EP2570679B1 - Vérin de verrouillage et procédés de verrouillage et de déverrouillage correspondants - Google Patents

Vérin de verrouillage et procédés de verrouillage et de déverrouillage correspondants Download PDF

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Publication number
EP2570679B1
EP2570679B1 EP12197151.9A EP12197151A EP2570679B1 EP 2570679 B1 EP2570679 B1 EP 2570679B1 EP 12197151 A EP12197151 A EP 12197151A EP 2570679 B1 EP2570679 B1 EP 2570679B1
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EP
European Patent Office
Prior art keywords
locking
cylinder
spindle
fluid
piston
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EP12197151.9A
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German (de)
English (en)
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EP2570679A1 (fr
Inventor
Walter Neumeister
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Neumeister Hydraulik GmbH
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Neumeister Hydraulik GmbH
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Priority to PL12197151T priority Critical patent/PL2570679T3/pl
Publication of EP2570679A1 publication Critical patent/EP2570679A1/fr
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    • 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 locking cylinder according to the preamble of claim 1.
  • the invention also relates to a method for locking a locking cylinder according to claim 8 and a method for unlocking a locking cylinder according to claim 9.
  • Such locking cylinders seem, for example, from the DE-OS 20 39 296 and from the DE 196 33 412 A1 to have become known in the form of frictionally locking working cylinders.
  • a frictional locking of a spindle rotatable relative to a cylinder can take place by means of friction rings in the manner of a friction brake.
  • the spindle is automatically locked by friction solely by gravity and supported by the load acting on the piston, ie by frictional engagement.
  • a friction ring of the friction rings can be lifted together with the spindle using a pressure exerted by a fluid pressure medium pressure from the other friction ring in the axial direction, so that then the spindle is rotatable about its axis of rotation relative to the cylinder, which then coupled to the spindle Piston is movable in the axial direction.
  • the safety of this cylinder against unlocking and consequently against a decrease in the load is limited by design.
  • Such a cylinder is for example from the DE 297 20 838 U1 known.
  • a spindle is rotatably supported at its one end via two thrust bearings about its axis of rotation relative to a cylinder in such a way that it is clamped secured to one of the thrust bearing against axial displacement.
  • the other thrust bearing supports a rotationally fixed to the spindle mounted rotary cone with outer cone, which rotatably attached to the cylinder attached and can be used as a hub brake, axially displaceable against the spring force of a spring, cone-shaped brake piston with inner cone can be braked.
  • This braking device allows only a frictional braking of the spindle and consequently of this coupled via the self-locking spindle thread piston.
  • the braking force exerted by the compression spring remains the same regardless of the load to be moved by means of the piston, so that this working cylinder is only suitable for lifting or lowering comparatively light loads, but not for moving heavy loads, without any significant loss of security comes.
  • working cylinders of this type are for example from DE 38 31 459 A1 and from the US 6,612,221 B1 known. These working cylinders are linear actuators whose pistons are fastened to a piston rod in a thread-free manner or secured against axial movement relative to the piston rod. These cylinders also comprise conical brake bodies, which are constantly acted upon by the spring forces of one or more springs, whereby a frictional locking of the piston relative to the cylinder is achievable. These brake bodies can be released by the action of pressure forces of a fluid pressure medium against the spring forces of the springs.
  • the flange-shaped projection is formed with a cylindrical and coaxial with the axis of rotation of the spindle formed support and bearing body which extends in the axial direction to the cylinder bottom of the cylinder and at its cylinder bottom side end Having a normal to the axis of rotation of the spindle formed flat support and bearing surface.
  • This support and bearing surface is opposite to a likewise flat counter-support and bearing surface of a plain bearing disc, which is supported on the cylinder base.
  • the support and bearing surface and the counter-support and -lager arrangements may form a fluid fluid pressurizable hydrostatic fluid bearing.
  • the flange-shaped approach is based on its side facing away from the locking recesses on a needle bearing, which also serves to support the spindle.
  • the locking security of this locking cylinder meets high demands even with large loads and / or high piston speed.
  • this locking cylinder is accordingly elaborately constructed and also requires a corresponding amount of production time and costs.
  • Such a cylinder is also off DE 36 29 677 A1 known. It is accordingly an object of the invention to provide a locking cylinder and a method of locking and a method for unlocking a locking cylinder available with a comparatively simple, space-saving and robust construction and at relatively low cost manufacturability, yet, even at high loads, a high operational reliability over a long time.
  • the invention preferably relates to a locking cylinder having a cylinder and a piston which, by means of a fluid pressure means which can be supplied to a working channel or both sides of the piston via a working channel or both sides of the piston via these sides, is parallel to the longitudinal axis of the cylinder in a first direction and in a second direction opposite to the first direction is movable, and which is provided with a piston thread, the formation of a non-self-locking thread with a spindle thread frictionally, ie non-positively by friction and, preferably exclusively, by gravity, in particular acting on the piston Load, automatically or automatically, preferably drive-free, in particular without action or support of force accumulators,
  • springs, lockable spindle is engaged, which is rotatable relative to the cylinder about a parallel to the longitudinal axis of the cylinder arranged axis of rotation and relative to the cylinder in the axial direction or parallel to its axis of rotation, preferably only slightly, axially dis
  • the clamping cone bodies when their locking conical surfaces abut each other, can be frictionally jammed together by friction with each other, or the clamping cone bodies, when their locking conical surfaces are abutted against each other, frictionally be jammed by friction with each other self-locking.
  • the locking cylinder according to the invention can be made particularly simple and inexpensive in space-saving and particularly robust construction and offers due to the per se self-locking clamping lock or deadlock a comparatively high reliability in all expected operating conditions, ie not only in normal operation, but also in the occurrence of overloads and / or in case of any pressure loss or leakage.
  • a per se self-locking locking the spindle relative to a rotation about its axis of rotation relative to the cylinder achievable or achieved, so even without that drive or load-related forces would be introduced via the spindle.
  • a double or 2-fold self-locking locking of the spindle can be achieved relative to the cylinder.
  • a particularly large negative efficiency can be realized at a standstill, whereby the safety of the self-locking can be increased compared to the known from the prior art constructions.
  • a first working chamber associated with a first side of the piston preferably delimited by this, and in the, in particular second, direction of axial movement of the piston parallel to the longitudinal axis of the cylinder or parallel to the axis of rotation of the spindle viewed behind or is arranged after the piston
  • Parallel to such a means or parallel to the input and output of such a lowering brake valve or load-holding brake valve may preferably be provided a means for shutting off a passageway in a flow direction and for releasing the passageway in an opposite flow direction.
  • Such an agent may preferably be a check valve.
  • the clamping cone bodies may preferably be designed frusto-conical. At least one of the clamping cone bodies, in particular the first clamping cone body can be designed with or as a conical disk or truncated cone disk.
  • the locking cylinder may preferably have a hollow piston or a piston nut, with an internal thread, in combination with a spindle with an external thread. It is understood, however, that the locking cylinder may alternatively also have a hollow spindle or a spindle nut, with an external thread, in combination with a piston with an external thread.
  • the locking cylinder may preferably be a rotatably mounted relative to the cylinder threaded spindle in combination with a rotatably mounted relative to the cylinder spindle nut, in particular with a threaded piston, which may be connected to a led out of the cylinder drive body, in particular a piston rod.
  • a threaded piston which may be connected to a led out of the cylinder drive body, in particular a piston rod.
  • kinematic reversal of the locking cylinder may comprise a non-rotatable threaded spindle and a rotatably mounted spindle nut, in particular a threaded piston.
  • first locking support body and the first bearing body are integrally connected or manufactured and / or form a, preferably common, first locking support and bearing body and / or that the second locking support Body and the second bearing body are integrally connected or manufactured and / or form a, preferably common, second locking support and bearing body.
  • first locking support and bearing body as a first locking cone surfaces having, self-locking or self-locking acting, first clamping cone body is formed and that the second locking support and bearing body as a second locking cone surfaces having, self-locking or self-locking , second clamping cone body is formed.
  • first locking cone surfaces of the first clamping cone body with the axis of rotation of the spindle form a first angle of inclination and that the second locking cone surfaces of the second clamping cone body with the longitudinal axis of the cylinder or with the axis of rotation of the spindle form a second inclination angle, wherein the first inclination angle and the second inclination angle is equal, preferably four to ten or thirteen, in particular four to seven degrees, preferably six to seven degrees.
  • first inclination angle and the second inclination angle is equal, preferably four to ten or thirteen, in particular four to seven degrees, preferably six to seven degrees.
  • first clamping cone body with or as an outer cone is formed and that the second clamping cone body is formed with or as an inner cone. It is understood, however, that alternatively the first clamping cone body can also be formed with one or as an inner cone and that the second clamping cone body can also be formed with or as an outer cone.
  • first clamping cone body tapers conically in the direction of the axis of rotation of the spindle and in the direction away from the piston or towards a cylinder bottom of the cylinder and / or that the first clamping cone element tapers.
  • Body tapers conically towards the axis of rotation of the spindle and towards the piston towards or away from the cylinder bottom.
  • first locking cone surfaces of the first clamping cone body are arranged in the region or on the side thereof pointing away from the piston or toward the cylinder base or the cylinder base, and in that the second locking cone surfaces of the second clamping cone body are arranged in the region or on the side thereof pointing in the direction of the pistons or away from the cylinder base and / or that the first locking conical surfaces of the first clamping cone Cone body in the region or on which in the direction of the piston toward or from the cylinder bottom side facing away are arranged and that the second locking cone surfaces of the second clamping cone body in the region or in the direction of the piston away or to the cylinder bottom facing side are arranged.
  • the first clamping cone body forms one end of the spindle, preferably a cylinder bottom end of the spindle.
  • one end of the spindle preferably the cylinder bottom end of the spindle, may be formed with or as the first clamping cone body.
  • the second bearing body is formed with or as a cylinder bottom of the cylinder or with the cylinder bottom of the cylinder and / or that the second bearing body as, preferably integrally connected to the cylinder or produced, in particular is formed radially and transversely to the longitudinal axis of the cylinder or to the axis of rotation of the spindle extending approach, which is arranged between the first clamping cone body and the piston.
