EP2039944A2 - Linear actuator, in particular cylinder-piston unit with locking device - Google Patents

Abstract

The drive (1) has a threaded spindle (28) supported in an end housing (9) of a cylinder body (4) in a rotatable manner. A locking element (35) is arranged in the housing and formed by a rotational symmetric locking body (36) with a rotational symmetric axis (37) lying parallel to a longitudinal axis and a movement area (38) accommodating the locking body. The movement area is changed with respect to the longitudinal axis in a radial direction by an operating surface (44) of an operating unit (41) supported in the housing, and adjusted between a releasing position and a locking position (45).

Description

The invention relates to a Linearverstellantrieb as described in the preamble of claim 1.

It is often necessary to fix a Linearverstellantrieb in end positions or intermediate positions, so that this position is reliably maintained even when external forces occur and an unintentional adjustment of the position is prevented. Such Linearverstellantrieb is acted upon as a pressurized medium double-acting hydraulic cylinder with locking device of the EP 1 106 841 A known, in which a tubular piston rod is formed with a working piston and in a pressure cylinder against rotation by pressurization with a pressurized fluid is arranged linearly adjustable. In the piston rod and with this movement connected to a threaded spindle is arranged, which is offset by longitudinal adjustment of the piston in a rotary motion. This threaded spindle is rotatably mounted in an end housing of the cylinder and can be blocked by means of a switchable locking arrangement in its rotational movement. In this case, the blocking arrangement comprises a blocking piston which can be acted upon by a pressure medium and projects into the locking position in at least one locking receptacle arranged on the circumference of the threaded spindle with a blocking extension facing in the radial direction of the cylinder longitudinal center axis.

Although a Linearverstellantrieb with such a locking arrangement has a relatively simple technical structure, a disadvantage of this design, however, is that the components of the locking arrangement, in particular the barrier extension are subject to heavy wear.

The object of the invention is to provide such a Linearverstellantrieb, in particular a pressurizable with a pressure medium cylinder-piston unit with a locking arrangement, which avoids the disadvantages mentioned also with a simple structure.

This object of the invention is achieved by the reproduced in the characterizing part of claim 1 features, according to which the locking element engaging in the locking receptacle blocking element is formed by a rotationally symmetrical locking body with a cylinder longitudinal axis approximately parallel or only slightly inclined rotational symmetry axis and in the end housing, the blocking body receiving movement space is formed, which is variable in the radial direction with respect to the cylinder longitudinal axis of an actuating surface of an adjustable between a release position and a locking position actuator. For this purpose, the actuating element can, for example, execute a rectilinear or a rotating adjusting movement, that is to say be mounted as a locking slide in a linear guide or as a rotatably mounted rotary body.

In the blocking position, therefore, the blocking body is urged by the actuating surface of the actuating element in the locking receptacle of the threaded spindle and an optionally by an external load on the piston assembly acting on the threaded spindle torque on the set in the locking recess locking body in the end housing and a movement of the piston assembly reliable prevented. By adjusting the actuator with its actuating surface in the release position of the movement space for the locking body in the radial direction is increased whereby this is displaced in a possible rotational movement of the threaded spindle in the enlarged radial direction of movement space, whereby the rotational movement of the threaded spindle and thus the longitudinal displacement of the piston in the Cylinder is no longer blocked.

In a linear drive according to the invention, the contact point between the locking body and the actuating surface at the release position has a greater distance from the cylinder longitudinal axis than in the blocking position. The distance of the contact point and thus also the center or rotational symmetry axis of the blocking body from the cylinder longitudinal axis changes during the transition from the blocking position into the release position and vice versa. The point of contact may remain unchanged on the actuating surface in this process, e.g. However, the contact point is in many cases change its position on the actuating surface in a locking operation or a release operation, whereby the wear stress on the actuating surface is not concentrated on a single point and the risk of premature wear and tear is reduced.

The surprising advantage here is that by using a rotationally symmetrical locking body, for example, a ball or a circular cylinder, this can perform minor rotational movements in use during locking operations or release operations and a wear occurring due to the blocking forces on the locking body can be distributed over its entire surface, while in the use of a barrier extension associated with a locking piston this is always claimed in the same places and therefore wear occurs earlier. The life of such a Linearverstellantriebes can be much higher compared to the prior art and the economy can be increased due to lower maintenance or repair costs.

The linear drive according to the invention, for example, as a hydraulically actuated pressure cylinder but also be designed as a pull cylinder, the outer cylinder pressure acting primarily in the retraction of the piston rod and a fixation is required in the extended state, while it acts on the pull cylinder in the extension direction of the piston rod and the retracted state to secure the piston assembly.

It is possible that the axis of rotational symmetry of the locking body to the cylinder longitudinal axis has a small angle of inclination of up to 15 °, whereby the contact forces occurring between threaded spindle and locking sleeve and locking body also have axial components that support the axial bearing of the threaded spindle in one direction and the corresponding parts of the axial bearing are loaded accordingly less or this can be made simpler.

As already mentioned above, there are various possibilities for the embodiment of the actuating element with the actuating surface acting on the blocking body. Thus, the actuating element may be designed as a rotatably mounted in the end housing rotary body which forms the actuating surface with a non-concentric with respect to its axis of rotation peripheral surface which acts in such an embodiment as the peripheral surface of an eccentric or a clamping cam.

A further embodiment consists in that the actuating element is designed as a linearly guided locking slide, which is mounted in a linear guide in the end housing and urges the locking body in the blocking position in a locking recess on the threaded spindle or a rotatably connected thereto locking sleeve.

Both of the aforementioned embodiments can use the principle of an inclined plane, whereby a force applied to the actuating element actuating force is converted into a larger acting on the locking body fixing force. A large actuating travel of the actuating element causes in this case a small radial change of the movement space with corresponding power amplification.

An advantageous development is that the actuating surface of the actuating element has a helix angle to a tangential surface on the circumference of the threaded spindle or the locking sleeve in the region of the locking body, that is not aligned at right angles to the radial direction. The movement of the blocking body within the movement space can be influenced by the contact forces acting on the blocking body from the actuating surface act not only in the radial direction, but also may have tangential or axial components relative to the cylinder longitudinal axis and thereby in the release position, the position of the locking body can be controlled within the movement room. Furthermore, can be adjusted in the radial direction by this inclination of the actuating surface of the movement space, without that the actuating element must have a radial movement component.

The displacement direction of the locking slide can in this case in particular run parallel to a tangential surface on the circumference of the threaded spindle, whereby the radial length of the locking arrangement can be reduced.

According to a further embodiment, the direction of displacement of the locking slide in the form of a locking slide can also extend at right angles to a radial plane through the cylinder longitudinal axis, d. H. the direction of displacement of the locking slide is parallel to a tangent to the threaded spindle or the locking sleeve in the region of the blocking body. As a result, not only the radial size but also the axial length of the lock assembly is significantly reduced.

