EP2039944B1 - Actionneur linéaire, en particulier unité cylindre-piston dotée d'un dispositif de verrouillage - Google Patents

Actionneur linéaire, en particulier unité cylindre-piston dotée d'un dispositif de verrouillage Download PDF

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Publication number
EP2039944B1
EP2039944B1 EP20080005441 EP08005441A EP2039944B1 EP 2039944 B1 EP2039944 B1 EP 2039944B1 EP 20080005441 EP20080005441 EP 20080005441 EP 08005441 A EP08005441 A EP 08005441A EP 2039944 B1 EP2039944 B1 EP 2039944B1
Authority
EP
European Patent Office
Prior art keywords
locking
adjustment actuator
linear adjustment
cylinder
piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP20080005441
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German (de)
English (en)
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EP2039944A3 (fr
EP2039944A2 (fr
Inventor
Martin Brantner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Weber Hydraulik GmbH Austria
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Weber Hydraulik GmbH Austria
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Publication date
Application filed by Weber Hydraulik GmbH Austria filed Critical Weber Hydraulik GmbH Austria
Publication of EP2039944A2 publication Critical patent/EP2039944A2/fr
Publication of EP2039944A3 publication Critical patent/EP2039944A3/fr
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Publication of EP2039944B1 publication Critical patent/EP2039944B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/26—Locking mechanisms
    • F15B15/262—Locking mechanisms using friction, e.g. brake pads
    • F15B15/264—Screw mechanisms attached to the piston

Definitions

  • the invention relates to a Linearverstellantrieb as described in the preamble of claim 1.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the blocking 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the locking slide can be arranged in particular in a locking slide guide with a circular cross-section.
  • a locking slide guide with a circular cross-section.
  • other cross-sectional shapes for example, a rectangular cross-sectional shape of the locking slide guide may be formed.
  • 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 smaller than 10 °, in particular smaller 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.
  • 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.
  • 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.
  • 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 Einberichtelement.
  • the stop element 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 SperrausEnglishept 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.
  • 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.
  • 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, which this 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 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.
  • the threaded spindle or the locking sleeve has at least six equally distributed on the outer periphery locking recesses.
  • Linearverstellantriebs may be that the material hardness of the locking body is selected to be greater than the material hardness of the actuating element.
  • the locking slide is manually operated by a user
  • 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.
  • 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.
  • a fluid-operated control piston for example a hydraulically actuated control piston which is mounted in the end housing.
  • 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 Ein facedelement.
  • 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.
  • 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 SperrausEnglishept on the threaded spindle and the locking sleeve urges.
  • 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.
  • 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.
  • 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, Aufwinkolben and Ein interviewedelement are preferably summarized in the end housing that can also be used to accommodate additional valves to control the cylinder functions.
  • 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.
  • 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.
  • an end housing 9 is arranged at an opposite end 8 of the cylinder jacket 4 is fixedly connected to the tube 5, for example screwed, welded, etc.
  • 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.
  • the Linearverstellantrieb 1 can be used to adjust or mutual fixation of two relatively linearly movable device parts within a given adjustment.
  • 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 ,
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • Fig. 2 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.
  • 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.
  • stop elements 54th blocked.
  • 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.
  • 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.
  • 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.
  • the controls 58, 58 ' here include actuated by pressure medium Aufberichtkolben 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.
  • 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.
  • the locking slide 42 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.
  • 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 '.
  • second pressure medium line 66 under high pressure pressure medium supplied.
  • second control line 67 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.
  • valve elements 68 may be arranged, which have the effect of a control member 34.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 Ein Kunststoffiatas 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 Ein capitaelement 72 comprises a approximately tangentially in the direction of 73 slidably mounted in the end housing 9 Einberichtkolben 74 which is pressed by a spring element 75 against the tangential direction 73 - in this case to the right.
  • the Ein capitaelement 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.
  • 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 Ein whyelement 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.
  • 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.
  • 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 Aufberichtkolben 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.
  • pressure medium 62 is supplied via the first pressure port 62 and the first pressure medium line 63 to the piston bottom side cylinder space 61 and due to the freewheel 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the rotational symmetry axis 37 of the circular cylinder 81 occupies an inclination angle 80 to the cylinder longitudinal axis 22.
  • the Spemausnaturalept 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.
  • the locking sleeve 33 has a convex contour and the locking body 36 has a matching concave contour.
  • a further embodiment of a locking arrangement 3 for a linear drive 1 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.
  • 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.
  • 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.