  • the first clamping cone body is mounted on the fixed bearing, preferably rigidly connected to the cylinder or on one or the cylinder base via the first axial bearing.
  • the first axial bearing is a roller bearing, in particular a needle bearing, preferably a ring bearing and / or a fluid bearing which is preferably acted upon or acted upon by a fluid pressure medium or fluid.
  • both the first axial bearing and the second axial bearing can be designed as a, preferably hydrostatic, fluid plain bearings. This can be an even more cost effective and robust As well as space-saving design can be achieved, up to a construction in which an inventive locking cylinder is locked not only on pressure or only on train, but both pressure and train.
  • the first clamping cone body is at least partially received in a recess, in particular in a chamber, of the cylinder, preferably one or the cylinder bottom of the cylinder, on the one hand by a or the cylinder bottom of the cylinder Cylinder and on the other hand by a, preferably integrally connected to the cylinder or produced, in particular radially and transversely to the longitudinal axis of the cylinder or to the axis of rotation of the spindle extending approach is limited.
  • a particularly preferred regulation or control of the locking and / or lift-off process can be created while still simpler and comparatively space-saving and robust construction.
  • first clamping cone body is at least partially received in a recess, in particular a chamber, of the cylinder, preferably one or the cylinder bottom of the cylinder, into which the first fluid channel opens on a first side of the first clamping cone body, which is inclined to the axis of rotation of the spindle towards the first locking cone surfaces assigned.
  • first fluid channel can be arranged on that side of the first clamping cone body to which its or the first locking cone surfaces incline.
  • a further improvement in terms of the above advantages can be achieved by inserting into the recess on a second side of the first clamping cone body pointing away from the first side of the first clamping cone body, preferably immediately adjacent to the first locking cone body.
  • Conical surfaces of the first clamping cone body, a second fluid channel opens, and wherein in the locked state, in which the clamping cone bodies abut against each other, the first fluid channel and the second fluid channel through a first locking cone surfaces containing Part of the first clamping cone body separated from each other, in particular sealed against each other.
  • a second fluid channel or the second fluid channel opens into the recess immediately adjacent to the first locking cone surfaces of the first clamping cone body.
  • a particularly advantageous pressure distribution can be achieved in that the first fluid channel or the second fluid channel opens in a region of the recess or the fluid plain bearing containing or cutting the axis of rotation of the spindle.
  • the recess is sealed by a seal against the piston or against a or the working chamber, which is formed between the cylinder and the piston and the of the
  • the first clamping cone body facing side of the piston possibly also of the second bearing body and / or of the approach is limited and into which the working channel opens.
  • the operability and reliability can be achieved or increased to a particular extent.
  • this may alternatively or additionally be accomplished by having the first fluid channel and / or the second fluid channel opposite a working chamber formed between the cylinder and the piston and facing the first pinch-cone body Side of the piston, possibly also of the second bearing body and / or of the approach is limited and into which the working channel opens, is sealed by a or the seal or are.
  • the seal bears against a thread-free part of the spindle arranged between the first clamping cone body and the spindle thread and / or the piston and is supported on the second bearing body and / or on the projection.
  • the recess viewed in a cross section containing the longitudinal axis of the cylinder or the axis of rotation of the spindle and viewed parallel to the longitudinal axis or to the axis of rotation, has a T-shaped cross section.
  • the first clamping cone body and the second clamping cone body or the at least partially limited recess of this can preferably be designed rotationally symmetrical.
  • the first clamping cone body can be designed rotationally symmetrical to the axis of rotation of the spindle and the second clamping cone body and / or at least partially limited recess can be designed rotationally symmetrical to the longitudinal axis of the cylinder or to the axis of rotation of the spindle ,
  • a further simplified, space-saving and robust construction can be achieved in that the first axial bearing and / or the second axial bearing is arranged in the recess and / or is formed with the recess bounding wall parts.
  • a further improved construction can be realized in that the first thrust bearing is arranged between the first clamping cone body and the second bearing body and / or the lug and / or that the second thrust bearing is arranged between the first clamping cone body and the lug ,
  • first thrust bearing is at least partially mounted in a bearing annular groove of the recess or formed or limited with a bearing annular groove of the recess.
  • the first bearing surface of the first clamping cone body viewed in a projection perpendicular to the axis of rotation of the spindle, ie in a direction parallel to the axis of rotation of the spindle Projection direction, is greater than a spindle surface of the spindle, which is located on the sealed by the seal of the first clamping cone body at least partially receiving recess side of the seal and in, preferably directly or directly, fluid connection with one or the working chamber is preferably acted upon by the pressure medium located in one or the working chamber, which is formed between the cylinder and the piston and of the side facing the first clamping cone body side of the piston. possibly also of one or the second bearing body and / or the approach is limited and opens into the working channel.
  • the first bearing surface of the first clamping cone body that can be acted upon or acted upon by the fluid pressure medium has an outer diameter and that the seal has an inner diameter, the outer diameter of the first bearing surface being larger, preferably much larger is, as the inner diameter of the seal or as the outer diameter of the unthreaded portion of the spindle against which the seal is applied and / or which is in fluid communication with the working chamber.
  • a suitable for many or even all expected operating conditions axial bearing of the rotatable spindle, ie in any phase and in any position, even in case of failure of the hydraulic or in case of leakage, can be achieved if the fluid bearing during a movement of the piston both in the first direction as well as in the second direction and / or during one, preferably arbitrary, Rotation of the spindle about its axis of rotation, preferably in the course or during the stopping of the piston, in particular in any holding position of the piston, is acted upon or fluid fluid pressure medium is such that the clamping cone bodies are detached from each other, in particular, are lifted apart from each other so that their locking cone surfaces do not touch, preferably so that the spindle is then unlocked.
  • a particularly advantageous unlocking of the self-locking and friction locked by static friction clamping cone body can be achieved that at least one of the clamping cone body of a locking position in which the locking cone surfaces of the clamping cone body by frictionally Stiction with each other self-locking connected or jammed, are, preferably exclusively, by acting on the hydrostatic fluid bearing with the fluid pressure medium, in particular under elevated pressure, in a, preferably a rotation of the spindle about its axis of rotation relative to the cylinder enabling, unlocking position can be transferred is or be transferred.
  • a preferred embodiment of the invention can be provided that in a housing, preferably in a provided in the region of the thrust bearing and / or cylinder bottom of the cylinder or in the cylinder bottom end housing, fluid channels or flow and connection channels and a control unit forming control and / or control elements between connecting lines or holes for an alternating supply or discharge of the pressure medium and fluid channels or lines to both sides of the piston provided working chambers and the fluid bearing are arranged.
  • a control unit forming control and / or control elements between connecting lines or holes for an alternating supply or discharge of the pressure medium and fluid channels or lines to both sides of the piston provided working chambers and the fluid bearing are arranged.
  • control and / or regulating members of the control unit are self-medium-actuated or self-medium-controlled by the pressure medium.
  • the pressure medium Preferably can be completely dispensed with electrical lines.
  • the locking cylinder can preferably be safely operated exclusively by means of a pump for the pressure medium for a long time.
  • a means for releasing a first passageway between the fluid channel and a first connection channel of the connection channels and for, preferably substantially simultaneous, blocking a second passageway between a fluid channel fluid-fluid bearing fluid channel and two alternately serving as a flow channel or return channel between the fluid channel and a second connection channel of the connection channels or for releasing the second passageway between the fluid channel and the second connection channel and for, preferably substantially simultaneous, blocking the first passageway between the fluid channel and the first connection channel is arranged.
  • Such a means may preferably be a shuttle valve and / or such means may be formed with double check valves. This allows an even more compact and robust construction be achieved in conjunction with long-term safe operation.
  • a particularly preferred embodiment of the invention can be provided that between the first fluid channel, which is when the locking-supporting body or the clamping cone body are clamped together, shut off from the fluid fluid with the fluid bearing fluid channel and the when the interlocking support bodies and the clamping conical bodies are lifted apart from one another, is fluidically connected to the fluid channel, and a second fluid channel, which is in fluid communication with one or the working chamber, preferably with one or the second working chamber fluidly connected between the piston and a lid of the cylinder associated with the free end of the spindle, means for switching or releasing or, if necessary, throttling or releasing a passageway between the first fluid channel and the second fluid channel, is arranged.
  • Such a means may preferably be a shut-off valve or a throttle / passage changeover valve, in particular a 2-2-way valve.
  • This can preferably be coupled or fluid-connected to a switching or actuating channel, by means of which, when it is acted upon by the pressure medium, switching from a passage position into a blocking position or from a passage position into a throttle position can be achieved.
  • a switching or actuating channel by means of which, when it is acted upon by the pressure medium, switching from a passage position into a blocking position or from a passage position into a throttle position can be achieved.
  • the invention also relates to a method for non-rotatable frictional locking of the rotatable about its axis of rotation
  • Spindle of the locking cylinder having the features of at least one claim of Claims 1 to 7 against rotation about the axis of rotation relative to the cylinder, at least one of the locking support bodies being unlocked to permit rotation of the spindle about its axis of rotation relative to the cylinder.
  • a locking position in one or the axial direction parallel to the axis of rotation of the spindle or to the longitudinal axis of the cylinder, transferred into a locking position, preferably displaced, is in which the locking-support body frictionally locked by static friction and thus clamped together self-locking, that they can only be transferred into the unlocked position by exercising release forces that release the deadlock.
  • At least one of the locking support bodies is parallel to an unlocking position, in which the spindle is freely rotatable about its axis of rotation relative to the cylinder, preferably in one or the axial direction to the axis of rotation of the spindle or to the longitudinal axis of the cylinder is transferred to the locking position in which the locking support body frictionally jammed by static friction and are clamped together so self-locking that you only under exercise of the clamping solving dissolving forces in the Unlocked position in which the spindle about its axis of rotation relative to the cylinder is substantially freely or freely rotatable.
  • the locking-cone surfaces having locking-support body from a lifting and unlocking position in which the locking-support body are lifted apart from each other so that their locking-cone surfaces do not touch, preferably in one or the axial direction parallel to the axis of rotation of the spindle or to the longitudinal axis of the cylinder, be transferred to an investment and locking position, in which the locking cone surfaces of the locking support body abut each other and non-rotatably by friction friction and are clamped together so self-locking that you can be transferred only under exercise of the clamping release separating forces in the Abhebe- and unlocked position.