In order to achieve high reliability, it is advantageous if a force acting on the actuating element in the direction of the locking position spring element is provided. Thus, the blocking function of the locking arrangement is ensured as long as the release position of the actuating element is not effected by active actuation by the application of force against the spring force.

The spring element can be formed by two concentric compression springs, whereby in case of failure of a compression spring still a sufficient spring force for displacement of the actuating element can be present in the blocking position and thereby the reliability is further increased.

For reasons of a simple production of the locking slide can be arranged in particular in a locking slide guide with a circular cross-section. Of course, however, other cross-sectional shapes, for example, a rectangular cross-sectional shape of the locking slide guide may be formed.

Favorable power relationships in the displacement of the locking body in the locking recess are achieved when the actuating surface relative to the direction of the locking slide by a pitch angle, in particular by a pitch angle is less than 45 ° inclined. The force exerted radially on the locking body of the actuating surface contact force, for example, at a pitch angle smaller than 30 ° at least twice as large as the force applied to the displacement of the locking slide actuating force, whereby relatively small forces are required for a drive of the locking slide. Here, the previously mentioned principle of the inclined plane is applied.

The actuation surface can furthermore have different inclinations with respect to the displacement direction, for example in the region of the release position, which already causes a relatively large radial displacement of the blocking body with slight displacement of the blocking slide and, for example, a slight incline in the blocking position has, whereby a further displacement of the locking slide causes only a small radial displacement of the locking body. Due to the different slopes thus different ratios between the movement of the locking slide and the radial movement of the locking body can be effected.

The actuating surface may further comprise a fixing portion which is adapted to the cross section of the locking body. This can thereby engage, for example, in the blocking position of the locking slide or the rotating body quasi in the actuating surface, whereby the locking slide can be reliably held by the spring elements in the blocking position.

The actuating surface in the fixing section may preferably have a pitch angle of less than 10 °, in particular less than 5 °, whereby the effect of a self-locking between locking body and the gate valve can be achieved.

The contact forces required for a locking of the threaded spindle can be effective between the locking receptacle and the blocking body on the one hand and the locking body and the actuating surface on the other hand, which alone can be sufficient for securing the piston position. For a secure fixation of the locking body and thus a secure blocking of the rotational movement of the threaded spindle, however, it is advantageous if the movement space for the locking body is limited at least in a tangential direction by a rigid stop element in the end housing. This stop element may be formed for example by a portion of a bore inner wall in the end housing or a flat inner wall in the end housing.

The stop element, which blocks the movement of the blocking body in the tangential direction, can in particular run parallel to a radial plane through the cylinder axis, whereby the blocking body is guided by the stop element in the radial direction. In particular, both tangential directions can be assigned a stop element, whereby the locking body pressed into the locking exception can block the rotation of the threaded spindle in both circumferential directions by being able to be supported in both circumferential directions against a stop element.

In contrast, the movement space for the blocking body in a tangential direction can also be limited by a spring-loaded, tangentially compliant insertion element. This causes a guide of the locking body during the shift from the release position to the blocking position, in which this protrudes into the locking recess and additionally allows the function of a freewheeling of the locking arrangement in the circumferential direction, in which the locking body is pressed against the tangentially resilient Einsteuerelement. In the opposite circumferential direction of the locking body is blocked by the stop element and thus also prevents the rotational movement of the threaded spindle when the movement space is restricted in the radial direction by the actuating element in the blocking position.

Preferred embodiments of the Linearverstellantriebs are the locking body as a ball, as a circular cylinder, as a circular truncated cone or barrel-shaped form. The cooperating Sperrausnehmungen are accordingly spherical cap, circular cylinder segment-shaped, circular cone segment-shaped or barrel-shaped concave. Due to the selected shape of the blocking body, the position and direction of the locking recess and locking body on the one hand and the locking body and actuating surface on the other hand acting contact forces can be favorably influenced.

Compact dimensions of the end housing are achieved when a maximum diameter of the locking body corresponds to a maximum of 0.3 times a threaded spindle diameter or a locking sleeve diameter, since with larger blocking bodies, the required movement space in the end housing must be made correspondingly larger.

Furthermore, it is advantageous if a radial depth of the locking recess corresponds to a maximum of 0.4 times the maximum diameter of the blocking body. At deeper penetration of the locking body in the locking recess acting between locking recess and locking body contact force could continue to migrate in the tangential direction and makes it difficult to displace the locking body in the released from the gate valve in the release position movement space, d. H. the locking body could also wedge in the release position of the actuator in the locking receptacle and block the cylinder-piston unit unintentionally.

Furthermore, the locking recess may have an effective radius between 1.0 times and 1.1 times a radius of the locking body. At a 1.0 times ratio thus corresponds to the inner contour of the locking recess exactly a part of the outer contour of the locking body, whereby it can take a solid, largely backlash-free seat in the locking recess. The radial depth of the locking recess must not be too large in this case, so that the locking body is not accidentally wedged in the locking recess. An embodiment with a locking recess with a 1.1-fold effective radius relative to the radius of the locking body, however, has a slight work cycle, so that the entry or exit of the locking body is facilitated in the locking recess, however, a larger contact force between the locking body and actuating surface is required to obtain a secure barrier effect.

So that the locking arrangement already after the smallest possible angular rotation of the threaded spindle can be effective by the locking body is urged by the actuating surface in a locking recess, it is advantageous if the threaded spindle or the locking sleeve has at least six equally distributed on the outer periphery locking recesses.

An advantageous development of the Linearverstellantriebs may be that the material hardness of the locking body is selected to be greater than the material hardness of the actuating element. By this combination of materials wear occurs mainly on the actuator, which is easier to replace via an access in the end housing, as the locking body.

Although it is also possible that the locking slide is manually operated by a user, it is advantageous if the actuating element is adjustable by means of a control from the blocking position to the release position. The adjustment in the direction of the blocking position is advantageously carried out in this case by means of a previously described spring element. The unlocking of the lock assembly can be automated with the help of the control, whereby the unlocking does not have to be performed by the user.

In particular, the control element may be formed by a fluid-operated control piston, for example a hydraulically actuated control piston which is mounted in the end housing. As a result, large actuation forces can be applied to the locking slide or the rotary body in order to shift it against the high spring forces of the spring elements, which are high for safety reasons, from the blocking position into the release position.

It is advantageous in this case if an adjustment direction of the control piston runs parallel to the displacement direction of the locking slide, since thereby the Aufsteuervorgang can be performed with the least possible friction losses and the Aufsteuerkolben can thereby be made smaller, whereby the end housing is kept compact.

