnet with a locking slide actuated Anchor be formed. Although the actuator also on other known, for example hydraulic or pneumatic Acting principles can be based on the electromagnetic controlled gate valves are particularly fast in terms of time and with high speeds Press precision. With regard to low Manufacturing costs can be the gate valve and the anchor be combined into a one-piece component. In This case can be different mechanical and electromagnetic Requirements for the component properties, for example by adapted material selection with a possibly required wear-resistant surface coating Be taken into account.

After all it is envisaged that the spring means as concentric around the Locking slide extending helical compression spring is formed, the an end face of the second end of the Aktuatorstifts one hand and at one of the actuator pin facing end of an intermediate the helical compression spring and the armature fixedly arranged in the housing Socket is supported on the other hand. The function of the socket is not only on the support of the helical compression spring limited. Rather, those of the helical compression spring opposite end face of the bush as an axial stop for the anchor and the bushing bore as a longitudinal guide to serve for the gate valve.

Provided it is possible and appropriate the aforementioned features and configurations also arbitrarily with each other be combined.

Brief description of the drawings

Further Features of the invention will become apparent from the following description and from the drawings, in which embodiments of the Partial adjustment device according to the invention partially are shown. Unless otherwise stated, are included identical or functionally identical features or components with the same Reference numbers provided. Show it:

1 an overall view of an adjusting device according to the invention in longitudinal section;

2 a schematic diagram of the adjusting device in the region of the support surfaces with decreasing in the retraction of the Aktuatorstifts distance;

3 a schematic diagram of the adjusting device in the region of the support surfaces with a constant distance in the direction of retraction of the Aktuatorstifts;

4 designed as a unit actuator with three actuator pins and

5 a cooperating with the actuator Hubvariablen valve drive a Brenn engine in perspective view.

Detailed description the drawings

In 1 is an embodiment of an adjusting device according to the invention 1 discloses that for controlling a known and in 5 shown variable stroke valve train 2 an internal combustion engine is used. The basic operating principle of such a valve train 2 For example, goes from the cited documents DE 196 11 641 C1 and DE 10 2004 021 376 A1 and can be summarized to the effect that instead of a conventionally rigid camshaft, a carrier shaft 3 with a non-rotatably and longitudinally displaceably arranged cam piece 4 is provided. The cam piece 4 has two groups of axially adjacent cams 5 and 6 with different opening gradients, which for operating point-dependent actuation of gas exchange valves 7 serve. The for selective activation of the respective cam 5 or 6 required displacement of the cam piece 4 on the carrier shaft 3 via helical sliding grooves 8th on the cam piece 4 , Which differ according to the direction of displacement in their orientation and in, depending on the instantaneous position of the cam piece 4 , one actuator pin each 9 with his first end 10 can be coupled.

Starting from the in 1 shown first switching position of the adjusting device 1 in which the actuator pin 9 is in its retracted stop position, there is the coupling of the actuator pin 9 into the shifting groove 8th by extending the actuator pin 9 in its working position. It is clear that the sliding grooves 8th not just an axial protrusion to move the cam piece 4 on the carrier shaft 3 , but also a radially acting discharge area 11 have, whose collection the Aktuatorstift 9 shifted back to its stop position towards the end of the shifting process.

As already mentioned, it is an essential feature of the adjusting device according to the invention 1 that the actuator pin 9 after leaving the sliding door 8th does not fall back into this again, but is securely held in the holding position. In this holding position it comes at worst to a grinding, mechanically but uncritical contact of the actuator pin 9 with a to the outlet area 11 subsequent cylindrical surface section 12 while the actuator pin 9 otherwise with a sufficient distance to the cylindrical surface section 12 is held. This property results from the structure of the adjusting device according to the invention explained in detail below 1 ,