  • the invention also relates to a method for unlocking the non-rotatably and frictionally, ie non-positively by friction, and by gravity, preferably by a load acting on the piston, automatically, preferably without drive, in particular without the action or support of force accumulators, such as springs, against rotation about its axis of rotation relative to the cylinder of the locking cylinder having the features of at least one claim of claims 1 to 7, locked spindle, wherein the spindle is locked in the locked state by means of the locking support body frictionally against rotation about its axis of rotation relative to the cylinder wherein the latch support bodies receive axial forces acting on the spindle in the second direction, preferably such that the spindle is locked in the locked state against movement in the second direction on the cylinder, the latch support bodies be transferred to an unlocking position in which the spindle is rotatable about its axis of rotation relative to the cylinder, and wherein at least one of the locking-supporting body from a locking position in which the locking-supporting body frictionally by
  • the unlocking can be achieved in a particularly simple manner in that the locking-supporting body of the locking position in which they are frictionally clamped by friction with each other self-locking, preferably exclusively, by applying the hydrostatic fluid bearing with the fluid pressure fluid under elevated pressure, preferably in one or the axial direction parallel to the axis of rotation of the spindle or to the longitudinal axis of the cylinder, into a rotation of the spindle about its axis of rotation relative to the cylinder enabling unlocking position are transferred or transferred to an unlocking, in which is relatively free to rotate freely relative to the cylinder.
  • the locking-cone surfaces having locking-support body of the Locking position in which they are frictionally clamped by friction with each other self-locking, preferably exclusively, by acting on the hydrostatic fluid bearing with the fluid pressure fluid under increased pressure, preferably in one or the axial direction parallel to the axis of rotation of the spindle or to the longitudinal axis the cylinder, in a, preferably a rotation of the spindle about its axis of rotation relative to the cylinder enabling, lifting and unlocking position are transferred, in which the locking support body are lifted from each other, so that their locking-cone surfaces no longer touch.
  • the unlocking can be provided that, preferably by means of a or the control device, first the fluid bearing is subjected to the pressure medium to allow rotation of the spindle about its axis of rotation relative to the cylinder and / or order a lifting of the locking-support body or the clamping cone body from the locking position in which they are frictionally clamped together by friction with each other, to effect in a lifting and unlocking, in which the locking support body or the Clamping cone body are lifted apart from each other so that their locking cone surfaces at least partially no longer touch, and that only then the pressure medium is supplied to a working chamber, which is assigned to one side of the piston, preferably limited by this is, either about a movement of the piston in an axial direction parallel to the length axis of the cylinder or parallel to the axis of rotation of the spindle to enable or effect or whereby a movement of the piston in the axial direction enables, supports or effects.
  • a procedure has particular advantages when the piston or the piston rod is to be moved
  • the fluid bearing can first be acted upon by one or the fluid channel or supply channel with the pressure medium, whereby a lifting of the locking support body or the clamping cone body, from the locking position in which they by frictional Stiction are clamped together, in a lift-off and unlocking, is effected, in which the locking-support body or the clamping cone body are at least partially lifted from each other, so that their locking-cone surfaces at least partially no longer touch and thereby opening or forming a passageway or gap between and along the opposite in the off-hook locking-cone surfaces, which is fluidly connected to one or the fluid channel or discharge channel, preferably via one or the Working channel, is fluidly connected to the working chamber or, so that the piston with the is acted upon by the fluid or discharge channel in the working chamber or flowing pressure medium, either to allow movement of the piston in an axial direction parallel to the longitudinal axis of the cylinder or parallel to the axis of rotation of the spindle to support or effect , or whereby a movement of
  • the locking support bodies are designed as self-locking or self-locking clamping cone body.
  • first clamping cone bodies preferably of two first clamping cone bodies rotatably connected to the spindle or fixed to the spindle and that one, preferably numerically corresponding, plurality of second clamping Cone bodies, preferably of two second clamping cone bodies, rotatably connected to the cylinder or are fixed to the cylinder.
  • first clamping cone bodies are designed and manufactured in one piece as a clamping double cone body.
  • first clamping cone body and / or that the second clamping cone body is or are each designed as a clamping double-cone body.
  • the clamping double-conical body or bodies may be formed symmetrically to an axis or plane perpendicular to the axis of rotation of the spindle or perpendicular to the longitudinal axis of the cylinder.
  • the clamping cone body, in particular of the clamping double-cone body are each designed as an outer cone or as an inner cone.
  • the locking cone surfaces of the clamping cone body in particular of the clamping double-cone body, can form or enclose with the axis of rotation of the spindle or with the longitudinal axis of the cylinder a different angle of inclination or, preferably, an equally large angle of inclination.
  • the locking conical surfaces of the clamping cone bodies in particular of the respective clamping double-cone body, may point in the same or preferably in different directions.
  • the locking cone surfaces of the clamping cone bodies preferably a first clamping double cone body, may face away from each other and the locking cone surfaces of the clamping cone body, preferably a second clamping double cone Body, can face each other or face each other.
  • the locking conical surfaces of the clamping cone body preferably a first clamping double-cone body, facing each other or can face each other and that the locking conical surfaces of the clamping cone Body, preferably a second clamping double-cone body, facing away from each other.
  • FIG. 1 is a lockable pressure lock cylinder 20 and in FIG. 2 a lockable on train locking cylinder 120 is illustrated in each case in a longitudinal cross-section.
  • Identical components, elements and directional arrows are provided with the same reference numerals. Different components, elements and arrows are designated in the train lockable locking cylinder 120 with 100-numerals, while corresponding components, elements and arrows are designated in the pressure-lockable locking cylinder 20 with 10-digits.
  • Each locking cylinder 20, 120 comprises a cylinder and a displaceable therein in the axial direction 59, but non-rotatably mounted to the cylinder 21 piston 22.
  • Der Piston 22 is sealed relative to the cylinder inner wall of the cylinder 21 by a ring seal 37 and on its in the direction of the longitudinal axis 25 of the cylinder 21 facing away from each other sides 23.1, 23.2 by a fluid, in particular hydraulic, pressure medium, preferably oil, acted upon by a pressure medium assisted To allow movement of the piston 22 in a first direction 31 or in a second direction 32.
  • the first direction 31 is the extension direction
  • the second direction 32 is the retraction direction of the piston 22.
  • the lock-lock cylinder 120 is the first direction 31 the retraction direction and in the second direction 32 about the extension direction of the piston 22.
  • the pressure medium can be supplied via a first working channel 24.1 on the cylinder bottom 40 facing side 23.1 of the piston 22 in a first working chamber 48 to a movement of the piston 22 along the Cylinder 21 in the second direction 32 to achieve.
  • the pressure medium via a second working channel 24.2 on a second side 23.2 of the piston 22, which points away from the first side 23.1, fed into a second working chamber 49 to achieve a movement of the piston 22 along the cylinder 21 in the first direction 31 to be able to.
  • the first working chamber 48 is sealed relative to the second working chamber 49 via a ring seal 37 of the piston 22.
  • the seal 37 is supported in an annular groove of the piston 22 that is open outwards to the cylinder jacket inner wall.
  • the piston 22 forms a projection which is non-rotatably connected to the piston rod 22.1.
  • the piston rod 22.1 extends from the annular second side 23.2 of the piston 22 in the axial direction 59 coaxial with the longitudinal axis 25 of the cylinder 21 and to the rotational axis 33 of the spindle 30.
  • the piston 22 is designed as a tubular hollow body and has a designated as a piston thread 26 internal thread.
  • the piston 22 may also be referred to as a piston nut.
  • the piston thread 26 is engaged with an external thread, also referred to as a spindle thread 28, of the spindle 30, on which the piston 22 is guided.
  • the piston thread 26 and the spindle thread 28 form a non-self-locking thread 27.
  • the non-self-locking thread 27 is designed right-handed, but can also be designed left-handed.
  • the piston thread 26 and the spindle thread 28 in each case as one, in particular multi-start, coarse thread, preferably trapezoidal coarse thread designed.
  • an eight-speed coarse thread can be used.
  • the cylinder 21 is closed at its the free end 71 of the spindle 30 associated side by a piston rod 22.1 receiving cover 40.1.
  • the ring-shaped piston cover 40.1 surrounds the piston rod 22.1 and has an open towards the piston rod 22.1 annular groove. In this annular groove, a ring seal 60 is supported, which seals the second working chamber 49 to the outside.
  • the cylinder 21 is closed by a lid or head forming the cylinder bottom 40. This can preferably be connected in several parts with the cylinder 21.
  • the spindle 30 is arranged about a parallel to the longitudinal axis 25 of the cylinder 21 arranged rotational axis 33 relative to the cylinder 21 and is also relatively axially displaceable relative to the cylinder 21 in the axial direction 59 or parallel to the longitudinal axis 25 of the cylinder 21.
  • the axial displaceability of spindle 30 indicated by double arrow 34 or the axial spindle clearance is only about 1.0 to 1.5 mm.
  • the spindle 30 is frictionally, ie non-positively by friction, and in the embodiments shown exclusively by gravity, in particular by a force acting on the piston 22 load 29, 129, automatically or automatically, drive-free and without the action or support of power stores, such.
  • the spindle 30 is self-locking lockable and indeed double-self-locking according to the invention.
  • two locking support elements which can be converted into a mutual frictional locking engagement are provided.
  • Body 35, 36; 135, 136 provided. These are intended to be able to lock the spindle 30 frictionally against rotation about its axis of rotation 33 and to be able to absorb axial forces acting on the spindle 30 in the second direction 32, in the embodiments shown such that the spindle 30 is in the locked state secured against movement in the second direction 32 secured to the cylinder 21, here at the cylinder bottom 40, is supported.
  • the first lockup support body 35, 135 of the lockup support bodies 35, 36; 135, 136 is rotatably, preferably rigidly connected to the spindle 30 and secured to the spindle 30.
  • the second Lockup support body 36; 136, the lockup support bodies 35, 36; 135, 136 is non-rotatably, preferably rigidly connected to the cylinder 21 or to the cylinder bottom 40 or attached to the cylinder 21, here on the cylinder base 40, preferably in one piece.