In order to effect the deactivation of the locking arrangement necessary for a movement of the piston assembly of the cylinder, the control piston acting on the actuating element can be fluid-connected to a first pressure medium line leading to the piston bottom side cylinder space or to a second pressure medium line leading to the piston rod side cylinder space and the movement space for the blocking body in FIG a tangential direction, which corresponds to the unlockable by the control piston movement direction of the piston assembly to be limited by a spring-loaded tangentially resilient Einsteuerelement. For a direction of movement of the piston assembly thus a freewheeling function of the lock assembly is available, while for the opposite direction of movement of the piston assembly acting on the actuator control piston is activated by the increasing pressure in the pressure medium supply and thereby the blocking effect is also canceled. By this design, only one control piston is required and the construction costs are correspondingly lower.

However, it is also possible for two control pistons acting on the actuating element to be provided, wherein a first control piston is fluid-connected to a first pressure-medium line leading to the bottom side of the cylinder space and a second control piston is fluid-connected to a second pressure-medium line leading to the piston rod-side cylinder space. By such an embodiment, both the retracting piston rod and extending piston rod is activated by the pressure increase in the respective pressure medium supply one of the control piston and thereby deactivates the lock assembly, whereby the movement of the piston unit is made possible.

The actuating element can also be designed as a threaded spindle or the locking sleeve concentrically comprehensive actuating ring, in particular as a sliding ring. This can be adjustable in the direction of the cylinder longitudinal axis and have an inner cone, which forms the actuating surface and in axial adjustment one, or in particular two or more locking body in the radial direction in Sperrausnehmungen on the threaded spindle and the locking sleeve urges. In an embodiment with at least two locking bodies which can simultaneously engage with the locking recesses, the contact forces to be transmitted by a respective locking body are reduced according to their number. Due to the axially adjustable or rotatable sliding ring can be actuated with only one actuating element more locking body. However, it is also possible in previously described embodiments with rectilinear locking slide or rotary body several, each to provide one of several locking elements acting actuators, whereby the structural complexity and the space required for the lock assembly increases. By using a plurality of blocking bodies and corresponding reduction of the contact forces to be transmitted, the blocking bodies and the actuating elements can be made smaller be, whereby the size can still be kept small anyway. The inner cone is not limited to a rotationally symmetrical shape, but may also have other to the cylinder longitudinal axis oblique surface portions as the actuating surface. The sliding ring can also be considered as an embodiment of a locking slide, which is why the possible embodiments and advantageous embodiments of the actuating surface described with reference to the embodiment with a locking slide are also possible with an actuating element in the form of a sliding ring.

Likewise, the actuating ring can be rotatably mounted concentrically to the threaded spindle and the actuating surfaces partially helical or helical, whereby upon rotation of the actuating ring of the locking body and the locking body are urged into the locking recesses of the threaded spindle or the locking sleeve.

Actuating, Aufsteuerkolben and Einsteuerelement are preferably summarized in the end housing that can also be used to accommodate additional valves to control the cylinder functions.

Advantageous embodiments of the invention will be explained in more detail below with reference to the embodiments illustrated in the drawings.

Fig. 1

einen Längsschnitt durch einen erfindungsgemäßen Linearverstellantrieb in Form einer Zylinder-Kolben-Einheit;

Fig. 2

einen Querschnitt durch das Endgehäuse eines Linearverstellantriebs gemäß Linie II-II in Fig. 1;

Fig. 3

einen Querschnitt durch das Endgehäuse eines Linearverstellantriebs gemäß Linie III-III in Fig. 2;

Fig. 4

ein Hydraulikschema eines Linearverstellantriebs gemäß der Ausführung nach Fig. 3;

Fig. 5

einen Querschnitt durch das Endgehäuse einer weiteren Ausführungsform eines Linearverstellantriebs;

Fig. 6

ein Hydraulikschema eines Linearverstellantriebs gemäß der Ausführung nach Fig. 5;

Fig. 7

mehrere Ausführungsformen von Sperrkörpern und Sperranordnungen eines erfindungsgemäßen Linearverstellantriebs (7a bis 7d);

Fig. 8

einen Schnitt durch eine weitere Ausführungsform der Sperranordnung für einen Linearverstellantrieb, mit einem Betätigungselement in Form eines axial verstellbaren Schieberings;

Fig. 9

eine weitere Ausführungsform der Sperranordnung mit einem Betätigungselement in Form eines Drehkörpers.

Each shows in a simplified schematic representation:

Fig. 1

a longitudinal section through a Linearverstellantrieb invention in the form of a cylinder-piston unit;

Fig. 2

a cross section through the end housing of a Linearverstellantriebs according to line II-II in Fig. 1 ;

Fig. 3

a cross section through the end housing of a Linearverstellantriebs according to line III-III in Fig. 2 ;

Fig. 4

a hydraulic schematic of a Linearverstellantriebs according to the embodiment according to Fig. 3 ;

Fig. 5

a cross section through the end housing of another embodiment of a Linearverstellantriebs;

Fig. 6

a hydraulic schematic of a Linearverstellantriebs according to the embodiment according to Fig. 5 ;

Fig. 7

several embodiments of locking bodies and locking arrangements of a Linearverstellantriebs (7a to 7d) according to the invention;

Fig. 8

a section through a further embodiment of the locking arrangement for a Linearverstellantrieb, with an actuating element in the form of an axially adjustable sliding ring;

Fig. 9

a further embodiment of the locking arrangement with an actuating element in the form of a rotary body.

By way of introduction, it should be noted that in the differently described embodiments, the same parts are provided with the same reference numerals or the same component names, wherein the disclosures contained in the entire description can be mutatis mutandis to the same parts with the same reference numerals or component names. Also, the location information chosen in the description, such as top, bottom, side, etc. related to the immediately described and illustrated figure and these are mutatis mutandis to transfer to a new position on a change in position. Furthermore, individual features or combinations of features from the illustrated and described, different embodiments may represent for themselves, inventive or inventive solutions.

All statements on ranges of values in objective description are to be understood as including any and all sub-ranges thereof, eg the indication 1 to 10 should be understood to include all sub-ranges, starting from the lower limit 1 and the upper limit 10 ie, all subareas begin with a lower limit of 1 or greater and end at an upper limit of 10 or less, eg 2 to 9 or 2 to 4 or 3 to 7.

In Fig. 1 is a sectional view of a Linearverstellantriebs 1 in the form of an acted upon with a pressure medium, double-acting cylinder-piston unit 2 shown. This is equipped with a locking arrangement 3, with a mechanical fixation in final and intermediate positions of an adjustment is achieved. The cylinder-piston unit 2 consists of a cylinder body 4, formed by a tube 5, which has a Zylinderendadapter 7 or guide piece at a front end 6. At an opposite end 8 of the cylinder jacket 4 is fixedly connected to the tube 5, for example screwed, welded, etc., an end housing 9 is arranged. The end housing 9 is provided with a bearing head 10, in which, for example, a radial spherical plain bearing 11 is arranged for receiving a bearing pin 12.