The adjusting device 1 includes an elongate cylindrical housing 13 with an actuator pin 9 overlapping longitudinal guide 14 , wherein the formed by a helical compression spring spring means 15 in the extension direction kraftbeaufschlagte actuator pin 9 relative to the housing 13 between its retracted holding position and its (not shown) working position in which the Aktuatorstift 9 around one of the depths of the sliding grooves 8th corresponding hub is extended, back and forth. To hold the actuator pin 9 in the holding position and for releasing the actuator pin 9 from the holding position is one with 16 designated holding and releasing device. The holding and releasing device 16 comprises one in the direction of travel of the actuator pin 9 and from this independently movable gate valve 17 as well as the gate valve 17 in the extension direction of the actuator pin 9 kraftiebeaufschlagendes further spring means 18 , here in the form of a spring tongue made of sheet metal. The trained as a cylindrical pin locking slide 17 is in one at the second end 19 of the actuator pin 9 extending and formed here as a blind hole longitudinal bore 20 arranged and has a circular frustoconical first end portion 21 on, wherein an imaginary tip of the circular cone in the extension direction of the Aktuatorstifts 9 has.

Including the 2 and 3 serves the first end section 21 the locking slide 17 as the first support surface 22 for three trained as balls locking body 23 running in three evenly over the circumference of the actuator pin 9 distributed and the longitudinal bore 20 cutting transverse bores 24 are movably arranged. As will be explained in detail below, the balls are supported 23 on the housing side on a second support surface 25 that either according to 2 parallel to the direction of travel of the actuator pin 9 runs or according to 3 , an enlarged schematic section of the support surfaces 22 . 25 in 1 represents, is also formed kreisgegelstumpfförmig. Consequently, the in 2 illustrated constellation of the support surfaces 22 . 25 geometrically shaped so that the support surfaces 22 . 25 one in the retraction of the Aktuatorstifts 9 have decreasing distance from each other. The inclination angle of the support surfaces 22 . 25 are accordingly α for the circular frustoconical first end portion 21 the locking slide 17 and β = 0 ° for the parallel to the direction of travel of the actuator pin 9 extending second support surface 25 of the housing 13 , The inclination angle α is taking into account the on the gate valve 17 and the actuator pin 9 acting spring forces and the friction conditions on the ball-support surface contacts chosen so that the balls 23 due to self-locking between the support surfaces 22 . 25 are clamped and so the actuator pin 9 securely fix in the holding position. A suitable angle of inclination α could be, for example, 5 °.

A deviating constellation of the support surfaces 22 . 25 to each other goes out 3 in which case the spacing of the support surfaces 22 . 25 to each other in the retraction direction of the Aktuatorstifts 9 is constant. Both the first support surface 22 the locking slide 17 as well as the second support surface 25 in the case 13 are formed with identical inclination angles α and β circular frustoconical. Also in this embodiment of the support surfaces 22 . 25 turns a frictional clamping of the balls 23 in the extension direction of the actuator pin 9 due to self-locking.

An essential property of in 3 illustrated constellation of the support surfaces 22 . 25 to each other is that a changed end position of the Aktuatorstifts 9 in the holding position according to the ball shown dotted 23 the corresponding axial position of the locking slide 17 due to the constant spacing of the support surfaces 22 . 25 unaffected. In other words, this results in an operation of the adjusting device 1 largely constant axial position of the locking slide 17 caused by dynamic end-position changes of the actuator pin 9 is almost independent in its holding position. However, this does not apply to the retraction direction of the Aktuatorstifts 9 decreasing distance of the support surfaces 22 . 25 according to 2 : as it is from the also dotted representation of the sphere 23 and the first support surface 22 shows, in this case due to component tolerances or inertia further retracted end position of the actuator pin 9 in the holding position to the same axial position change of the locking slide 17 ,

A from the constant position of the locking slide 17 according to 3 The resulting advantage relates to the dimensioning of a 1 illustrated actuator 26 as part of the holding and releasing device 16 is formed by a not shown here control unit of the internal combustion engine controllable Elektrohubmagnet. The electric lifting magnet 26 comprises as essential components a magnetic coil 27 with a magnetic core running inside 28 and the aforementioned spring tongue 18 one with the gate valve 17 at its second end portion 29 firmly connected anchors 30 in the extension direction of the actuator pin 9 with force. The different end positions of the actuator pin 9 largely independent position of the gate valve 17 results in a nearly constant distance of the armature 30 to the magnetic core 28 , so that when dimensioning the Elektrohubmagneten 26 Operational fluctuations of the air gap between the magnetic core 28 and anchor 30 can largely be disregarded.