  • the spindle 30 is here at two axial bearings 38 spaced apart in the axial direction 38, 39; 138, 139 stored.
  • a first thrust bearing 38; 138 is intended to receive axial forces acting on the spindle 30 in the first direction 31.
  • the second thrust bearing 39; 139, the thrust bearings 38, 39; 138, 139 is intended, in its function as a fluid sliding bearing, to receive axial forces acting on the spindle 30 in the second direction 32.
  • the spindle 30 is further provided with a first bearing body 41; 141 provided, the first bearing surface 43; 143 having a second bearing surface 44; 144 a rotationally fixed, preferably rigid, connected to the cylinder 21 and attached to the cylinder 21 second bearing body 42; 142, here the cylinder bottom 40, opposite.
  • the first bearing surface 43; 143 of the first bearing body 41; 141 and the second bearing surface 44; 144 of the second bearing body 42; 142 form the second thrust bearing 39; 139 off.
  • the second thrust bearing 39; 139 is inventively as a, preferably hydrostatic, fluid bearings 45; 145 designed, in particular via a first fluid channel 46; 146 is acted upon with or with the fluid pressure medium.
  • the first locking-supporting body 35; 135 as a first locking cone surface 51; 151, self-locking or self-locking acting, first clamping cone body 53; 153 and the second lock-up support body 36; 136 is as a second Locking cone surfaces 52; 152, self-locking or self-locking acting, second clamping cone body 54; 154 designed.
  • the locking cone surfaces 51, 52; 151, 152 of these clamping cone bodies 53, 54; 153, 154 can be clamped together self-locking.
  • clamp-cone body 53; 153 are displaced in the first direction 32 parallel to the longitudinal axis 25 of the cylinder 21 until its locking cone surfaces 51; 151 at the opposite, counter-surface forming locking cone surfaces 52; 152 of the second clamp-cone body 54; Abut 154, wherein the clamping cone body 53, 54; 153, 154 can be frictionally clamped by friction with each other self-locking or can be.
  • the lock according to the invention is thus a kind of double-self-locking lock.
  • the clamping cone bodies 53, 54; 153, 154 are each frustoconical shaped.
  • the first clamping cone body 53; 153, the rotatably connected to the spindle 30 and rotatably attached to the spindle 30 is here in each case as a conical disk or as a cone-butt-disk 55; 155 designed.
  • the respective first clamping cone body 53; 153 and the respective second clamping cone body 54; 154 are rotationally symmetrical to the axis of rotation 33 of the spindle 30 and to the longitudinal axis 25 of the cylinder 21 designed.
  • the respective first clamping cone body 53; 153 is in each case in a designed as a chamber recess 75; 175 of the cylinder bottom 40 received or arranged.
  • the recess 75 is preferably also rotationally symmetrical to the longitudinal axis 25 of the cylinder 21 and to the axis of rotation 33 of the spindle 30 designed.
  • the respective first clamping cone body 53; 153 is rotatably connected to or fixed to a non-threaded portion 50 of the spindle 30, which in turn rotatably connected to the spindle thread 28 having part of the spindle 30 is connected or attached thereto.
  • the not provided with a spindle thread portion 50 of the spindle 30 is in a bore of a radially inwardly and transversely to the longitudinal axis 25 of the cylinder 21 extending projection 72; 172 recorded.
  • the approach 72; 172 is here between the respective first clamping cone body 53; 153 and the first working chamber 48 is arranged.
  • the approach 72; 172 has an open to the unthreaded portion 50 of the spindle 30 annular groove on the wall, a ring seal 76 is supported. About the ring seal 76, the respective recess or chamber 75; 175 sealed against the first working chamber 48.
  • first lockup support body 35; 135 and the first bearing body 41; 141 made in one piece and each form a common first locking support and bearing body 61; 161 out, here in the form of the clamping cone disc 55; 155.
  • second locking support body 36; 136 and the second bearing body 42; 142 are made in one piece and form a common second locking support and bearing body 62; 162 off.
  • the first locking cone surfaces 51; 151 of the rotatably connected to the spindle 30 first clamping cone body 53; 153 close with the axis of rotation 33 of the spindle 30, a first inclination angle 63; 163.
  • the second locking cone surfaces 52; 152 of the cylinder bottom side clamping cone body 54; 154 close to the longitudinal axis 25 of the cylinder 21 and with the axis of rotation 33 of the spindle 30 has a second inclination angle 64; 164.
  • the inclination angle 63; 163 of the locking cone surfaces 51; 151 of the rotatably connected to the spindle 30 first clamping cone body 53; 153 and the inclination angle 64; 164 of the locking cone surfaces 52; 152 of the rotatably connected to the cylinder 21 second clamping cone body 54; 154 are the same size and here are each preferably about 6.5 degrees.
  • inclination angles 63, 64; 163, 164 or more generally at angles of inclination of about 4 to 13 degrees, preferably from 4 to 10 degrees can be, depending on the selected material pairing and other parameters in juxtaposition or nesting of the first clamping cone body 53; 153 and the second clamping cone body 54; 154 to achieve a self-locking in such a way that the first clamping cone body 53 and the second clamping cone body 54 and that the first clamping cone body 153 and the second clamping cone body 154 is no longer relative to each other around the Longitudinal axis 25 and about the axis of rotation 33 are rotatable and also no longer relative to each other can be moved or displaced in the axial direction 59, that is also not in the first direction 31, ie here in a direction away from each other. Because it then enters a self-locking by jamming of the respective two clamping cone body 53, 54 and 153, 154 a.
  • the first clamping cone body 53; 153 is as outer cone 56; 156 formed while the second clamping cone body 54; 154 as an inner cone 57; 157 is formed.
  • the first clamp-cone body 53 tapers conically toward the rotational axis 33 of the spindle 30 and toward the cylinder bottom 40 of the cylinder 21.
  • the first clamping cone body 153 of the train lockable lock cylinder 120 tapers toward the piston 22 and away from the cylinder bottom 40 but also toward the rotation axis 33 of the spindle 30.
  • the first lock-taper surfaces 51 of the first clamp-cone body 53 non-rotatably connected to the spindle 30 are in the direction away from the piston 22 and toward the cylinder bottom 40 of the cylinder 21
  • Arranged side 65 and the second locking cone surfaces 52 of the rotatably connected to the cylinder 21 second clamping cone body 54 are in the direction. to the piston 22 and from the cylinder bottom 40 facing away side 66 is arranged.
  • the first locking cone surfaces 151 of the rotatably connected to the spindle 30 first clamping cone body 153 facing in the direction of the piston 22 and away from the cylinder bottom 40 away Page 165 arranged and the second locking cone surfaces 152 of the rotatably connected to the cylinder 21 second clamping cone body 154 are arranged on its in the direction of the piston 22 away or to the cylinder bottom 40 side facing 166.
  • the second bearing body 42 is formed with a part of the cylinder bottom 40 of the cylinder 21, while in the train lockable lock cylinder 120, the second bearing body 142 as the, preferably integrally connected to the cylinder 21 or manufactured itself radially inwardly and transversely to the longitudinal axis 25 of the cylinder 21 and to the axis of rotation 33 of the spindle 30 extending lug 172 is formed.
  • first thrust bearing 38, 138 in the exemplary embodiments shown is in each case a roller bearing designed as a needle bearing in the form of a ring bearing. This needle bearing is partially received in each case in a bearing annular groove 78, 178, which is formed coaxially to the longitudinal axis 25 of the cylinder 21.
  • the bearing groove 78; 178 delimits each chamber or recess 75; 175th
  • This chamber or recess 75; 175 has a T-shaped cross section 77; 177 on.
  • a first fluid channel 46 via which the fluid sliding bearing 45 can be acted upon by pressure medium, opens into a region of the recess 75 containing the longitudinal axis 25 of the cylinder 21. Accordingly, this first fluid channel 46 opens a first side 65 of the first clamping cone body 53, the one of the axis of rotation 33 of the spindle 30 inclined toward first locking cone surfaces 51; 151 is assigned. In the region of the other side 66 of the first clamping cone body 53, a second fluid channel 47 opens into the recess 75, specifically here immediately adjacent to the first locking cone surfaces 51 of the first clamping cone body 53.
  • spindle surface is an annular surface which is bounded on the one hand in the radial direction by the cylindrical outer surface of the not provided with the spindle thread portion 50 of the spindle and on the other hand with the outer diameter or external thread 28 of the spindle 30.
  • the acted upon by the fluid pressure medium first bearing surface 43; 143 of the first clamping cone body 53; 153 has an outer diameter 80; 180, which is larger, is preferably much larger than the inner diameter 81 of the seal 76 or as the outer diameter 82 of the unthreaded portion 50 of the spindle 30th
  • pressure medium either first via the first fluid channel 46 and then thereafter via the first working channel 24.1 or preferably simultaneously via the first fluid channel 46 and the first working channel 24.1 are supplied, so that accordingly either first the recess 75 and then the first working chamber 48 is acted upon with pressure medium or preferably by the recess 75 and the first working chamber 48 are acted upon simultaneously with pressure medium.
  • the piston 22 can move in the first direction 31, ie here in the extension direction or upwards, whereby the load 29 can be lifted.
  • pressure fluid flows through the first working channel 24.1 in the first working chamber 48 and at the same time in the second working chamber 49 optionally located pressure medium flows through the second working channel 24.2.
  • the fluid sliding bearing 39 is or are subjected to pressure medium in such a way that the clamping cone bodies 53, 54 are detached from one another, in particular lifted off from one another in such a way that their locking Do not touch the conical surfaces 51, 52, so that then the locking cone surfaces 51, 52 are in a lifting and unlocking.
  • the first working channel 24.1 can be depressurized. If both the first working channel 24.1 and the first fluid channel 46 are depressurized, the piston 22 together with the spindle 30 and rotatably connected thereto first first clamping cone body 53 due to the direction of gravity, ie in the second direction 32nd , acting load 29 in the second direction 32, by the intended small axial play from here about only 1.0 to 1.5 mm, until the first clamping cone body 53 at or in the second clamping cone Body 54 self-locking jammed stuck.