The arranged at the front end 6 Zylinderendadapter 7 is penetrated in a bore 13 by a tubular piston rod 14 which is fixedly connected to a further bearing head 15, for example, welded. Also, this bearing head 15 has, for example, a further radial spherical plain bearing 16 for receiving a bearing pin 17. Thus, the Linearverstellantrieb 1 can be used to adjust or mutual fixation of two relatively linearly movable device parts within a given adjustment.

The in a bounded by the cylinder jacket 4, cylinder end adapter 7 and end housing 9 pressure chamber 18 extending tubular piston rod 14 is immovably connected to an annular piston 19. The piston 19 and the associated piston rod 14 together form a piston assembly 20. The piston 19 has on its outer circumference a plurality of sealing and guide elements 21 and forms a pressure-tight subdivision of the pressure chamber 18 and thus the double-acting design of the cylinder-piston unit. 2 ,

In the end housing 9 arranged in a concentric with a cylindrical longitudinal axis 22, stepped stepped bore 23 a bearing assembly 26 formed from radial bearings 24 and thrust bearings 26 for rotatably supporting a bearing extension 27 of a piston crown side extending into the tubular piston rod 14 threaded spindle 28 is provided. The radial bearing 24 is formed in the illustrated embodiment by two plain bearing rings, while the thrust bearing 25 is formed by two acting in opposite directions needle bearing units.

The threaded spindle 28 has an external thread 29, for example in the form of a trapezoidal thread. The external thread 29 of the threaded spindle 28 is in engagement with an internal thread 30, which is arranged in a concentric to the cylinder longitudinal axis 22 opening 31 in the annular piston 19. The external thread 29 and the internal thread 30 are, as already mentioned, preferably a trapezoidal thread, which is designed to run more frequently and has a non-self-locking thread pitch, whereby a drive connection between the piston assembly 20 and the threaded spindle 28 is achieved. If the piston 19 is moved linearly by being acted upon by a pressure medium in the cylinder body 4 and this is secured against rotation, takes place via the engagement of the external thread 29 and internal thread 30, a rotational movement of the threaded spindle 28 according to the predetermined ratios of the pitch of the thread and the distance covered the piston assembly 20th

For the corresponding embodiment of the bearing assembly 26, the bearing extension 27 of the threaded spindle 28 consists of an integrally formed on the threaded spindle 28 cylindrical bearing pin 32 and a concentrically comprehensive and with the bearing pin 32 rotatably connected locking sleeve 33 for the locking arrangement. 3

In the illustrated embodiment, the thrust bearings 25 act in the form of needle bearings on the two end face surfaces of the locking sleeve 33, while the radial bearings 24 in the form of plain bearing rings lead the bearing extension 27 in the radial direction.

The end housing 9, in which the threaded spindle 28 is rotatably mounted on the bearing assembly 26 and in which the locking assembly 3 is arranged to block the rotational movement of the threaded spindle 28, further comprises all necessary for the operation of the Linearverstellantriebes 1 flow and connection channels for the application the cylinder-piston unit 2, and required for the immediate operation of the Linearverstellantriebs 1 internal control elements 34, for example in the form of valve cartridges.

The locking arrangement 3 for blocking the rotational movement of the threaded spindle 28 essentially comprises a locking element 35 arranged in the end housing 9 in the form of a rotationally symmetrical locking body 36 with a rotational symmetry axis 37 approximately parallel to the cylinder longitudinal axis 22. This locking body 36, for example in the form of a ball, is in one Movement space 38 movably mounted in the interior of the end housing 9 and projects in the blocking position of the locking arrangement 3 in a trained on the periphery 39 of the locking sleeve 33 or the bearing extension 27 of the threaded spindle 28 locking recess 40, which corresponds to a kugelkalottenförmigen depression in the illustrated embodiment. To fix the locking body 36 in the blocking position, in which it protrudes into the locking recess 40 on the locking sleeve 33 and the threaded spindle 28, the movement space 38 by means of an actuating element 41, in the illustrated embodiment in the form of a locking slide 42, in a cylinder longitudinal axis 22nd right-angled radial direction 43 changeable. The actuating element 41, here the locking slide 42, for this purpose has an actuating surface 44 which limits the movement space 38 in the radial direction 43 and the movement space 38 is shortened when adjusting the locking slide 42 in the blocking position so that the locking body 36 is pressed into the locking recess 40 and in the release position of the actuating element 41, the movement space 38 in the radial direction is increased so that the locking body 36 can emerge completely from the locking recess 40, whereby the rotational locking of the threaded spindle 28 is released. In the execution according to Fig. 1 is the locking assembly 3 in blocking position 45, in which the locking body 36 protrudes into one of a plurality of locking recesses 40, shown.

Fig. 2 shows a section through the end housing 9 along the line II - II in Fig. 1 , The locking arrangement 3 is in Fig. 2 unlocked by the locking slide 42 is displaced in the direction 46 to the right and from the actuating surface 44 in the radial direction 43 enlarged movement space 38 is released for the locking body 36. In the illustrated release position 47 of the locking slide 42, the locking body 36 can come to rest entirely by the radially enlarged movement space 38 outside the periphery 39 of the locking sleeve 33, whereby it no longer protrudes into the locking recess 40. The rotational movement of the threaded spindle 28 with the locking sleeve 33 is thus not blocked in the illustrated release position 47 and the piston assembly 20 can perform a retraction or extension movement by applying pressure medium. In the case of a right-handed external thread 29 of the threaded spindle 28, a retraction of the piston rod 14 causes a left-hand rotation 48 of the threaded spindle 28 with the locking sleeve 33; an extension of the piston rod 14, however, causes a clockwise rotation 49 of the threaded spindle 28th

As Fig. 2 is further removed, the actuating surface 44 with a helix angle 50 with respect to a Tangentialtläche 51 to the periphery 39 of the threaded spindle 28 and the Locking sleeve 33 aligned in the region of the locking body 36. A movement of the locking slide 42 in the direction of displacement 46 is thereby converted according to the principle of an inclined plane in a displacement of the locking body 36 in the radial direction 43. The displacement direction 46 of the locking slide 42 can run parallel to the tangential plane 51, in particular as in Fig. 2 shown, also at right angles to a radial plane 52 extend through the cylinder longitudinal axis 22.

The actuating surface 44 is also arranged obliquely with respect to the displacement direction 46 of the locking slide 42 and that by a pitch angle 53, which corresponds to the helix angle 50 in the illustrated embodiment, since the displacement direction 46 is oriented parallel to the tangential plane 51. In this case, an actuating surface 44 which is aligned parallel to the displacement direction 46 would cause no displacement of the locking body 36 in the radial direction 43, which is why a pitch angle 53 is mandatory in this case. If the displacement direction 46 does not extend parallel to the tangential plane 51, the locking slide 42 itself has a component of movement in the radial direction 43 when moving in the displacement direction 46, for which reason the actuating surface 44 with the tangential plane 51 would not have to assume a helix angle 50 in this case.

