DE102007024598A1 - Regulation device has housing and controllable holding and release device to hold actuator pin in retaining position and to release actuator pin from retaining position - Google Patents

Abstract

The regulation device (1a) has a housing (13) and a controllable holding device (16a) and release device to hold the actuator pin (9) in the retaining position and to release the actuator pin from the retaining position. The two supporting surfaces (21,24) are inclined in such a manner for the traversing direction of the actuator pin so that the locking body (22) of the support surface is subjected to tension at actuator pin in retraction direction of the actuator pin.

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, the magnetic Anzie holding force holds the Aktuatorstift against the force of the spring means in the holding position on the de-energized electromagnet. For releasing the actuator pin from the holding position, only pulse-shaped energization of the electromagnet is required to overcome the magnetic attraction of the permanent magnet, the actuator pin not only by the force of the spring means but also by the force of a magnetic repulsion effect between the permanent magnet and the energized electromagnet in the direction 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, with different disadvantages ver be. 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 exists in the case of the illustrated variable-stroke valve train 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.

The usability of the adjusting device would be particularly in a variable stroke valve train of the same genus, as in the DE 196 11 641 C1 is proposed, as constructive prove extremely difficult. Because the cam piece proposed there has three adjacent No with different opening gradients 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 relatively small, taking into account the freedom of the cam piece adjacent camshaft bearing points, it would come in this case to an impermissible penetration of the actuators in the field of magnets.

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 a secure hold of the actuator pin within its residual stroke in the stop position. In other words should a radial as small as possible adjusting device be created that the actuator pin safe and opposite the Verschiebenut sufficient engagement free in the holding position fixed. In addition, the actuator should be possible easy and inexpensive under mass production conditions be produced.

Summary of the invention

• – einen in Verfahrrichtung des Aktuatorstifts und von diesem unabhängig verlagerbaren Sperrschieber sowie ein den Sperrschieber in Ausfahrrichtung des Aktuatorstifts kraftbeaufschlagendes weiteres Federmittel;
• – eine am Sperrschieber ausgebildete erste Stützfläche;
• – eine am Aktuatorstift ausgebildete zweite Stützfläche;
• – eine im Gehäuse ausgebildete dritte Stützfläche;
• – zumindest einen in der Halteposition des Aktuatorstifts zwischen den Stützflächen und auf diesen beweglich eingespannten Sperrkörper, wobei zwei der Stützflächen derart zur Verfahrrichtung des Aktuatorstifts geneigt sind, dass der Sperrkörper die zweite Stützfläche am Aktuatorstift in Einfahrrichtung des Aktuatorstifts kraftbeaufschlagt;
• – und, zum Lösen des Aktuatorstifts aus der Halteposition, eine ansteuerbare und den Sperrschieber in Einfahrrichtung des Aktuatorstifts verlagernde Betätigungsvorrichtung.

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

• - A further in the direction of travel of the actuator pin and independently displaceable locking slide and a locking slide in the extension of the actuator pin kraftbeaufschlagendes further spring means;
• - A formed on the locking slide first support surface;
• A second support surface formed on the actuator pin;
• - A formed in the housing third support surface;
• - At least one in the holding position of the Aktuatorstifts between the support surfaces and on this movably clamped locking body, wherein two of the support surfaces are inclined to the direction of movement of the Aktuatorstifts that the locking body, the second support surface on the Aktuatorstift in the retraction of the Aktuatorstifts kraftbeaufschlagt;
• - 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 the technology, but by clamping action against the force of the Actuator pin acting in the extension direction spring means in the holding position fixed. The radial space requirement of the retaining and release device is relatively small, since the required Holding force of the actuator pin here as a clamping force between the support surfaces and the clamp body is generated and one opposite a magnetic effective surface considerably smaller contact surface requires. The by such a holding and releasing device generated clamping action prevents on the one hand an uncontrolled Retracting the actuator pin from the stop position in the direction the working position, so that the actuator pin the machine part or the cam piece immediately after leaving the sliding groove inconveniently contacted, but without grinding during subsequent work games in the Verschiebenut fall back and, mechanically and acoustically unfavorable, to be pushed out of this again.