Claims (37)

  1. Actionneur linéaire (1), en particulier un vérin à double effet (2), destiné à être sollicité par un fluide sous pression, comportant un corps de cylindre (4), un système de piston (20), mobile en translation à l'intérieur du corps de cylindre (4) le long d'un axe longitudinal (22) du cylindre et immobile en rotation, une broche filetée (28), qui s'étend parallèlement à l'axe longitudinal (22) du cylindre, en particulier dans ledit axe longitudinal (22), s'engage du côté du fond du piston dans le système de piston (20) et est muni d'un filetage extérieur (29) qui coopère avec un filetage intérieur (39) dans le système de piston (20), ladite broche filetée (28) étant montée rotative dans un carter d'extrémité (9) du corps de cylindre (4), ainsi qu'un élément de blocage (35), agencé dans le carter d'extrémité (9) et s'engageant, dans la position de blocage, dans au moins un évidement de blocage (40) disposé sur la périphérie extérieure de la broche filetée (28) ou sur la périphérie extérieure d'une gaine de blocage (33) reliée de manière solidaire en rotation à ladite broche filetée, caractérisé en ce que l'élément de blocage (35) est formé par un corps de blocage (36) à symétrie de révolution, avec un axe de symétrie de révolution (37) sensiblement parallèle à l'axe longitudinal (22) du cylindre ou seulement faiblement incliné par rapport à ce dernier, et dans le carter d'extrémité (9) est réalisé un espace de mouvement (38), qui reçoit le corps de blocage (36) et qui peut être modifié dans la direction radiale (43) par rapport à l'axe longitudinal (22) du cylindre par une surface d'actionnement (44) d'un élément d'actionnement (41), monté mobile dans le carter d'extrémité (9) entre une position de déblocage (47) et une position de blocage (45).
  2. Actionneur linéaire (1) selon la revendication 1, caractérisé en ce que l'axe de symétrie de révolution (37) du corps de blocage (36) forme avec l'axe longitudinal (22) du cylindre un angle d'inclinaison (80) de 15° maximum.
  3. Actionneur linéaire (1) selon la revendication 1 ou 2, caractérisé en ce que l'élément d'actionnement (41) est réalisé sous la forme d'un corps rotatif (86) monté rotatif dans le carter d'extrémité (9).
  4. Actionneur linéaire (1) selon la revendication 1 ou 2, caractérisé en ce que l'élément d'actionnement (41) est réalisé sous la forme d'un coulisseau de blocage (42) guidé de manière rectiligne dans le carter d'extrémité (9).
  5. Actionneur linéaire (1) selon l'une quelconque des revendications 1 à 4, caractérisé en ce que la surface d'actionnement (44) de l'élément d'actionnement (41) forme un angle d'inclinaison (50) avec un plan tangentiel (51) sur la périphérie (39) de la broche filetée (28) ou de la gaine de blocage (33) dans la zone du corps de blocage (36).
  6. Actionneur linéaire (1) selon la revendication 4 ou 5, caractérisé en ce qu'une direction de coulissement (46) du coulisseau de blocage (42) est parallèle à un plan tangentiel (51) sur la périphérie (39) de la broche filetée (28) ou de la gaine de blocage (33).
  7. Actionneur linéaire (1) selon l'une quelconque des revendications 4 à 6, caractérisé en ce que la direction de coulissement (46) du coulisseau de blocage (42) passe par l'axe longitudinal (22) du cylindre perpendiculairement par rapport à un plan radial (52).
  8. Actionneur linéaire (1) selon l'une quelconque des revendications 1 à 7, caractérisé en ce qu'il est prévu un élément à ressort (56) qui agit sur l'élément d'actionnement (41) dans la direction de la position de blocage (45).
  9. Actionneur linéaire (1) selon la revendication 8, caractérisé en ce que l'élément à ressort (56) est formé par deux ressorts de pression (57) concentriques.
  10. Actionneur linéaire (1) selon l'une quelconque des revendications 4 à 9, caractérisé en ce que le coulisseau de blocage (42) est disposé dans un guidage à section transversale circulaire.
  11. Actionneur linéaire (1) selon l'une quelconque des revendications 4 à 10, caractérisé en ce que la surface d'actionnement (44) est inclinée selon un angle de montée (53) par rapport à la direction de coulissement (46) du coulisseau de blocage (42).
  12. Actionneur linéaire (1) selon la revendication 11, caractérisé en ce que l'angle de montée (53) est choisi inférieur à 30°.
  13. Actionneur linéaire (1) selon la revendication 11 ou 12, caractérisé en ce que la surface d'actionnement (44), considérée sur la trajectoire de mouvement du coulisseau de blocage (42), présente différents angles de montée (53) par rapport à la direction de coulissement (46).
  14. Actionneur linéaire (1) selon l'une quelconque des revendications 1 à 13, caractérisé en ce que la surface d'actionnement (44) comporte une partie d'immobilisation (76), à laquelle la section transversale du corps de blocage (36) est largement ajustée.
  15. Actionneur linéaire (1) selon la revendication 14, caractérisé en ce que la surface d'actionnement (44) possède dans la partie d'immobilisation (76) un angle de montée (53) inférieur à 10°, en particulier inférieur à 5°.
  16. Actionneur linéaire (1) selon l'une quelconque des revendications 1 à 15, caractérisé en ce que l'espace de mouvement (38) pour le corps de blocage (36) est limité au moins dans une direction tangentielle par un élément de butée (54) immobile dans le carter d'extrémité (9).
  17. Actionneur linéaire (1) selon la revendication 16, caractérisé en ce que l'élément de butée (54) est formé par une partie de la paroi intérieure d'une forure dans le carter d'extrémité (9).
  18. Actionneur linéaire (1) selon la revendication 16, caractérisé en ce que l'élément de butée (54) est formé par une paroi intérieure (55) dans le carter d'extrémité (9).
  19. Actionneur linéaire (1) selon l'une quelconque des revendications 16 à 18, caractérisé en ce que l'élément de butée (54) passe par l'axe longitudinal (22) du cylindre, parallèlement à un plan radial (52).