All conceivable orientations and embodiments of the actuating element 41, in particular of the locking slide 42 has in common that the trained on this actuating surface 44 when moving the locking slide 42, the movement space 38 for the locking body 36 in the radial direction 43 increases or decreases, so also the point of contact between the locking body 36 and the actuating surface 44 changes its distance from the cylinder longitudinal axis 22. In the illustrated embodiment, for example, by the linear adjustment of the locking slide 42, but there are also possible embodiments in which the actuating element 41 in the form of a rotary body performs a rotational movement and thereby change the movement space 38 of the locking body 36 with a formed on this rotary body actuating surface 44.

In order to prevent the locking body 36 in locking position 45, in which it protrudes into the locking recess 40, is carried in the tangential direction by the rotational movement of the locking sleeve 33 and the threaded spindle 28 and thereby allows the rotational movement, its movement in the tangential direction in the end housing 9 rigidly arranged stop elements 54th blocked. These are in Fig. 2 formed by inner walls 55 and 55 'of the solid end housing 9 itself and thereby suitable for receiving even the largest contact forces from the locking body 36. The inner walls 55 may be flat or be formed by a portion of a bore inner wall in the end housing 9. Likewise, the stop element 54 may be designed as in the end housing 9, in particular releasably, inserted additional part, which can be replaced in the event of wear.

Fig. 2 further shows a spring element 56, for example in the form of a compression spring 57 which exerts a spring force in the direction of the blocking position 45 on the locking slide 42. In the illustrated embodiment, this is a spring force to the left, which shifts the locking slide 42 in the direction of displacement 46 to the left, as long as no control forces acting on the locking slide 42, which are greater than the spring force exerted by the spring element 56 and the locking slide 42 to the right in the direction of move shown release position 47.

Fig. 3 shows a section through the end housing 9 along line III - III in Fig. 2 , This sectional view shows the locking slide 42 in blocking position 45, ie in the direction of displacement 46 in the left position. The spring element 56 comprises in this embodiment, two concentrically arranged compression springs 57 which exert on the locking slide 42 in the direction of the blocking position 45 to the left a spring force. In order to spend the locking slide 42 in the release position 47, two control elements 58 and 58 'are arranged in this embodiment, which can exert a control force to the right on the locking slide 42 and thereby overcome the spring force of the spring elements 56, whereby the locking slide 42 after right and thus can be spent in release position 47. The controls 58, 58 'here include actuated by pressure medium Aufsteuerkolben 59, 59', which are guided sealed in cylinder bores in the end housing 9 and respectively by pressurizing from the left to perform a shift to the right and thereby the locking slide 42 against the action of the compression springs 57 to the right spend in the release position 47, whereby the movement space 38 is increased for the locking body 36 so that it no longer engages in the locking recesses 40 and a rotational movement of the threaded spindle 28 is possible.

Fig. 4 shows the operation of a Linearverstellantriebs invention 1 in the form of a cylinder-piston unit 2 based on a hydraulic scheme. The cylinder in the body 4 displaceable piston assembly 20 shares with its piston 19, the interior of the cylinder body 4 in a piston rod side cylinder chamber 60 and a piston bottom side cylinder chamber 61. As described above, causes a displacement of the piston assembly 20 in the cylinder body 4 by the threaded engagement rotational movement of the threaded spindle 28 and a rotationally fixed with this connected locking sleeve 33, wherein the rotational movement is blocked in the illustrated blocking position 45 by the standing in engagement with the locking recess 40 locking body 36. The locking position corresponds to the rest position of the locking slide 42 caused by the spring element 56, in which the latter pushes the locking body 36 into the locking recess 40 with its actuating surface 44. In order to enable a movement of the piston assembly 20 in the cylinder body 4, the locking slide 42 must be moved out of the blocking position 45 against the action of the spring force of the spring element 56 in the release position 47. This is done by activation of one of the two control pistons 59 and 59 'by pressure medium.

To effect starting from a blocked state of the Linearverstellantriebs 1, for example, an extension of the piston rod 14, on the one hand the piston bottom side cylinder chamber 61 must be acted upon with pressure medium and on the other hand, the locking slide 42 are brought into release position 47. For this purpose, a first control line 64 is branched off at a first pressure-medium line 63 leading from the first pressure connection 62 to the piston-bottom-side cylinder space 61, which transfers the fluid pressure existing in the first pressure-medium line 63 to the control piston 59 '. If, for example, by means of a 4/2-way valve at the first pressure port 62, a high pressure is applied; this is transmitted via the first control line 64 to the Aufsteuerkolben 59 'whereby this against the spring force of the spring element 56, the locking slide 42 spares to the left in the release position 47 whereby the fixation of the locking body 36 in the locking recess 40 of the locking sleeve 33 is released and the piston assembly 20th is increased to the left when enlarging the piston bottom side cylinder chamber 61 and the piston rod 14 extends, since the threaded spindle 28 is no longer blocked in this state.

Similarly, in order to effect retraction of the piston rod 14 via a second pressure port 65 and a leading from this to the piston rod side cylinder chamber 60 second pressure medium line 66 under high pressure pressure medium supplied. In order to allow the retraction movement of the piston rod 14, branches from the second pressure medium line 66 a second control line 67 from which leads to the second control piston 59. If the second pressure connection 65 is acted upon by a non-illustrated 4-2-way valve, the pressure occurring in the second control line 67 and acting on the control piston 59 causes a displacement of the locking slide 42 against the spring force of the spring element 56 to the left. The thus enlarged movement space 38 for the locking body 36 thereby allows again the radial leakage of the locking body 36 from the locking recess 40 on the locking sleeve 33 whereby the free rotation of the threaded spindle 28 is made possible again and the piston assembly 20 by increasing the piston rod side cylinder chamber 60 a shift to the right Thus, a retraction of the piston rod 14 can perform.

In the pressure medium lines 63 and 66, further valve elements 68 may be arranged, which have the effect of a control member 34. Thus, the valve element 68 may serve as an overload protection, for example, which allows a controlled, braked retraction of the piston rod 14 when exceeding a force acting on the piston rod 14 or acts as a lowering brake valve, the too high retraction speed by throttling the normal retraction of the piston rod 14 Pressure fluid drain to the pressure port 62 avoids.

Fig. 5 shows a cross section through the end housing 9 of another embodiment of a Linearverstellantriebs invention 1 in the form of a cylinder-piston unit 2 with a locking arrangement 3 in blocking position 45. In this blocking position 45 of the locking body 36 projects, here also in the form of a ball 69 in a locking recess 40 of the locking sleeve 33 and is fixed in the radial direction by the actuating surface 44 of the locking slide 42. The locking slide 42 is held by the spring element 56 in the form of compression springs 57 in the locked position. To release the rotational locking of the threaded spindle 28 and thus also the longitudinal locking of the cylinder-piston unit 2, the locking slide 42 is displaced against the action of the spring element 56 in the release position 47 by means of the control piston 59, which is acted upon by high-pressure fluid the available for the locking body 36 in the form of the ball 69 movement space 38 is increased and the ball 69 can escape in the radial direction 43 of the locking recess 40 and thereby the rotation blocking is released. For reasons of ease of manufacture of the gate valve 42 has a circular cross-section and is in a cylindrical Bore 70 is guided in the end housing 9. A lid 71 which closes the bore serves at the same time to support the spring element 56.