  • first working channel 24.1 can be depressurized, but not the first fluid channel 46, so that then during the stopping of the piston 22, the fluid bearing 45 is still acted upon with pressure medium and will and accordingly with the Spindle 30 rotatably connected first clamping cone body 53 can still be kept lifted from the second clamping cone body 54 or possibly regulated, can be held in an intermediate position in which a brake friction but not jamming the Clamping cone body 53, 54 occurs.
  • pressure medium can be supplied via the first fluid channel 46, wherein only then or simultaneously pressure medium can be supplied in the second working channel 24.2.
  • the first fluid channel 46 is always with pressure medium acted upon, so that in this case the fluid-sliding bearing 45 is constantly acted upon with pressure medium and at the same time rotatably connected to the spindle 30 first clamping cone body 53 of the non-rotatably connected to the cylinder 21 second clamping cone body 54 in a lift - And unlocked position is lifted, in which their locking cone surfaces 51, 52 do not touch, so that is then the first clamping cone body 53 and the spindle 30, preferably substantially free to the spindle rotation axis 33 relative to the cylinder 21 can rotate.
  • both the second working channel 24.2 and the first fluid channel 46 can now be depressurized, so that the spindle 30, together with the first clamping cone, is immediately caused by the acting load 29 -Body 53 moves in the second direction 32, again only to the small spindle-shifting play from here about 1.0 to 1.5 mm, until the first clamping cone body 53 at or in the second terminal Cone body 54 self-locking jammed stuck. Then the spindle 30 is against rotation by this self-locking clamp lock locked about its axis of rotation 33 relative to the cylinder 21 as well as against an axial lifting in the axial direction 59, ie in the first direction 31, so that in turn also a double self-locking is achieved.
  • pressure medium either first via the first fluid passage 146 and then via the second working channel 24.2 or preferably simultaneously via the first fluid channel 146 and be supplied to the second working channel 24.2, so that accordingly either first the recess 175 and then the second working chamber 49 is acted upon by pressure medium or by preferably the recess 175 and the second working chamber 49 are acted upon simultaneously with pressure medium.
  • the piston 22 can move in the first direction 31, ie here in the retraction direction or upwards, whereby the load 129 can be lifted.
  • pressure fluid flows through the second working channel 24.2 in the second working chamber 49 and at the same time in the first working chamber 48 optionally located pressure medium flows through the first working channel 24.1.
  • the fluid sliding bearing 139 is or are subjected to pressure medium in such a way that the clamping cone bodies 153, 154 are detached from one another, in particular lifted off from one another in such a way that their locking Do not touch cone surfaces 151, 152 so that then the locking cone surfaces 151, 152 are in a lifting and unlocking.
  • the second working channel 24.2 can be depressurized. If both the second working channel 24.2 and the first fluid channel 146 are depressurized, the piston 22 together with the spindle 30 and rotatably connected thereto first clamping cone body 153 due to the in the direction of gravity, ie in the second direction 32nd , acting load 29 in the second direction 32 from, namely by the intended low axial play from here about only 1.0 to 1.5 mm, until the first clamping cone body 153 on or in the second clamping cone body 154 self-locking jammed stuck.
  • first clamping cone body 153 can still be kept lifted from the second clamping cone body 154 or possibly regulated, can be held in an intermediate position in which a brake friction but not jamming the Clamping cone body 153, 154 enters.
  • pressure medium can be supplied via the first fluid channel 146, wherein only then or simultaneously pressure medium can be supplied in the first working channel 24.1.
  • the rotatably connected to the spindle 30 first clamping cone body 153 can be moved together with the threaded spindle 30 and the piston 22 in the first direction 31 and raised, in turn until the first clamping cone body 153 on the rolling bearing 138th comes to the plant, whereupon the spindle 30 begins to rotate together with the rotatably connected with it first clamping cone body 153 in the now opposite direction, whereupon the piston 22 together with the load 129 in the second direction 32, ie here in Extension direction is moved.
  • the pressure medium located in the second working chamber 49 can flow out via the second working channel 24.2.
  • first clamping Cone body 153 is lifted from the rotatably connected to the cylinder 21 second clamping cone body 154 in a Abhebe- and unlocked position in which their locking cone surfaces 151, 152 do not touch, so that is then the first Clamping cone body 153 and the spindle 30, preferably substantially free to rotate about the spindle rotation axis 33 relative to the cylinder 21.
  • both the first working channel 24.1 and the first fluid channel 146 can now be depressurized, so that then due to the acting Load 129 immediately moves the spindle 30 together with the first clamping cone body 153 in the second direction 32, again only to the small spindle-shifting play from here about 1.0 to 1.5 mm, until the first Clamping cone body 153 on or in the second clamping cone body 154 self-locking clamped stuck.
  • the spindle 30 is locked by this self-locking clamping lock against rotation about its axis of rotation 33 relative to the cylinder 21 as well as against an axial lifting in the axial direction 59, ie also in the first direction 31, so that in turn also one double self-locking is achieved.
  • the clamping force between the respectively clamped conical bodies 53 and 54 or 153 and 154 clamped with each other increases with increasing load 29; 129 proportionally.
  • an always secure locking of the spindle 30 against rotation about its axis of rotation 33 relative to the cylinder 21 can be achieved and as a result, further movement of the piston 22 and acting on this load 29, 129 can be reliably prevented, and although not only in a normal operation of the locking cylinder 29, 129, but also in a pressure failure of the pressure fluid system or in a possibly occurring leakage of the pressure fluid system.
  • the locking cylinder 20, 120 according to the invention provide a higher locking security than previously known frictionally locking locking cylinder.
  • FIGS Figures 3 and 4 Two preferred embodiments of locking cylinders 20, 120 equipped with control units 85, 185 according to the invention are shown in FIGS Figures 3 and 4 shown. Except for the integrated control units 85, 185, these locking cylinders are designed the same as those in the FIGS. 1 and 2 illustrated locking cylinder 20, 120, so that in this regard can be made to the above statements.
  • a control unit 85, 185 with a plurality also as fluid channels 46, 146; 91, 191; 97, 197; 99, 199; 103, 203; 106, 206 designated flow and connection channels and control members 108, 208; 88; 90; 98, 98 ', 198; 104 integrated, which are shown as usual in such circuit diagrams, with circuit symbols or symbols of fluid technology.
  • preferably only two connecting lines 86 and 87 or bores for an alternating supply and discharge of the pressure medium can be provided.
  • Each of the connecting lines 86 and 87 can thus serve as a supply line or as a return line.
  • a switching or control valve not shown in the figures may be provided, which is fluidly connected to a supply device for the pressure medium also not shown in the figures, which may contain a pump and a tank for the pressure medium.
  • Each control unit 85, 185 has as essential control or regulating organs at least one load-holding lowering brake valve or lowering brake valve 90, a shuttle valve 104, at least one check valve 88, 92, preferably also a switching or changeover valve, in particular in shape a 2-2-way valve 98, 198, on.
  • the respective load-holding lowering brake valve or lowering brake valve 90 has an inlet 95, an outlet 96 and a control connection to which a control line or a control channel 91 is connected.
  • the inlet 95 of the lowering brake valve 90 is fluidly connected to the first working chamber 48 via the also referred to as working channel fluid channel 24.1 and the outlet 96 is fluidly connected to the connection channel 86.
  • the inlet 95 of the lowering brake valve 90 to the second working chamber 49 fluidly connected via the also referred to as working channel fluid channel 24.2 and the outlet 96 is fluidly connected to the connection channel 87.
  • a check valve 92 Fluidly connected, which blocks a flow of the pressure medium from the inlet 95 to the outlet 96, but allows in the opposite direction.
  • a locking member 93 may be used, for example, a ball.
  • the respective lowering brake valve 90 can be acted upon by the spring force of a spring 94, which counteracts the force exerted by the pressure medium via the control channel 91, 191 force.
  • the passageway between the inlet 95 and the outlet 96 of the lowering brake valve 90 is when the control channel 91 is not acted upon by pressure medium or is depressurized, shut off, so that possibly at the inlet 95 under pressure pressure medium the Senkbrems valve 90 can not happen.
  • the lowering brake valve can be used as a load-holding lowering brake valve. Because in the closed position of the valve 90, the piston 22 can not lower further. In this way, optionally, regardless of or in addition to a mechanical locking hydraulic locking can be achieved.
  • the outlet 96 of the respective lowering brake valve 90 is fluidly connected to a fluid passage 107 or 207 which is fluidly connected to the port 86 in the case of the pressure-lockable lock cylinder 20 and fluidly connected to the port 87 in the case of the lock-lock cylinder 120 ,
  • the pressure-lockable locking cylinder 20 can be effected by means of the load-holding lowering brake valve or the lowering brake valve 90 or causes when pressurizing the piston 22 on its second side 23.2 with the located in the second working chamber 49 Pressure fluid to form a working pressure, which causes a displacement of the piston 22 in the retraction direction 32, simultaneously acting in the first working chamber 48 on the first side 23.1 of the piston 22 by the pressure medium in the first working chamber 48 applied back pressure.
  • the counterpressure acting in the first working chamber 48 is kept at pressure values, which are always lower than the working pressure in the second working chamber, by means of the lowering brake valve 90 during the pressurization of the second working chamber 49 and consequently during retraction of the piston 22 in the retraction direction 32 49 are, so that at the retracting or lowering movement the piston 22 in the retraction 32, a controlled deceleration of the piston 22 in the retraction 32 is effected. As a result, an uncontrolled advance of the piston 22 in the lowering or retraction direction 32 can be avoided.
  • lockable on train locking cylinder 120 can be effected with the help of the load-holding lowering brake valve or the lowering brake valve 90 or causes when pressurizing the piston 22 on its first side 23.1 with the located in the first working chamber 48 Pressure fluid with the formation of a working pressure, which causes a displacement of the piston 22 in the extension direction 32, simultaneously acting in the second working chamber 49 on the second side 23.2 of the piston 22 by a pressure medium in the second working chamber 49 applied back pressure.