Apart from this limiting case, however, a particular effect of the adjusting device according to the invention basically results from the fact that the locking body is movably clamped in the holding position of the Aktuatorstifts on the support surfaces and due to the inclination of the support surfaces of the actuator pin in its retraction force. Depending on the friction conditions between the clamping body and the support surfaces on the one hand and the selected spring forces of the spring means and the other spring means on the other hand, this can lead to an intermittent or continuous automatic retraction of the Aktuatorstifts in the holding position, while simultaneously displacing the locking slide in the extension of the Aktuatorstifts. To put it simply, this means that the holding and releasing device pulls the actuator pin further in the retraction direction beyond the retraction stroke generated by the radial course of the displacement groove and against the force of the spring means acting on it. Consequently, the holding position is, strictly speaking, not a fixed position of the actuator pin, but rather a residence area in which the actuator pin in the abovementioned limiting case Machine part or the cam piece straight contacting contacted, but without coming into engagement with the sliding groove, and is otherwise held with more or less large safety distance to the machine part or the cam piece.

The The aforementioned intermittent retraction of the actuator pin can at appropriate constellation of friction conditions and the spring forces due to vibration-induced mass effects be caused on Aktuatorstift, wherein the holding and releasing device similar like a freewheel the actuator pin locks in the extension direction and releases in the retraction direction. This property also performs that the actuator pin due to concentricity errors on the adjoining the sliding door section of the Machine part or the cam piece continue in retraction relocated and held there.

In contrast, is a continuous further retraction of the actuator pin in particular then expect, if at very small frictional forces, the force the other spring means significantly larger than the Force of the spring means is and the on the support surfaces sliding and / or rolling blocking body together Reluctant to move with the actuator pin in the retraction direction can.

There the applied by the actuator release force at the locking slide much smaller than the producible clamping force on Aktuatorstift is, in addition to the holding and releasing device also the actuator largely independent made of their physical action radially very small construction become.

Around a complete retraction of the actuator pin in the holding position up to the mechanically predetermined stop limits of the adjusting device to enable, it is provided in development of the invention, that in the holding position, the force of the further spring means always greater than the force of the spring means is.

As is also clear from a later explained embodiment of the invention, also a Hubumkehrverhältnis h _A / h _{S is provided} from 0.5 to 1, where h _{A is} the stroke of the actuator pin in its retraction and h _S the stroke of the locking slide in the extension direction of Actuator are each in the holding position of the actuator. The Hubumkehrverhältnis is dependent on the inclination size and difference of the two support surfaces, which cooperate with the locking body, that this force the support surface on the Aktuatorstift in its retraction direction.

In Another embodiment of the invention, the locking body be designed as a ball, as they are extremely inexpensive Removable mass product of Wälzkörperfertigung is.

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. deviant However, there is also the possibility of the support surfaces equipped with raceways for the clamping body, which is in the case of the ball, for example, a groove with could act circular segmental cross-section. In this context it should also be mentioned that the on the lock slide over and support surfaces formed on the actuator pin and in the housing Of course, do not run directly on these components but also surfaces of separate Components, such as rings or bushings, may be on the Locking slide, attached to the actuator pin or in the housing are.

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 also be the gate valve and the anchor combined to form a one-piece component be. In this case, different mechanical and electromagnetic requirements for component properties for example by adapted material selection with an optionally required, wear-resistant surface coating Be taken into account.

In a kinematic embodiment of the invention is intended in the holding position of the actuator pin of the locking slide the actuator pin engage around at its second end, wherein the first support surface on the gate valve and the second support surface on Actuator pin enlarging in the extension direction of the Aktuatorstifts Have distance.

In a kinematic alternative embodiment are intended in the holding position of the actuator pin as a cylindrical pin trained locking slide in a running at the second end of the Aktuatorstifts Longitudinal bore and the locking body in a Longitudinal bore intersecting and the second support surface be arranged forming transverse bore. In this case, the first support surface on the gate valve and the third Support surface in the housing a in Increase retraction direction of the Aktuatorstifts Distance up.