The movement space 38 for the ball 69 is formed in a tangential direction, here in the case of a clockwise rotation 49 by a stop element 54 in the form of the inner wall 55 in the end housing 9. Acts on the piston assembly 20, a load that would cause a clockwise rotation of the locking sleeve 33, thus the locking slide 42 in blocking position 45, the movement space 38 through the inner wall 55 and the actuating surface 44 of the locking slide 42 is reduced so that the ball 69 in the locking recess 40th the locking sleeve 33 is fixed and the rotational movement is blocked to the right.

In the second tangential direction, ie in the case of a left-hand rotation of the locking sleeve 33, a spring-mounted insertion element 72 is arranged instead of a fixed stop element 54, which causes the ball 69 to tangentially despite a blocking slide 45 located in the blocking position 42 when the blocking sleeve 33 is turned can be moved to the left and the movement space 38 so far increased by the resilient yielding of the Einsteuerelementes 72 in the tangential direction that the locking body 36 in the form of the ball 69 despite blocking slide 42 in locking position 45 can escape completely from the Sperraushehmung 40 and thereby a Rotary movement of the locking sleeve 33 is possible.

The Einsteuerelement 72 comprises a approximately tangentially in the direction of 73 slidably mounted in the end housing 9 Einsteuerkolben 74 which is pressed by a spring element 75 against the tangential direction 73 - in this case to the right. The Einsteuerelement 72 thereby causes a freewheeling function by a left turn of the locking sleeve 33 and thus a longitudinal displacement of the piston assembly 20 allows, but reversing the direction of movement of the piston assembly 20 a clockwise rotation by the support of the locking body 36 on the stop element 54th is blocked immediately in the form of the inner wall 55, as long as the gate valve 42 is not actively spent, for example by means of the control piston 59 from the blocking position 45 in the not illustrated release position 47. Thus, for example, an extension of the piston rod 14 take place by the piston bottom side cylinder chamber 61 is subjected to pressure medium and the locking assembly 3 due to the freewheeling function by the Einsteuerelement 72 a the extension of the piston rod 14 corresponding rotational movement of the locking sleeve 33 allows while, for example, for the retraction of the piston rod 14 in addition to the loading of the piston assembly 20 via the piston rod side cylinder chamber 60 at the same time the open-ended piston 59 must be pressurized to cancel the blocking function of the lock assembly 3 and allow the retraction of the piston rod 14.

The longitudinal section through the gate valve 42 in Fig. 5 shows further that the actuating surface 44 along the direction of displacement 46 has different pitches so different pitch 53 with respect to the direction of displacement 46 of the locking slide 42 and that in the blocking position 45, the actuating surface 44 has a pronounced fixing portion 76 in which the actuating surface 44 to the surface of the locking body 36, here the ball 69 is adjusted.

In the in Fig. 5 illustrated embodiment corresponds to a radial depth 77 of the locking recess 40 is about 0.3 times the maximum diameter 78 of the locking body 36, whereby too deep penetration and thus a self-locking blocking body 36 in the locking recess 40 of the locking sleeve 33 is avoided. A compact size of the end housing 9 can be achieved if, as in the illustrated embodiment, the maximum diameter 78 of the locking body 36 about 0.2 times, but at most 0.3 times the threaded spindle diameter or the lock sleeve diameter 79 corresponds.

Fig. 6 shows a hydraulic diagram for a Linearverstellantrieb 1 in the form of a cylinder-piston unit 2 with a locking arrangement 3 according to the basis of Fig. 5 described embodiment. Since the operation of this hydraulic scheme according Fig. 6 largely with the operation of the hydraulic scheme according to Fig. 4 is to be referred to the explanatory notes at this point Fig. 4 referenced below and are only the differences Fig. 4 explained.

Since the locking arrangement 3 in this embodiment has a freewheeling function for one direction of rotation of the threaded spindle 28, the rotational blocking must be effected by displacement of the locking slide 42 in the release position 47 only for the oppositely oriented direction of rotation of the threaded spindle 28. This displacement of the locking slide 42 takes place in accordance with the example Fig. 6 only for the retraction movement of the piston rod 14, by the second pressure medium line 66 leading to the piston rod-side cylinder chamber 60, a control line 67 branches off, which activates the Aufsteuerkolben 59 in the presence of a high pressure at the second pressure port 65 and thereby shifts the locking slide 42 in the release position 47.

For the extension of the piston rod 14, pressure medium 62 is supplied via the first pressure port 62 and the first pressure medium line 63 to the piston bottom side cylinder chamber 61 and due to the freewheeling function of the locking arrangement 3, the piston assembly 20 can perform a displacement and accordingly the threaded spindle 28 perform the associated rotation, without the locking slide 42 would have to be spent in the release position 47.

Such a construction of the Linearverstellantriebs 1 can be used in many applications, for example in car transporters, lifts, fall protection devices, support elements for excavation work, etc. and is characterized by a simpler and more cost-effective production.

In the Fig. 7a to 7d further possible embodiments of the invention Linearverstellantriebs 1 are shown simplified.

Fig. 7a shows a threaded spindle 28 with a locking sleeve 33, in which the locking body 36 is formed by a ball 69 which is pressed by the locking slide 42 into the locking recess 40. In this embodiment, the locking sleeve 33 has a frusto-conical surface and the axis of rotational symmetry 37 of the locking body 36 is inclined by an inclination angle 80 relative to the cylinder longitudinal axis 22.

In Fig. 7b the blocking body 36 is formed by a circular cylinder 81, whose rotational symmetry axis 37 is aligned parallel to the cylinder longitudinal axis 22 in the illustrated embodiment. However, it is similar here as in Fig. 7a possible that the rotational symmetry axis 37 of the circular cylinder 81 occupies an inclination angle 80 to the cylinder longitudinal axis 22. The Spemausnehmungen 40 on the locking sleeve 33 are circular cylinder segment shaped adapted to the outer surface of the circular cylinder 81. The production of the actuating surface 44 can be done using a circular cylinder 81 as a locking body 36 by means of a simple end mill, while the use of a locking body 36 in the form of a ball 69, a finger milling cutter with spherical tip is used.