One in the housing 13 pressed bush 31 serves with its magnetic coil 27 facing end face as axial stop for the anchor 30 and with her the actuator pin 9 facing end face as a support for the concentric to the gate valve 17 extending helical compression spring 15 , This is a great radial clearance to the gate valve 17 having inner diameter of the socket 31 may alternatively be designed so small that the socket 31 as a longitudinal guide for the gate valve 17 serves. To an inadmissible twist of the helical compression spring 15 due to rotation of the actuator pin 9 when engaged in the sliding groove 8th To prevent, it may be appropriate to the front pages of the socket 31 and / or the actuator pin 9 with good sliding properties or alternatively with separate sliding discs as a support for the helical compression spring 15 to provide.

Another embodiment of the invention is based 4 forth, in the three actuators accordingly 1 to a compact unit 32 are combined in a common housing. Such a unit 32 For example, with one opposite 5 cooperate modified valve train, in which case two immediately adjacent displacement grooves and three cams per cam group are to be provided according to a three-stage variable valve train on the cam piece.

Finally, let the operation of the adjusting device according to the invention 1 explained. Starting point is the in 1 illustrated state in which the actuator pin 9 due to the previously described clamping of the balls 23 between the support surfaces 22 . 25 is fixed in its holding position. A release of the actuator pin 9 from this holding position is by energizing the Elektrohubmagneten 26 initiated, the anchor 30 together with the gate valve 17 to the magnetic core 28 attracted and consequently the clamping action of the balls 23 opposite the support surfaces 22 . 25 will be annulled. The thus released actuator pin 9 is due to the force of the helical compression spring 15 driven into his working position, with the balls 23 in the case of the constant spacing of the support surfaces 22 . 25 according to 3 the inclination of the second support surface 25 in the case 13 follow and move radially inward in the cross holes 24 relocate. During the extension movement or after reaching the working position of the actuator pin 9 is the energization of Elektrohubmagneten 26 switched off, so that by the spring tongue 18 force-loaded gate valve 17 also shifted in the direction of the working position. This is the extension stroke of the locking slide 17 through the sleeve serving as an axial stop 31 limited.

In the case of the valvetrain 2 according to 5 is the retraction movement of the actuator pin 9 by the radial rise of the sliding grooves 8th generated. On due to the entrainment effect of the balls 23 follows the gate valve 17 this retraction movement either until reaching the holding position according to 2 or until shortly before reaching the stop position according to 3 , In the latter case, the Aktuatorstift shifts 9 with already stationary gate valve 17 continue in retraction while the bullets 23 the inclined course of the first support surface 22 following dodge radially. Upon reaching the holding position, the clamping action of the balls 23 one, leaving the actuator pin 9 is again fixed in its holding position.

1

locking device

2

valve train

3

carrier wave

4

cam piece

5

cam

6

cam

7

Gas exchange valve

8th

shift groove

9

actuator pin

10

first End of the actuator pin

11

discharge area

12

Cylinder surface section

13

casing

14

longitudinal guide

15

Spring means / helical compression spring

16

holding and release device

17

blocking slide

18

additional Spring means / spring tongue

19

second End of the actuator pin

20

longitudinal bore

21

first End portion of the locking slide

22

first support surface

23

Blocking body / ball

24

cross hole

25

second support surface

26

actuator

27

solenoid

28

magnetic core

29

second End portion of the locking slide

30

anchor

31

Rifle

32

unit

α

tilt angle the first support surface

β

tilt angle the second support surface

QUOTES INCLUDE IN THE DESCRIPTION

This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.