  • the counterpressure acting in the second working chamber 49 is maintained at pressure values, which are always lower than the working pressure in the first working chamber, by means of the lowering brake valve 90 during the pressurization of the first working chamber 48 and consequently during the extension of the piston 22 in the extension direction 32 48, so that in the extension or lowering movement of the piston 22 in the extension direction 32, a controlled braking of the piston 22 in the extension direction 32 is effected.
  • a controlled braking of the piston 22 in the extension direction 32 is effected.
  • a shuttle valve 104 as a means for Releasing a first passageway between the first fluid channel 46, 146 and the porting channel 86 and, preferably substantially simultaneously, shutting off a second passageway between the first fluid channel 46, 146 and the other porting channel 87 or for releasing the second passageway between the first fluidic channel 46 , 146 and the connection channel 87 and, preferably substantially simultaneously, shut off the first passageway between the fluid channel 46, 146 and the connection channel 86 is arranged.
  • the shuttle valve 104 preferably has only one locking member 105, such as a ball on.
  • connection channel 87 is pressurized, ie serves as a supply channel or is switched
  • the pressure medium can flow via the fluid channel 106 or 197 into the shuttle valve 104, whereby the shuttle valve 104 blocks the passage to the other connection channel 86 and the pressure medium from the shuttle valve 104 in the first fluid passage 46, 146 can flow to act on the fluid sliding bearing 45, 145.
  • connection channel 86 is pressurized, ie serves as a flow channel or is connected
  • the pressure medium via the fluid channel 97 and 206 in the shuttle valve 104 flow, whereby the shuttle valve 104 blocks the passage to the other port 87 and the Pressure medium from the shuttle valve 104 in turn in the first fluid passage 46, 146 for acting on the fluid sliding bearing 45, 145 can flow.
  • the respective switching or changeover valve which is a 2-2-way valve 98, 198, forms in the case the pressure-lockable lock cylinder 20 is a means for switching off or releasing a passageway as required, and in the case of the lockable lock cylinder 120, provides a means for throttling or releasing a passageway as required.
  • the respective passageway or the respective valve 98, 198 is arranged in the case of the pressure-lockable locking cylinder 20 between the fluid channel 47 and the fluid channel 103, which opens into the second working channel 24.2, and is in the case of lockable on train locking cylinder 120 between the Fluid channel 147 and the fluid channel 203 arranged, which opens into the first working channel 24.1.
  • the respective fluid channel 47, 147 is when the lock-supporting bodies 35, 36; 135, 136 and the clamping cone bodies 53, 54; 153, 154 frictionally abutting each other, compared to the fluid with the fluid bearing 45, 145 fluidly connected fluid channel 46, 146 shut off.
  • the fluid channel 103 is fluidly connected to the second working chamber 49, which is between the piston 22 and a free end 71 of the spindle 30th associated cover 40.1 of the cylinder 21 is arranged.
  • the fluid passage 203 is fluidly connected to the first working chamber 48 disposed between the piston 22 and the cylinder bottom 140 of the cylinder.
  • connection channel 86 For the purpose of extending the piston rod 22.1 of the pressure-lockable latching cylinder 20 in the extension direction 31, the connection channel 86 is subjected to pressure medium. As a result, the pressure medium can flow out through the connection channel 86 and out of it at a branch point, both through the fluid channel 97 fluid-connected to the shuttle valve 104 and through the fluid channel 107 fluid-connected to the lowering brake valve 90 and the check valve 92. The pressure medium in the fluid channel 97 can now flow into the shuttle valve 104, which thereby or pressure-releasing, the passageway to the fluidic with the fluid bearing 45 fluid-connected fluid channel 46, while substantially simultaneously through the locking member 105 of the shuttle valve 104, the passageway to the fluid channel 106th is shut off.
  • the fluid bearing 45 is subjected to pressure medium.
  • the pressure medium via the check valve 93 arranged parallel to the lowering brake valve 90 in the first working channel 24.1 and consequently in the first working chamber 48 flow, which is formed between the neck 72 of the cylinder bottom 20 and the piston 22 and which can form there.
  • the fluid sliding bearing 45 and the first working chamber 48 are acted upon substantially simultaneously with the pressure medium.
  • the first clamping cone body 53 designed as a cone-butt disc 55 with an outer cone 56 lifts off from the second clamping cone body 54, which is designed with an inner cone, in the direction 31 until the first clamping cone -Body 53 abuts the thrust bearing 38. Due to the friction effects occurring at the latest, also in conjunction with the working pressure acting simultaneously in the first working chamber 48, the spindle 30 can rotate so that the piston 22 and consequently the piston rod 22.1 are thereby moved in the extension direction 31 as a result.
  • shut-off valve 98 also another shut-off valve 98 'schematically.
  • this two check valves are provided in the blocking path, of which each check valve blocks a flow of the pressure medium in the direction of the other non-return valve.
  • connection channel 86 In the case of said pressurization of the connection channel 86, the other connection channel 87 is depressurized by means of a suitable means not shown in the figures.
  • a suitable means not shown in the figures.
  • connection channel 87 For the purpose of retracting the piston rod 22.1 of the pressure-lockable locking cylinder 20 in the retraction direction 32 of the connecting channel 87 is acted upon by pressure medium, while the other connection channel 86 is depressurized.
  • the pressure medium can then flow through the connection channel 87 into the fluid channel 106 which is fluidically connected to the shuttle valve 104, so that the blocking element 105 of the shuttle valve 104 thereby or, as a result of pressure, moves from the in FIG. 3 position shown in a passageway between the fluid channel 97 and the fluid channel 46 shut-off position reaches, in which the pressure fluid from the fluid passage 106 through the shuttle valve 104 in the fluid fluid bearing 45 fluidly connected to the fluid channel 46 can flow or flows.
  • check valve 88 ensures that the inflowing through the connection channel 87 pressure medium first applied to the fluid bearing 45 and only after lifting the cone-butt Washer 55, so the first clamping cone body 53, of the second clamping cone body 54 and a consequent creation of a gap or passageway along the opposite locking-cone surfaces 51, 52 of the two clamping cone Body 53, 54, the pressure medium, here via the second working channel 24.2, can flow into the second working chamber 49, to then cause an axial movement of the piston 22 and the piston rod 22.1 in the retraction 31.
  • the shut-off valve 98 is in the in FIG. 3 shown passage position 100. This position is, possibly supported by a pointing away from the fluid channel 47 control channel 102 is reached. Because the connection channel 86 is depressurized, the control channel 99 of the shut-off valve 98, which is fluid-connected to the latter via the fluid channel 97, is then depressurized, so that the shut-off valve 98 in the in FIG. 3 shown passage position 100 remains.
  • the pressure medium in the first working chamber 48 is displaced in the first working channel 24.1 and can flow from there via the lowering brake valve 90 in the connecting channel 86 serving here as a reflux channel.
  • the lowering brake valve 90 in the first working chamber 48 a working pressure in the second working chamber 49 counteracting counter or brake pressure is maintained, which causes the piston 22 and consequently the piston rod 22.1 does not move uncontrolled in the retraction 32 , in particular, can not lead in an uncontrolled manner in the retraction direction 32.
  • the lowering brake valve 90 as in FIG.
  • the lowering brake valve 90 opens a passageway between the first working channel 24.1 and the connecting channel 86 depending on the working pressure acting in the second working channel 24.2 or in the second working chamber 49, namely Preferably proportional to the working pressure, so that with increasing working pressure in the second working chamber 49 by means of the lowering brake valve 90, a corresponding, preferably proportional, increasing back pressure in the first working chamber 48 can be achieved or achieved.
  • connection channel 86 For the purpose of extending the piston rod 22.1 of the lockable on train locking cylinder 20 in the extension direction 32 of the connecting channel 86 is acted upon with pressure medium, while the other connection channel 87 is depressurized.
  • the pressure medium can then flow through the connection channel 86 into the fluid channel 206 which is fluidically connected to the shuttle valve 104, so that the blocking element 105 of the shuttle valve 104 thereby or, as a result of pressure, moves from the in FIG. 4 position shown in the passageway between the fluid passage 206 and the fluidic fluid bearing 145 fluidly connected fluid passage 146 releasing passage position passes while substantially simultaneously the passageway between the fluid passage 197 and the fluid passage 146 is shut off.
  • the pressure medium can thus now flow from the fluid channel 206 via the shuttle valve 104 into and through the fluid channel 206 and pressurize the fluid sliding bearing 145.
  • connection channel 86 Due to the check valve 88 arranged between the connection channel 86 and the first working channel 24.1 parallel to the fluid sliding bearing 145, it is ensured that the pressure medium flowing through the connection channel 86 first acts on the fluid sliding bearing 145 and only after the cone-butt disk has been lifted off 155, ie the first clamping cone body 153, of the second clamping cone body 154 and a Resulting creation of a gap or passageway along the opposite locking-cone surfaces 151, 152 of the two clamping cone body 153, 154, the pressure medium, here via the first working channel 24.1, in the first working chamber 48 can flow to then causing an axial movement of the piston 22 and the piston rod 22.1 in the extension direction 32.
  • the throttle / passage change-over valve 198 which is designed as a 2-way valve, is located in the in FIG. 4 shown passage position 200. This position is, possibly supported by a pointing away from the fluid channel 147 control channel 202 achieved. Because the connection channel 87 is depressurized, the control channel 199 of the valve 198, which is fluidically connected to the latter via the fluid channel 197, is then also depressurized, so that the valve 198 in the in FIG. 4 shown passage position 200 remains.
  • first the fluid sliding bearing 145 is subjected to pressure medium and forcibly only then the first working chamber 48 is supplied or acted upon by the pressure medium, first the rotationally fixed to the spindle 30 first clamping cone body 153 lifted from the second clamping cone body 154, so that then a rotation of the spindle 30 about its axis of rotation 33 relative to the cylinder 21 is possible, and only then can the pressure medium through a gap or passageway between the opposite locking cone Surfaces 151, 152 of the two clamping cone bodies 153, 154 flow into the first working chamber 48 in order to effect an axial movement of the piston 22 and consequently of the piston rod 22.1 in the extension direction 32.
  • the pressure medium in the second working chamber 49 is displaced into the second working channel 24.2 and can flow from there via the lowering brake valve 90 into the connection channel 87 serving here as a return flow channel.