Fig. 7c shows an embodiment of a locking arrangement 3 with a locking body 36 in the form of a circular truncated cone 82 and with locking recesses 40 on the locking sleeve 33 which are circular cone segment-shaped. The rotational symmetry axis 37 of the circular truncated cone 82 extends in this illustrated embodiment at an inclination angle to the cylinder longitudinal axis 22, but may also be aligned parallel to the cylinder longitudinal axis 22.

Fig. 7d shows the use of a barrel-shaped locking body 36 so a rotationally symmetric body whose final diameter is smaller than the center diameter. The locking body 36 thereby has a spherical surface and the locking recesses 40 on the locking sleeve 33 are matching barrel-shaped concave, whereby a point load between locking body and locking recess with resulting high surface pressures and higher wear is avoided. It is also possible that in longitudinal section through the cylinder longitudinal axis 22, the locking sleeve 33 has a convex contour and the locking body 36 has a matching concave contour.

In Fig. 8 a further embodiment of a locking arrangement 3 for a linear drive 1 is shown, wherein the actuating element 41 is formed by an actuating ring 83 which comprises the threaded spindle 28 and the locking sleeve 33 concentrically. The actuating ring 83 is mounted axially and concentrically to the cylinder longitudinal axis 22 and can therefore also be referred to as a Schiebring 84, which thus also represents an embodiment of a locking slide 42.

The radial adjustment of two diametrically opposed to the cylinder longitudinal axis 22 arranged blocking bodies 36 takes place through an inner cone 85 which pushes in the blocking position 45, the locking body 36 in locking recesses 40 of the locking sleeve 33 and thereby blocks their rotational movement until the sliding ring 84 is moved in the release position and As a result, the movement space 38 is enlarged in the radial direction to the outside and a leakage of the locking body 36 is made possible from the locking recesses 40.

Fig. 9 shows an embodiment of a locking arrangement in which the actuating element 41 is formed as a rotary body 86 which is rotatably mounted in the end housing 5 and the peripheral surface 87 forms the actuating surface 44, which changes the movement space 38 in the radial direction upon rotation of the rotary body 86. The circumferential surface has with respect to the axis of rotation of the rotary body 86 variable radii.

The rotation of the piston assembly 20, which is required for the transmission of torque between the threaded spindle 28 and the piston rod 14 can be realized by means of the bearing heads 10, 15 and bearing pins 12, 17 of a device in which the Linearverstellantrieb is used; Alternatively, however, may also be formed an internal anti-rotation device for receiving the force acting on the piston unit 20 torque. For example, the piston rod 14 may be e.g. have diametrically opposed, longitudinally extending guide surfaces and the implementation of the piston rod 14 through the Zylinderendadapters 7 is formed according to the cross-sectional shape of the piston rod 14 and thus forms a guide arrangement by which the piston rod 14 against the cylinder body 4 is secured against rotation and thus the resulting in the threaded connection torque is recorded.

The embodiments show possible embodiments of the Linearverstellantriebs, which should be noted at this point that the invention is not limited to the specifically illustrated embodiments of the same, but also various combinations of the individual embodiments are mutually possible and this variation possibility due to the teaching of technical action by representational Invention in the skill of those skilled in this technical field. So are all conceivable embodiments, which are possible by combinations of individual details of the illustrated and described embodiment variant, includes the scope of protection.

For the sake of order, it should finally be pointed out that, for a better understanding of the construction of the linear adjustment drive, this or its components have been shown partly unevenly and / or enlarged and / or reduced in size.

The problem underlying the independent inventive solutions can be taken from the description.

Above all, the individual in the Fig. 1 . 2 . 3, 4 ; 5 ; 6 ; 7a to 7d ; 8th; 9 shown embodiments form the subject of independent solutions according to the invention. The relevant objects and solutions according to the invention can be found in the detailed descriptions of these figures.

REFERENCE NUMBERS

1 Linearverstellantrieb 36 blocking body 2 Cylinder-piston unit 37 Rotational symmetry axis 3 lock assembly 38 movement space 4 cylinder body 39 scope 5 pipe 40 locking recess 6 The End 41 actuator 7 Zylinderendadapter 42 blocking slide 8th The End 43 radial direction 9 backshell 44 actuating surface 10 bearing head 45 blocking position 11 Radial spherical plain bearings 46 displacement direction 12 bearing bolt 47 release position 13 drilling 48 turn left 14 piston rod 49 right turn 15 bearing head 50 helix angle 16 Radial spherical plain bearings 51 tangent 17 bearing bolt 52 radial plane 18 pressure chamber 53 lead angle 19 piston 54 stop element 20 piston assembly 55 inner wall 21 Sealing and guide element 56 spring element 22 cylinder longitudinal axis 57 compression spring 23 drilling 58 control 24 radial bearings 59 Opening piston 25 axial bearing 60 piston rod side cylinder space 26 bearing arrangement 61 piston bottom side cylinder space 27 Bearing extension 62 pressure connection 28 screw 63 Pressure medium line 29 external thread 64 control line 30 inner thread 65 pressure connection 31 breakthrough 66 Pressure medium line 32 pivot 67 control line 33 locking sleeve 68 valve element 34 regulating element 69 Bullet 35 blocking element 70 drilling 71 cover 72 A control element 73 tangential 74 A control piston 75 spring element 76 fixing 77 depth 78 Maximum diameter 79 Locking sleeve diameter 80 tilt angle 81 circular cylinder 82 Circular truncated cone 83 actuating ring 84 sliding ring 85 inner cone 86 rotating body 87 peripheral surface

Claims (37)