Conveniently, are three trained as balls locking body and three evenly over the circumference of the Actuator pin distributed transverse bores in which the balls arranged are provided. This arrangement is opposite only a ball on the one hand therefore advantageous because either identical Ball diameter larger clamping forces are producible or smaller ball diameter - accordingly a further reduced space requirement of the holding and releasing device - the if necessary, sufficient clamping force can only be generated by one ball. On the other hand, the arrangement of distributed by 120 ° leads Balls for a mechanically favorable, centered support the locking slide in the longitudinal bore of the Aktuatorstifts.

Furthermore should designed as an external helical compression spring Spring means and designed as an inner helical compression spring further spring means may be arranged concentrically with each other, wherein the outer helical compression spring on a front side the second end of the actuator pin arranged sliding disk and the inner helical compression spring on the part of the Aktuatorstifts on one firmly connected to the cylindrical pin Axialbund each one end are supported. The sliding disk is used for rotary decoupling the actuator pin and the associated helical compression spring, so that the transmission of a rotational movement of the actuator pin, which caused by its frictional contact on the sliding groove can be on the outer helical compression spring prevents and these in terms of their fatigue not is twisted inadmissible. A corresponding rotary Decoupling of the cylindrical pin and the associated inner helical compression spring by means of correspondingly good sliding properties However, the Axialbunds may also be appropriate be. This is the case when the rotation of the actuator pin by friction in the longitudinal bore on the cylindrical Transfer pin with its axial collar and - without further action - also inadmissible Twisting of the inner helical compression spring would result.

Further should the third support surface in the housing in an axial shoulder with a substantially parallel to the sliding disk go over the running ring end face. These serves as an end stop for the sliding disk when extended Actuator pin.

A Inadmissible twisting of the helical compression springs should also also be prevented by the helical compression springs respectively the other end on a housing-fixed further sliding washer together are supported. In the case of trained as Elektrohubmagnet Actuator can one between the other Sliding disc and the armature arranged ring of non-magnetic material be provided. The function of this ring is the magnetic To conduct field lines of the energized Elektrohubmagneten so that the armature is always tightened in the retraction direction of the actuator pin becomes.

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 Adjusting device according to the invention partially simplified are shown. Unless otherwise stated, are the same or functionally identical features or components with the same Reference numbers provided. Show it:

1 a first embodiment of an adjusting device according to the invention in longitudinal section with actuator pin in the holding position,

2 a hubvariabler valve drive of an internal combustion engine cooperating with the adjusting device in a perspective view,

3 the cross section II according to 1 .

4 an enlarged detail view 1 at maximum extended actuator pin in the holding position,

5 the detailed view according to 4 at maximum retracted actuator pin in the holding position,

6 the adjusting device according to 1 with released gate valve,

7 the adjusting device according to 6 with actuator pin in the working position and

8th A second embodiment of an adjusting device according to the invention in a greatly simplified longitudinal sectional view.

Detailed description the drawings

In 1 is a first embodiment of an adjusting device according to the invention 1a discloses that for controlling a known and in 2 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 that effect sen, 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 , an actuator pin 9 with his first end 10 can be coupled.

Starting from the in 1 shown first switching position of the adjusting device 1a 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, the holding position is a residence area of the actuator pin 9 , after leaving the Verschutsut a to the outlet area 11 subsequent cylindrical surface section 12 worst case contact, but without again in the Verschiebenut 8th fall back, and otherwise kept at a distance from the cam piece in the holding position.

This property results from the structure of the adjusting device according to the invention explained in detail below 1a , This includes an elongated cylindrical housing 13 with an actuator pin 9 overlapping longitudinal guide 14 , wherein the spring means formed by an outer helical compression spring 15 in the extension direction kraftbeaufschlagte actuator pin 9 relative to the housing 13 between its retracted stop position according to 1 and its extended working position according to 7 moves 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 16a designated holding and releasing device.

The holding and releasing device 16a 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 an external helical compression spring 15 concentrically arranged inner helical compression spring whose force in the holding position of the Aktuatorstifts 9 about a factor of 1.5 greater than that of the external helical compression spring 15 is.