  20. Actionneur linéaire (1) selon l'une quelconque des revendications 1 à 19, caractérisé en ce que l'espace de mouvement (38) pour le corps de blocage (36) est limité dans une direction tangentielle (73) par un élément de réglage (72) tangentiellement flexible, sollicité par un ressort.
  21. Actionneur linéaire (1) selon l'une quelconque des revendications 1 à 20, caractérisé en ce que le corps de blocage (36) est réalisé sous forme de boule (69) et l'évidement de blocage (40) coopérant avec celui-ci est réalisé en forme de calotte sphérique.
  22. Actionneur linéaire (1) selon l'une quelconque des revendications 1 à 20, caractérisé en ce que le corps de blocage (36) est réalisé sous la forme d'un cylindre circulaire (81) et l'évidement de blocage (40) coopérant avec celui-ci est réalisé en forme de segment de cylindre circulaire.
  23. Actionneur linéaire (1) selon l'une quelconque des revendications 1 à 20, caractérisé en ce que le corps de blocage (36) est réalisé sous la forme d'un cône tronqué circulaire (82) et l'évidement de blocage (40) coopérant avec celui-ci est réalisé en forme de segment de cône circulaire.
  24. Actionneur linéaire (1) selon l'une quelconque des revendications 1 à 20, caractérisé en ce que le corps de blocage (36) est réalisé en forme de fût et l'évidement de blocage (40) coopérant avec celui-ci est réalisé de manière concave en forme de fût.
  25. Actionneur linéaire (1) selon l'une quelconque des revendications 1 à 24, caractérisé en ce qu'un diamètre maximum (78) du corps de blocage (36) correspond au maximum à 0,3 fois un diamètre de la broche filetée ou un diamètre (79) de la gaine de blocage.
  26. Actionneur linéaire (1) selon l'une quelconque des revendications 1 à 25, caractérisé en ce qu'une profondeur radiale (77) de l'évidement de blocage (40) correspond au maximum à 0,4 fois le diamètre maximum (78) du corps de blocage (36).
  27. Actionneur linéaire (1) selon l'une quelconque des revendications 1 à 26, caractérisé en ce que l'évidement de blocage (40) possède un rayon actif compris entre 1,0 fois et 1,1 fois un rayon du corps de blocage (36).
  28. Actionneur linéaire (1) selon l'une quelconque des revendications 1 à 27, caractérisé en ce que la broche filetée (28) ou la gaine de blocage (33) comportent au moins six évidements de blocage (40) répartis largement uniformément sur le pourtour extérieur.
  29. Actionneur linéaire (1) selon l'une quelconque des revendications 1 à 28, caractérisé en ce que la dureté du matériau du corps de blocage (36) est choisie supérieure à la dureté du matériau de la face supérieure de l'élément d'actionnement (41).
  30. Actionneur linéaire (1) selon l'une quelconque des revendications 1 à 29, caractérisé en ce qu'il est prévu un élément de commande (58) destiné à déplacer l'élément d'actionnement (41) hors de la position de blocage (45) dans la position de déblocage (47).
  31. Actionneur linéaire (1) selon la revendication 30, caractérisé en ce que l'élément de commande (58) est formé par un piston de commande (59) actionné par un fluide.
  32. Actionneur linéaire (1) selon la revendication 31, caractérisé en ce qu'une direction de déplacement du piston de commande (59) est parallèle à la direction de coulissement (46) du coulisseau de blocage (42).
  33. Actionneur linéaire (1) selon la revendication 31 ou 32, caractérisé en ce que le piston de commande (59) agissant sur l'élément d'actionnement (41) communique par une liaison fluidique avec une première conduite de fluide sous pression (63) menant vers la chambre du cylindre (61) du côté du fond du piston ou avec une deuxième conduite de fluide sous pression (66) menant vers la chambre du cylindre (60) du côté de la tige du piston, et l'espace de mouvement (38) pour le corps de blocage (36) est limité par un élément de réglage (72) tangentiellement flexible, sollicité par un ressort, dans une direction tangentielle (73), qui correspond à la direction de déplacement du système de piston (20), non déverrouillable par le piston de commande (59).
  34. Actionneur linéaire (1) selon la revendication 31 ou 32, caractérisé en ce qu'il est prévu deux pistons de commande (59, 59') agissant sur l'élément d'actionnement (41), un premier piston de commande (59) communiquant par une liaison fluidique avec une première conduite de fluide sous pression (63) menant vers la chambre du cylindre (61) du côté du fond du piston, et un deuxième piston de commande (59') communiquant par une liaison fluidique avec une deuxième conduite de fluide sous pression (66) menant vers la chambre du cylindre (60) du côté de la tige du piston.
  35. Actionneur linéaire selon l'une quelconque des revendications 1 à 34, caractérisé en ce que l'élément d'actionnement (41) est réalisé sous la forme d'une bague d'actionnement (83) enserrant la broche filetée (28) ou la gaine de blocage (33).
  36. Actionneur linéaire selon la revendication 35, caractérisé en ce que la bague d'actionnement (83) est réalisée en tant que coulisseau de blocage (42) sous la forme d'une bague coulissante (84), qui peut coulisser dans le sens axial concentriquement à la broche filetée (28) et qui est munie d'une surface d'actionnement (44) conique.
  37. Actionneur linéaire (1) selon l'une quelconque des revendications 31 à 35, caractérisé en ce que l'élément d'actionnement (41), le piston de commande (59) et un élément de réglage (72) sont montés dans le carter d'extrémité (9).
EP20080005441 2007-09-21 2008-03-22 Actionneur linéaire, en particulier unité cylindre-piston dotée d'un dispositif de verrouillage Active EP2039944B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT14882007A AT505793B1 (de) 2007-09-21 2007-09-21 Zylinder-kolben-einheit mit sperranordnung