  • the lowering brake valve 90 in the second working chamber 49 a working pressure in the first working chamber 48 counteracting counter or brake pressure is maintained, which causes the piston 22 and consequently the piston rod 22.1 does not move uncontrolled in the extension 32 , in particular not uncontrolled in the extension direction 32 can lead.
  • the lowering brake valve 90 as in FIG.
  • the lowering brake valve 90 opens a passageway between the second working channel 24.2 and the connecting channel 87 depending on the operating pressure acting in the first working channel 24.1 or in the first working chamber 48, preferably proportional to the working pressure, so that with increasing working pressure in the first working chamber 48 with the aid of the lowering brake valve 90, a corresponding, preferably proportional, increasing back pressure in the second working chamber 49 can be achieved or achieved.
  • connection channel 87 For the purpose of retracting the piston rod 22. 1 of the lockable latch lock cylinder 20 in the retraction direction 31, the connection channel 87 is subjected to pressure medium. As a result, the pressure medium can flow out through the connection channel 87 and at a branch thereof, both through the fluid channel 197 fluid-connected to the shuttle valve 104 and through the fluid channel 207 fluid-connected to the lowering brake valve 90 and the check valve 92. The pressure medium in the fluid channel 197 can now flow into the shuttle valve 104, which thereby or pressure-releasing, the passageway to the fluid with the fluid bearing 145 fluid-connected fluid channel 146, while substantially simultaneously through the locking member 105 of the shuttle valve 104, the passageway to the fluid passage 206th is shut off.
  • the fluid bearing 145 is pressurized with pressure medium.
  • the pressure medium can flow via the check valve 93 arranged parallel to the lowering brake valve 90 into the second working channel 24.2 and consequently into the second working chamber 49 which is formed between the cylinder cover 40.1 and the piston 22 or which can form there , In this way, therefore, the fluid sliding bearing 145 and the second working chamber 49 are acted upon substantially simultaneously with the pressure medium.
  • the first clamping cone body 153 configured as a cone-butt disk 155 with an outer cone 156 comes off the second clamping cone body 154, which is designed with an inner cone, in the direction 31 until the first clamping cone Body 153 abuts the thrust bearing 138. Due to the friction effects occurring at the latest, also in conjunction with the simultaneously acting in the second working chamber 49 working pressure can the spindle 30 rotate so that then conditionally the piston 22 and consequently the piston rod 22.1 are moved in the extension direction 31.
  • connection channel 87 During said pressurization of the connection channel 87 with pressure medium, the other connection channel 88 is depressurized by means of a suitable means not shown in the figures.
  • a suitable means not shown in the figures.
  • the invention may also be summarized as follows:
  • the invention relates to a locking cylinder 20, 120 with a cylinder 21 and a relative to this by means of a pressure medium in the axial direction 59 movable and non-rotatably connected to the cylinder piston 22.
  • the piston 22 is provided with a piston thread 26, which forms a non-self-locking Thread 27 with a spindle thread 28 of a spindle 30 is in Engriff, which is rotatable about an axis of rotation 33 relative to the cylinder 21 and slidable in the axial direction relative to the cylinder 21.
  • the spindle 30 is rotationally fixed with a first locking cone surfaces 51, 151 having self-locking first clamping cone body 53; 153, the locking cone surfaces 51, 151 with second locking cone surfaces 52, 152 of a second self-locking clamping cone body 54, 154 are self-locking clamped.
  • the invention also relates to a method for the rotationally fixed frictional locking of a spindle 30 and to a method for unlocking a rotatably and frictionally locked spindle 30.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Braking Arrangements (AREA)
  • Clamps And Clips (AREA)

Claims (13)

  1. Vérin de verrouillage (20, 120) avec un cylindre (21) et un piston (22), qui peut être déplacé, à l'aide d'un fluide sous pression fluide introduit d'un côté (23.1) du piston (22) par l'intermédiaire d'un canal de travail (24.1) ou des deux côtés (23.1, 23.2) du piston (22) par l'intermédiaire de canaux de travail (24.1, 24.2) correspondant à ces côtés (23.1, 23.2), de manière parallèle à l'axe longitudinal (25) du cylindre (21) dans une première direction (31) et dans une deuxième direction (32) opposée à la première direction (31), et qui est muni d'un filetage de piston (26) qui est en engrènement, en formant un filetage non autobloquant (27), avec le filetage (28) d'une tige (30) verrouillable automatiquement par la gravité, qui est rotative par rapport au cylindre (21) autour d'un axe de rotation (33) parallèle à l'axe longitudinal (25) du cylindre (21) et coulissant axialement par rapport au cylindre (21) dans la direction axiale (59), et une première chambre de travail (48, 49) correspondant à un premier côté (23.1, 23.2) du piston (22) et étant disposée, vue dans la direction (32) d'un mouvement axial du piston (22) parallèle à l'axe longitudinal du piston (22), parallèle à l'axe longitudinal (25) du cylindre (21) ou parallèle à l'axe de rotation (33) de la tige (30), derrière ou après le piston (22), et une deuxième chambre de travail (49, 48) correspondant à un deuxième côté (23.2 ; 23.1) du piston (22) et étant disposé, dans la direction (32) mentionnée, avant le piston (22), et au moins deux corps de support de verrouillage (35, 36 ; 135, 136) pouvant être mis en engrènement de verrouillage mutuel par friction étant prévus, qui sont conçus pour verrouiller la tige (30) par friction contre une rotation autour de son axe de rotation (33) et pour absorber les forces axiales qui agissent dans la deuxième direction (32) sur la tige (30), au moins un premier corps de support de verrouillage (35 ; 135) des corps de support de verrouillage (35, 36 ; 135, 136) étant relié de manière solidaire en rotation avec la tige (30), et au moins un deuxième corps de support de verrouillage (36 ; 136) des corps de support de verrouillage (35, 36 ; 135, 136) étant relié de manière solidaire en rotation avec le cylindre (21), et la tige (30) étant logée sur au moins deux paliers axiaux (38, 39 ; 138, 139), le premier palier axial (38 ;138) étant conçu pour absorber les forces axiales qui agissent dans la première direction (31) sur la tige (30) et un deuxième palier axial (39 ; 139) étant conçu pour absorber les forces axiales qui agissent dans la deuxième direction (32) sur la tige (30), et la tige (30) étant relié ou constitué d'un première corps de palier (41 ; 141), qui présente une première surface de palier (43, 143), située en face d'une deuxième surface de palier (44, 144) d'un deuxième corps de palier (42 ; 142) relié de manière solidaire en rotation avec le cylindre (21), et la première surface de palier (43 ; 143) du premier corps de palier (41 ; 141) et la deuxième surface de palier (44, 144) du deuxième corps de palier (42 ; 142) formant le deuxième palier axial (39 ; 139), qui est conçu comme un palier lisse à fluide (45, 145) pouvant être alimenté par l'intermédiaire d'un premier canal de fluide (46 ; 146) avec un fluide sous pression fluide,
    caractérisé en ce que
    le premier corps de support de verrouillage (35 ; 135) est conçu comme un premier corps conique de blocage (53, 153) autobloquant comprenant des premières surfaces coniques de verrouillage (51 ; 151) et en ce que le deuxième corps de support de verrouillage (36 ; 136) étant conçu comme un deuxième corps conique de blocage (54 ; 154) autobloquant comprenant des deuxièmes surfaces coniques de verrouillage (52 ; 152), et les surfaces coniques de verrouillage (51, 52 ; 151, 152) des corps coniques de blocage (53, 54 ; 153, 154) peuvent être coincées de manière autobloquante entre elles, et, entre un premier canal de travail (24.1, 24.2) relié de manière fluidique avec la première chambre de travail (48, 49) et un deuxième canal de fluide (107, 86 ; 207, 87), se trouve un élément (90) de limitation de la pression et/ou du débit volumique du fluide sous pression à travers ou sur un trajet entre le premier canal de travail (24.1, 24.2) et le deuxième canal de fluide (107, 86 ; 207, 87) en fonction de la pression dans un deuxième canal de travail (24.2, 24.1) relié de manière fluidique à la deuxième chambre de travail (49, 48), et l'élément (90) étant conçu comme une soupape de freinage de descente ou une soupape de maintien de la charge (90) couplée avec un canal de commande (91) relié de manière fluidique avec la deuxième chambre de travail (49, 48) pour la commande ou la régulation d'une contre-pression dans la première chambre de travail (48, 49) qui agit contre la pression dans la deuxième chambre de travail (49, 48) .
  2. Vérin de verrouillage selon la revendication 1, caractérisé en ce que le premier corps conique de blocage (53 ; 153) est logé au moins partiellement dans un évidement (75 ; 175), plus particulièrement dans une chambre (75 ; 175) du cylindre (21), qui est limitée d'un côté par un fond (40) du cylindre (21) et de l'autre côté par un épaulement (72 ; 172), de préférence relié ou réalisé d'une seule pièce avec le cylindre (21), plus particulièrement s'étendant radialement et transversalement par rapport à l'axe longitudinal (25) du cylindre (21).
  3. Vérin de verrouillage selon la revendication 2, caractérisé en ce que l'évidement (75 ; 175) est étanchéifié à l'aide d'un joint d'étanchéité (76) par rapport au piston (22) ou par rapport à une première chambre de travail (48), qui est formée entre le cylindre (21) et le piston (22) et limitée par le côté (23.1) du piston (22) orienté vers le premier corps conique de blocage (53 ; 153), le cas échéant également par le deuxième corps de palier (142) et/ou par l'épaulement (72 ; 172) et dans laquelle débouche le canal de travail (24.1).
  4. Vérin de verrouillage selon l'une des revendications 1 à 3, caractérisé en ce que le palier lisse à fluide (45 ; 145) est alimenté, pendant un mouvement du piston (22) aussi bien dans la première direction (31) que dans la deuxième direction (32) et/ou pendant une rotation de la tige (30) autour de son axe de rotation (33), de préférence également au cours ou pendant l'arrêt du piston (22), plus particulièrement également dans une position d'arrêt du piston (22), avec le fluide sous pression fluide de façon à ce que les corps de support de verrouillage (53, 54 ; 153, 154) sont détachés l'un de l'autre, plus particulièrement soulevés l'un par rapport à l'autre de façon à ce que leurs surfaces coniques de verrouillage (51, 52 ; 151, 152) ne se touchent pas.