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 through hole longitudinal bore 20 arranged and has a circular frustoconical first end portion. Including 3 the first end section serves as the first support surface 21 for three trained as balls locking body 22 running in three evenly over the circumference of the actuator pin 9 distributed and the longitudinal bore 20 cutting transverse bores are arranged. The transverse bores each form a second support surface 23 for the balls 22 located on a circular cone-shaped third support surface 24 in the case 13 support.

How out 4 shows, are the first support surface 21 on the gate valve 17 and the third support surface 24 in the case 13 to the direction of movement of the actuator pin 9 inclined, in such a way that they are in the holding position of the actuator pin 9 have a widening in the retraction direction distance. Through this geometric constellation and due to the power ratio of the helical compression springs 15 and 18 is the in the extension direction of the Aktuatorstifts 9 effective excess force of the inner helical compression spring 18 over the gate valve 17 and the balls 22 on the second support surfaces 23 in the retraction of the Aktuatorstifts 9 diverted. Because the balls 22 between the support surfaces 21 . 23 and 24 are movably clamped, this force deflection can lead depending on the friction conditions on the one hand, that the Aktuatorstift 9 together with the balls 22 automatically, ie without outside influence by the radial outlet area 11 the shifting groove 8th continue to shift in retraction, leaving the first end 10 of the actuator pin 9 already shortly after leaving the sliding door 8th a sufficient safety distance to the cylindrical surface portion 12 of the cam piece 4 occupies (see 2 ). Additionally or alternatively, however, depending on the selected geometry / inclination of the support surfaces 21 . 23 and 24 and the friction conditions on these and in dependence of the helical compression springs 15 and 18 outgoing spring forces also the possibility that further retraction of the actuator pin 9 in the holding position by vibration excitation and / or by concentricity error of the cylindrical surface portion 12 is supported or initiated during operation of the internal combustion engine.

As it continues in the 6 and 7 can be seen, includes the holding and releasing device 16a one of a not shown here control unit of the internal combustion engine controllable and designed as Elektrohubmagnet actuator 25 that the gate valve 17 for releasing the actuator pin 9 from the holding position in the retraction of the Aktuatorstifts 9 relocated. This is where the balls are going 22 no longer from the first support surface 21 on the gate valve 17 supported, so that the balls 22 in the cross holes 23 can shift in the radially inward direction and by the outer helical compression spring 15 force-loaded actuator pin 9 together with the balls 22 in the in 7 shown working position extends.

The actuator 25 includes as essential components one on the housing 13 attached magnet housing 26 , an electric coil 27 , an electrical contact 28 as well as an anchor 29 , The gate valve 17 and the anchor 29 are firmly connected by the second end section 30 the locking slide 17 in a recess 31 of the anchor 29 is pressed. The anchor 29 is also with a flattening 32 which ensures that in the conical space between the anchor 29 and the anchor 29 in the retraction of the Aktuatorstifts 9 attractive pole surface 33 located air or accumulated oil in the extension of the actuator pin 9 along the anchor guide surface 34 inside the electric coil 27 can escape.

As an end stop for the anchor 29 is one in the housing 13 attached ring 35 with an opening for the gate valve 17 intended. To be in the position of the anchor 29 according to 1 a magnetic force of attraction in the direction of the pole face 33 Being able to produce is the ring 35 Made of non-magnetic, ie non-magnetizable material such as plastic, aluminum or austenitic steel.

An extensive decoupling of the helical compression springs 15 and 18 of component rotation occurring when coupling the actuator pin 9 in the move groove 8th over the actuator pin 9 in the adjusting device 1a are initiated by a front side of the second end 19 of the actuator pin 9 arranged sliding disk 36 and one on the ring 35 supporting further sliding washer 37 generated. While the outer helical compression spring 15 on the sliding disk 36 and the inner helical compression spring 18 on a tight with the gate valve 17 connected Axialbund, here in the form of a pressed-sleeve 38 , are supported at one end, support both helical compression springs 15 and 18 on the other sliding disk 37 at the other end together. One above the low surface friction value of the sliding discs 36 and 37 Extending rotary decoupling of the other sliding disk 37 and the ring 35 is achieved by the fact that the ring 35 a relatively large chamfer 39 and consequently a small contact surface with the additional sliding disk 37 having.