Publications (3)

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EP2039944A2 EP2039944A2 (fr) 2009-03-25
EP2039944A3 EP2039944A3 (fr) 2012-09-26
EP2039944B1 true EP2039944B1 (fr) 2013-10-09

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016119251A1 (de) * 2016-10-10 2018-04-12 Fbr Facondrehteile Gmbh Hydromechanischer Verriegelungszylinder und hydraulisches Steuersystem zu dessen Betätigung
CN110925267B (zh) * 2020-01-07 2021-08-17 长春工业大学 基于丝杆锁紧式减摩驱动型直线定位气缸及其控制方法
CN111903441B (zh) * 2020-06-03 2022-10-28 江苏中装建设有限公司 一种固沙栽草装置
CN115199680B (zh) * 2022-07-08 2024-03-19 潍柴动力股份有限公司 一种行走马达用强制解除制动装置及方法

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2782766A (en) 1954-01-05 1957-02-26 Gen Motors Corp Actuator locking means
US2970573A (en) 1959-02-18 1961-02-07 Gen Motors Corp Actuator with stroke end locks
AT4094U1 (de) 1999-12-07 2001-01-25 Weber Hydraulik Gmbh Linearverstellantrieb

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EP2039944A3 (fr) 2012-09-26
AT505793A1 (de) 2009-04-15
EP2039944A2 (fr) 2009-03-25
AT505793B1 (de) 2010-03-15

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