Cited patent literature

• WO 03/021612 A1 [0002]
• DE 102004021376 A1 [0003, 0024]
• - DE 19611641 C1 [0005, 0024]

Claims (10)

Adjusting device ( 1 ) with a housing ( 13 ) as well as in the housing ( 13 ), relative to the housing ( 13 ) extendable from a retracted holding position to a working position and by a spring means ( 15 ) in the extension direction force-loaded actuator pin ( 9 ) for adjusting one with the adjusting device ( 1 ) cooperating machine part, the one with a first end ( 10 ) of the actuator pin ( 9 ) in its working position cooperating Verschiebenut ( 8th ) having the actuator pin ( 9 ) displaced back into its holding position, wherein the adjusting device ( 1 ) a controllable holding and releasing device ( 16 ) for holding the actuator pin ( 9 ) in the holding position and for releasing the actuator pin ( 9 ) from the holding position, characterized by at least the following features having holding and releasing device ( 16 ): - a gate valve ( 17 ), which is in one at the second end ( 19 ) of the actuator pin ( 9 ) extending longitudinal bore ( 20 ) is arranged displaceable relative to this; - a lock slide ( 17 ) in the extension direction of the actuator pin ( 9 ) kraftbeaufschlagendes further spring means ( 18 ); - one on the gate valve ( 17 ) formed first support surface ( 22 ); - one in the housing ( 13 ) formed second support surface ( 25 ); At least one blocking body ( 23 ), which in one the longitudinal bore ( 20 ) intersecting transverse bore ( 24 ) and in the holding position of the Aktuatorstifts ( 9 ) between the support surfaces ( 22 . 25 ) is clamped in series self-locking, wherein the support surfaces ( 22 . 25 ) one in the retraction direction of the Aktuatorstifts ( 9 ) have constant or decreasing distance from each other; - and, for releasing the actuator pin ( 9 ) from the holding position, a controllable and the locking slide ( 17 ) in the retraction direction of the Aktuatorstifts ( 9 ) displacing actuator ( 26 ). Adjusting device ( 1 ) according to claim 1, characterized in that the first support surface ( 22 ) in the extension direction of the actuator pin ( 9 ) radially tapered and that the second support surface ( 25 ) parallel to the direction of travel of the actuator pin ( 9 ) runs. Adjusting device ( 1 ) according to claim 1, characterized in that the first support surface ( 22 ) in the extension direction of the actuator pin ( 9 ) radially tapered and that the support surfaces ( 22 . 25 ) parallel to each other. Adjusting device ( 1 ) according to claim 1, characterized in that the blocking body ( 23 ) is formed as a ball. Adjusting device ( 1 ) according to claim 4, characterized by three balls ( 23 ) and three evenly over the circumference of the Aktuatorstifts ( 9 ) distributed transverse bores ( 24 ), in which the balls ( 23 ) are arranged. Adjusting device ( 1 ) according to claim 1, characterized in that at least one of the support surfaces ( 22 . 25 ) rotationally symmetrical to the direction of movement of the Aktuatorstifts ( 9 ) is trained. Adjusting device ( 1 ) according to claim 6, characterized in that the first support surface ( 22 ) and / or the second support surface ( 25 ) is formed circular-frustoconical. Adjusting device ( 1 ) according to claim 1, characterized in that the actuating device ( 26 ) as Elektrohubmagnet with a locking slide ( 17 ) actuating armature ( 30 ) is trained. Adjusting device ( 1 ) according to claim 8, characterized in that the locking slide ( 17 ) and the anchor ( 30 ) are firmly connected. Adjusting device ( 1 ) according to claim 9, characterized in that the spring means ( 15 ) as concentric around the gate valve ( 17 ) extending helical compression spring is formed, which at one end face of the second end ( 19 ) of the actuator pin ( 9 ) on the one hand and on the actuator pin ( 9 ) facing end face of a between the helical compression spring ( 15 ) and the anchor ( 30 ) firmly in the housing ( 13 ) arranged bushing ( 31 ) on the other hand.