In the 4 and 5 are two limit positions between which the actuator pin 9 in the stop position, shown. In the position according to 4 is the actuator pin 9 maximally extended. Relative to this is the actuator pin 9 in the position after 5 maximum retracted by the stroke designated by h _A , so that its first end 10 a corresponding distance to the cylinder surface portion 12 (please refer 2 ) having. The stroke h _{A of} the actuator pin 9 in the retraction direction correlated with the stroke h _{S of} the gate valve 17 in the extension direction over the quotients h _A / h _S referred to below as the stroke reversal ratio. This results from the inclinations of the first support surface 21 on the gate valve 17 and the third support surface 24 in the case 13 , In the embodiment shown here are the first support surface 21 by α ₁ = 5 ° and the third support surface 24 tilted by α ₂ = 10 °, so that sets a Hubumkehrverhältnis of nearly 1. It is obvious that the Hubumkehrverhältnis with increasing difference in inclination of the support surfaces 21 and 24 would lose weight.

In 5 is also clearly seen that the third support surface 24 in the case 13 in an axial shoulder with a parallel to the sliding disk 36 extending annular end face 40 passes. This ring end face 40 serves as end stop for the sliding disk 36 in the working position of the actuator pin 9 according to 7 ,

In 8th is another embodiment of an adjusting device according to the invention 1b shown greatly simplified. The adjusting device 1b differs from the previously explained in detail adjusting device 1a essentially in that the locking slide 17 the actuator pin 9 at its second end 19 engages, being in the holding position of the actuator pin 9 the first support surface 21 on the gate valve 17 and the second support surface 23 on the actuator pin 9 a in the extension direction of the Aktuatorstifts 9 have increasing distance. Opposite the actuator 1a has the adjusting device 1b as it were a holding and releasing device 16b in kinematic reverse arrangement, by the gate valve 17 not inside, but outside the actuator pin 9 and the locking bodies 22 axially fixed in the housing 13 are arranged. Another difference concerns the arrangement of the spring means 15 and the other spring means 18 in that the actuator pin 9 force-applying spring means 15 not on the case 13 , but at the gate valve 17 is supported.

1 a, b

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 the shifting groove

12

Cylinder surface section

13

casing

14

longitudinal guide

15

Spring means / outer Helical compression spring

16a, b

holding and release device

17

blocking slide

18

additional Spring means / inner helical compression spring

19

second End of the actuator pin

20

longitudinal bore

21

first End section / first support surface on the locking slide

22

Blocking body / ball

23

Transverse bore / second Support surface on the actuator pin

24

third Support surface in the housing

25

Actuator / electric lifting magnet

26

magnet housing

27

electric coil

28

contact

29

anchor

30

second End portion of the locking slide

31

recess of the anchor

32

flattening of the anchor

33

pole

34

Armature guide surface

35

non-magnetic ring

36

sliding disk

37

Further sliding disk

38

Axial collar / sleeve

39

chamfer of the ring

40

Annular face

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, 0035]
• - DE 19611641 C1 [0005, 0035]

Claims (15)