Linearverstellantrieb (1), in particular a pressurizable medium, double-acting cylinder-piston unit (2), comprising a cylinder body (4), in the interior of the cylinder body (4) along a cylinder longitudinal axis (22) adjustable, non-rotating piston assembly (20) , a threaded spindle (28) extending parallel to the cylinder longitudinal axis (22), in particular in the cylinder longitudinal axis (22), projecting into the piston arrangement (20) on the piston bottom side, having an external thread (29) with an internal thread (39) in the piston arrangement (20). cooperates, wherein the threaded spindle (28) is rotatably mounted in an end housing (9) of the cylinder body (4), and in the end housing (9) arranged locking element (35) in the locked position in at least one on the circumference of the threaded spindle (28) or on the circumference of a locking sleeve (33) connected to this locking recess (40) protrudes; characterized in that the blocking element (35) is formed by a rotationally symmetrical blocking body (36) with an axis of rotation (22) approximately parallel or only slightly inclined rotational symmetry axis (37) and a blocking body (36) receiving movement space (38) is formed, of an actuating surface (44) of a between a release position (47) and a locking position (45) adjustably mounted in the end housing (9) mounted actuating element (41) relative to the cylinder longitudinal axis (22) in the radial direction (43) is variable. Linearverstellantrieb (1) according to claim 1, characterized in that the rotational symmetry axis (37) of the locking body (36) to the cylinder longitudinal axis (22) has an inclination angle (80) of at most 15 °. Linearverstellantrieb (1) according to claim 1 or 2, characterized in that the actuating element (41) is designed as a rotatable in the end housing (9) mounted rotary body (86). Linearverstellantrieb (1) according to claim 1 or 2, characterized in that the actuating element (41) as a straight line in the end housing (9) guided locking slide (42) is formed. Linearverstellantrieb (1) according to one of claims 1 to 4, characterized in that the actuating surface (44) of the actuating element (42) has a helix angle (50) to a tangential plane (51) on the circumference (39) of the threaded spindle (28) or the locking sleeve (33) in the region of the locking body (36). Linearverstellantrieb (1) according to claim 4 or 5, characterized in that a displacement direction (46) of the locking slide (42) parallel to a tangential plane (51) on the circumference (39) of the threaded spindle (28) and the locking sleeve (33) , Linearverstellantrieb (1) according to one of claims 4 to 6, characterized in that the displacement direction (46) of the locking slide (42) at right angles to a radial plane (52) through the cylinder longitudinal axis (22). Linearverstellantrieb (1) according to one of claims 1 to 7, characterized in that on the actuating element (41) in the direction of the locking position (45) acting spring element (56) is provided. Linearverstellantrieb (1) according to claim 8, characterized in that the spring element (56) by two concentric compression springs (57) is formed. Linearverstellantrieb (1) according to one of claims 4 to 9, characterized in that the locking slide (42) is arranged in a locking slide guide with a circular cross-section. Linearverstellantrieb (1) according to one of claims 4 to 10, characterized in that the actuating surface (44) relative to the displacement direction (46) of the locking slide (42) by a pitch angle (53) is inclined. Linearverstellantrieb (1) according to claim 11, characterized in that the pitch angle (53) is selected smaller than 30 °. Linearverstellantrieb (1) according to claim 11 or 12, characterized in that the actuating surface (44), viewed over the adjustment of the locking slide (42), different pitch angle (53) relative to the displacement direction (46). Linearverstellantrieb (1) according to one of claims 1 to 13, characterized in that the actuating surface (44) has a fixing portion (76) which is largely adapted to the cross section of the locking body (37). Linearverstellantrieb (1) according to claim 14, characterized in that the actuating surface (44) in the fixing section (76) has a pitch angle (53) less than 10 °, in particular less than 5 °. Linearverstellantrieb (1) according to one of claims 1 to 15, characterized in that the movement space (38) for the locking body (38) is limited at least in a tangential direction by a rigid stop element (54) in the end housing (9). Linearverstellantrieb (1) according to claim 16, characterized in that the stop element (54) is formed by a portion of a bore inner wall in the end housing (9). Linearverstellantrieb (1) according to claim 16, characterized in that the stop element (54) by a flat inner wall (55) in the end housing (9) is formed. Linearverstellantrieb (1) according to one of claims 16 to 18, characterized in that the stop element (54) parallel to a radial plane (52) through the cylinder longitudinal axis (22). Linearverstellantrieb (1) according to one of claims 1 to 19, characterized in that the movement space (38) for the locking body (36) in a tangential direction (73) by a spring-loaded, tangential yielding input element (72) is limited. Linearverstellantrieb (1) according to one of claims 1 to 20, characterized in that the locking body (36) as a ball (69) and the cooperating locking recess (40) is formed kugelkalottenförmig. Linearverstellantrieb (1) according to one of claims 1 to 20, characterized in that the locking body (36) as a circular cylinder (81) and the cooperating locking recess (40) is formed circular-cylindrical segment-shaped. Linearverstellantrieb (1) according to one of claims 1 to 20, characterized in that the locking body (36) as a circular truncated cone (82) and the cooperating Sperrausnehmung (40) is formed circular-cone segment-shaped. Linearverstellantrieb (1) according to one of claims 1 to 20, characterized in that the locking body (36) barrel-shaped and the cooperating Sperrausnehmung (40) is formed barrel-shaped concave. Linearverstellantrieb (1) according to one of claims 1 to 24, characterized in that a maximum diameter (78) of the locking body (36) corresponds to a maximum of 0.3 times a threaded spindle diameter or a Sperrhülsendurchmessers (79). Linearverstellantrieb (1) according to one of claims 1 to 25, characterized in that a radial depth (77) of the locking recess (40) corresponds to a maximum of 0.4 times the maximum diameter (78) of the locking body (36). Linearverstellantrieb (1) according to one of claims 1 to 26, characterized in that the locking recess (40) has an effective radius between 1.0 times and a1.1 times a radius of the locking body (36). Linearverstellantrieb (1) according to one of claims 1 to 27, characterized in that the threaded spindle (28) or the locking sleeve (33) has at least six largely uniformly distributed on the outer circumference locking recesses (40). Linearverstellantrieb (1) according to one of claims 1 to 28, characterized in that the material hardness of the blocking body (36) is selected to be greater than the material hardness of the surface of the actuating element (41). Linearverstellantrieb (1) according to one of claims 1 to 29, characterized in that a the actuating element (41) from the locking position (45) in the release position (47) adjusting control element (58) is provided. Linearverstellantrieb (1) according to claim 30, characterized in that the control element (58) by a fluid-actuated control piston (59) is formed. Linearverstellantrieb (1) according to claim 31, characterized in that an adjustment direction of the Aufsteuerkolbens (59) parallel to the displacement direction (46) of the locking slide (42). Linearverstellantrieb (1) according to claim 31 or 32, characterized in that on the actuating element (41) acting on the control piston (59) leading to the piston bottom side cylinder space (61) first pressure medium line (63) or with a piston rod side cylinder chamber (60) leading the second pressure medium line (66) is fluid-connected and the movement space (38) for the blocking body (36) in a tangential direction (73), which corresponds to the not by the control piston (59) unlockable direction of movement of the piston assembly (20), by a spring-loaded, tangentially yielding Einsteuerelement (72) is limited. Linearverstellantrieb (1) according to claim 31 or 32, characterized in that two on the actuating element (41) acting on Aufsteuerkolben (59, 59 ') are provided, wherein a first Aufsteuerkolben (59) with a piston bottom side to the cylinder chamber (61) leading first pressure medium line (63) is fluid-connected and a second control piston (59 ') with a piston rod-side cylinder chamber (60) leading to the second pressure medium line (66) is fluidly connected. Linearverstellantrieb, according to one of claims 1 to 34, characterized in that the actuating element (41) as a threaded spindle (28) and the locking sleeve (33) comprehensive actuating ring (83) is formed. Linearverstellantrieb, according to claim 35, characterized in that the actuating ring (83) as a locking slide (42) in the form of a concentric with the threaded spindle (28) axially displaceable sliding ring (84) is formed with a conical actuating surface (44). Linearverstellantrieb (1) according to one of claims 31 to 35, characterized in that the actuating element (41), Aufsteuerkolben (59) and Einsteuerelement (72) are combined in the end housing (9).

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