Adjusting device ( 1a . 1b ) 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 ( 1a . 1b ) 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 ( 1a . 1b ) a controllable holding and releasing device ( 16a . 16b ) 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 ( 16a . 16b ): One in the direction of travel of the actuator pin ( 9 ) and of this independently movable gate valve ( 17 ) as well as the locking 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 ( 21 ); - one on the actuator pin ( 9 ) formed second support surface ( 23 ); - one in the housing ( 13 ) formed third support surface ( 24 ); At least one in the holding position of the actuator pin ( 9 ) between the support surfaces ( 21 . 23 . 24 ) and on this movably clamped blocking body ( 22 ), wherein two of the support surfaces ( 21 . 23 . 24 ) in such a way to the direction of movement of the Aktuatorstifts ( 9 ) are inclined, that the blocking body ( 22 ) the second support surface ( 23 ) on the actuator pin ( 9 ) in the retraction direction of the Aktuatorstifts ( 9 ) charged with force; - 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 ( 25 ). Adjusting device ( 1a . 1b ) according to claim 1, characterized in that the machine part as on a support shaft ( 3 ) non-rotatably and longitudinally displaceable cam piece ( 4 ) of a variable-stroke valve drive ( 2 ) is formed of an internal combustion engine. Adjusting device ( 1a . 1b ) according to claim 1, characterized in that in the holding position of the Aktuatorstifts ( 9 ) the force of the further spring means ( 18 ) always greater than the force of the spring means ( 15 ). Adjusting device ( 1a . 1b ) according to claim 1, characterized in that a Hubumkehrverhältnis h _A / h _S of 0.5 to 1 is provided, wherein h _{A is} the stroke of the Aktuatorstifts ( 9 ) in the retraction direction of the Aktuatorstifts ( 9 ) and h _{S is} the stroke of the locking slide ( 17 ) in the extension direction of the actuator pin ( 9 ) in each case in the holding position of the Aktuatorstifts ( 9 ) are. Adjusting device ( 1a . 1b ) according to claim 1, characterized in that the blocking body ( 22 ) is formed as a ball. Adjusting device ( 1a . 1b ) according to claim 1, characterized in that at least one of the support surfaces ( 21 . 23 . 24 ) rotationally symmetrical to the direction of movement of the Aktuatorstifts ( 9 ) is trained. Adjusting device ( 1a ) according to claim 1, characterized in that the actuating device ( 25 ) as Elektrohubmagnet with a locking slide ( 17 ) actuating armature ( 29 ) is trained. Adjusting device ( 1a ) according to claim 7, characterized in that the gate valve ( 17 ) and the anchor ( 29 ) are firmly connected. Adjusting device ( 1b ) according to claim 1, characterized in that in the holding position of the Aktuatorstifts ( 9 ) the gate valve ( 17 ) the actuator pin ( 9 ) at its second end ( 19 ), wherein the first support surface ( 21 ) on the gate valve ( 17 ) and the second support surface ( 23 ) on the actuator pin ( 9 ) in the extension direction of the Aktuatorstifts ( 9 ) have increasing distance. Adjusting device ( 1a ) according to claim 1, characterized in that in the holding position of the Aktuatorstifts ( 9 ) formed as a cylindrical pin locking slide ( 17 ) in one at the second end ( 19 ) of the actuator pin ( 9 ) extending longitudinal bore ( 20 ) and the blocking body ( 22 ) in a longitudinal bore ( 20 ) and the second support surface ( 23 ) are arranged transverse bore, wherein the first support surface ( 21 ) on the gate valve ( 17 ) and the third support surface ( 24 ) in the housing ( 13 ) in the retraction direction of the Aktuatorstifts ( 9 ) have increasing distance. Adjusting device ( 1a ) according to claim 10, characterized in that three locking bodies designed as balls ( 22 ) and three evenly over the circumference of the Aktuatorstifts ( 9 ) distributed transverse bores ( 23 ), in which the balls ( 22 ) are arranged are provided. Adjusting device ( 1a ) according to claim 10, characterized in that the spring means formed as an external helical compression spring ( 15 ) and formed as an inner helical compression spring further spring means ( 18 ) are arranged concentrically with each other, wherein the outer helical compression spring ( 15 ) on a front side of the second end ( 19 ) of Aktua torstifts ( 9 ) arranged sliding disk ( 36 ) and the inner helical compression spring ( 18 ) by the actuator pin ( 9 ) on a fixed with the cylindrical pin ( 17 ) associated axial collar ( 38 ) are supported at one end. Adjusting device ( 1a ) according to claim 12, characterized in that the third support surface ( 24 ) in the housing ( 13 ) in an axial shoulder with a substantially parallel to the sliding disk ( 36 ) extending annular end face ( 40 ) passes over. Adjusting device ( 1a ) according to claim 12, characterized in that the helical compression springs ( 15 . 18 ) at the other end on a housing-fixed further sliding washer ( 37 ) are jointly supported. Adjusting device ( 1a ) according to claims 7 and 14, characterized by a between the other sliding washer ( 37 ) and the anchor ( 29 ) arranged ring ( 35 ) of non-magnetic material.