  5. Vérin de verrouillage selon l'une des revendications 1 à 4, caractérisé en ce que, dans un boîtier, de préférence dans des boîtiers d'extrémité situés au niveau des paliers axiaux (38, 39 ; 138, 139) et/ou d'un fond (40) du cylindre (21) ou dans le fond du cylindre (40), se trouvent des canaux de fluides (46, 146 ; 91, 191 ; 97, 197 ; 99, 199 ; 103, 203 ; 106, 206) et des organes de commande et/ou de régulation (108, 208 ; 88 ; 90 ; 98, 98', 198 ; 104) constituant une unité de commande (85, 185) entre des conduites de raccordement ou des alésages (86, 87) pour une alimentation ou une évacuation alternative du fluide sous pression et des canaux de fluides (24.1, 24.2) vers des chambres de travail (48, 49) prévues des deux côtés du piston (22) et vers le palier lisse à fluide (45, 145).
  6. Vérin de verrouillage selon l'une des revendications précédentes, caractérisé en ce que, entre un canal de fluide (46, 146) relié de manière fluidique avec le palier lisse à fluide (45, 145) et deux canaux de raccordement (86, 87) servant alternativement de canal aller ou de canal retour, se trouve un élément (104) pour la libération d'un premier trajet entre le canal de fluide (46, 146) et un premier canal de raccordement (86) des canaux de raccordement (86, 87) et pour le blocage, de préférence essentiellement simultané, d'un deuxième trajet entre le canal de fluide (46, 146) et un deuxième canal de raccordement (87) des canaux de raccordement (86, 87) ou pour la libération du deuxième trajet entre le canal de fluide (46, 146) et le deuxième canal de raccordement (87) et pour le blocage, de préférence essentiellement simultané, du premier trajet entre le canal de fluide (46, 146) et le premier canal de raccordement (86).
  7. Vérin de verrouillage selon l'une des revendications précédentes, caractérisé en ce que, entre un premier canal de fluide (47, 147), qui, lorsque les corps de support de verrouillage (35, 36 ; 135, 136) ou les corps coniques de blocage (53, 54 ; 153, 154) sont bloqués entre eux, est bloqué par rapport au canal de fluide (46, 146) relié de manière fluidique au palier lisse à fluide (45, 145) et qui, lorsque les corps de support de verrouillage (35, 36 ; 135, 136) ou les corps coniques de blocage (53, 54 ; 153, 154) sont soulevés l'un par rapport à l'autre, est relié de manière fluidique avec le canal de fluide (46, 146), et un deuxième canal de fluide (103, 24.2 ; 203, 24.1), relié de manière fluidique avec une ou la chambre de travail (49, 48), se trouve un élément (98, 98' ; 198) pour bloquer ou libérer, le cas échéant, un trajet entre le premier canal de fluide (47, 147) et le deuxième canal de fluide (103, 24.2 ; 203, 24.1).
  8. Procédé de verrouillage par friction de la tige (30) rotative autour de son axe de rotation (33) du vérin de verrouillage (20, 120) présentant au moins les caractéristiques des revendications 1 à 7 contre une rotation autour de l'axe de rotation (33) par rapport au cylindre (21), caractérisé en ce qu'au moins un des corps de support de verrouillage (35 ; 135) est déplacé d'une position de déverrouillage permettant une rotation de la tige (30) autour de son axe de rotation (33) par rapport au cylindre (21) vers une position de verrouillage dans laquelle les corps de support de verrouillage (35, 36 ; 135, 136) sont bloqués de manière solidaire en rotation par friction et bloqués entre eux de manière autobloquante de façon à ce qu'ils puissent être déplacés dans la position de déverrouillage uniquement en exerçant des forces supprimant le blocage.
  9. Procédé de déverrouillage de la tige (30) verrouillée de manière solidaire en rotation et par friction ainsi que de manière automatique contre une rotation autour de son axe de rotation (33) par rapport au cylindre (21) du vérin de verrouillage (20, 120) présentant les caractéristiques d'au moins une des revendications 1 à 7, la tige (30) étant verrouillée, dans l'état verrouillé, à l'aide des corps de support de verrouillage (35, 36 ;135, 136) par friction contre une rotation autour de son axe de rotation (33) par rapport au cylindre (21), les corps de support de verrouillage (35, 36 ; 135, 136) absorbant les forces axiales agissant dans la deuxième direction sur la tige (30) et les corps de support de verrouillage (35, 36 ; 135, 136) pouvant être déplacés vers une position de déverrouillage dans laquelle la tige (30) est rotative autour de son axe de rotation (33) par rapport au cylindre (21),
    caractérisé en ce qu'au moins un des corps de support de verrouillage (35, 135) peut être déplacé d'une position de verrouillage, dans laquelle les corps de support de verrouillage (35, 36 ; 135, 136) sont bloqués de manière solidaire en rotation par friction et bloqués entre eux de manière autobloquante de façon à ce qu'ils ne puissent être déplacés vers la position de déverrouillage permettant une rotation de la tige (30) autour de son axe de rotation (33) par rapport au cylindre (21), vers la position de déverrouillage uniquement en exerçant des forces supprimant le blocage.
  10. Procédé selon la revendication 9, caractérisé en ce que les corps de support de verrouillage (35, 36 ; 135, 136) sont déplacés de la position de verrouillage, dans laquelle ils sont bloqués de manière autobloquante entre eux par friction, par une alimentation du palier lisse à fluide (45 ; 145) avec le fluide sous pression fluide vers une position de déverrouillage permettant une rotation de la tige (30) autour de son axe de rotation (33) par rapport au cylindre (21) ou déplacés vers une position de déverrouillage dans laquelle la tige (30) est rotative essentiellement librement par rapport au cylindre (21).
  11. Procédé selon la revendication 10, caractérisé en ce que les corps de support de verrouillage (35, 36 ; 135, 136) présentant des surfaces coniques de verrouillage (51, 52 ; 151, 152) sont déplacés de la position de verrouillage dans laquelle ils sont bloqués de manière autobloquante entre eux par friction, par une alimentation du palier lisse à fluide (45 ; 145) avec le fluide sous pression fluide, vers une position de soulèvement et de déverrouillage dans laquelle les corps de support de verrouillage (35, 36 ; 135, 136) sont soulevés l'un de l'autre de façon à ce que leurs surfaces coniques de verrouillage (51, 52 ; 151, 152) ne se touchent plus.
  12. Procédé selon au moins une des revendications 9 à 11, caractérisé en ce que, de préférence à l'aide d'un ou du dispositif de commande (85, 185), le palier lisse à fluide (45, 145) est d'abord alimenté avec le fluide sous pression, pour permettre une rotation de la tige (30) autour de son axe de rotation (33) par rapport au cylindre (21) et/ou pour provoquer un soulèvement des corps de support de verrouillage (35, 36 ; 135, 136) ou des corps coniques de blocage (53, 54 ; 153, 154) de la position de verrouillage, dans laquelle ils sont bloqués entre eux par friction, vers une position de soulèvement et de déverrouillage dans laquelle les corps de support de verrouillage (35, 36 ; 135, 136) ou les corps coniques de blocage (53, 54 ; 153, 154) sont soulevés l'un de l'autre, de façon à ce que leurs surfaces coniques de verrouillage (51, 52) ne se touchent pas au moins partiellement et de façon à ce que le fluide sous pression soit ensuite introduit dans une chambre de travail (48, 49), qui correspond à un côté (23.1, 23.2) du piston (22), de préférence limitée par celui-ci, pour permettre, soutenir ou provoquer un mouvement du piston (22) dans une direction axiale (59) parallèle à l'axe longitudinal (25) du cylindre (21) ou parallèle à l'axe de rotation (33) de la tige (30).
  13. Procédé selon la revendication 12, caractérisé en ce que le palier lisse à fluide (45, 145) est d'abord alimenté par l'intermédiaire d'un ou du canal de fluide (46, 146) avec le fluide sous pression, ce qui provoque un soulèvement des corps de support de verrouillage (35, 36 ; 135, 136) ou des corps coniques de blocage (53, 54 ; 153, 154) de la position de verrouillage dans laquelle ils sont bloqués antre eux par friction, vers une position de soulèvement et de déverrouillage dans laquelle les corps de support de verrouillage (35, 36 ; 135, 136) ou les corps coniques de blocage (53, 54 ; 153, 154) sont soulevés au moins partiellement l'un de l'autre, de façon à ce que leurs surfaces coniques de verrouillage (51, 52) ne se touchent pas au moins partiellement et un trajet est ainsi formé entre et le long des surfaces coniques de verrouillage (51, 52) situées l'une en face de l'autre dans l'état soulevé, qui est relié de manière fluidique avec un ou le canal de fluide (47, 147), qui est relié de manière fluidique avec la chambre de travail (48, 49), de façon à ce que le piston (22) soit alimenté avec le fluide sous pression s'écoulant à travers le canal de fluide (47, 147) vers la chambre de travail (48, 49) afin de permettre, de soutenir ou de provoquer un mouvement du piston (22) dans une direction axiale (59) parallèle à l'axe longitudinal (25) du cylindre (21) ou parallèle à l'axe de rotation (33) de la tige (30).
EP12197151.9A 2009-04-09 2010-03-17 Vérin de verrouillage et procédés de verrouillage et de déverrouillage correspondants Active EP2570679B1 (fr)

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DE102009017212 2009-04-09
EP10156720.4A EP2239470B1 (fr) 2009-04-09 2010-03-17 Vérin de verrouillage et procédé de verrouillage et de déverrouillage d'un vérin de verrouillage

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EP12197159.2A Active EP2570680B1 (fr) 2009-04-09 2010-03-17 Procédé de déverrouillage d'un cylindre de verrouillage
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EP10156720.4A Active EP2239470B1 (fr) 2009-04-09 2010-03-17 Vérin de verrouillage et procédé de verrouillage et de déverrouillage d'un vérin de verrouillage

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AT516280B1 (de) * 2015-02-06 2016-04-15 Neuson Hydrotec Gmbh Kolben-Zylindereinheit mit Stellring
DE102015108829A1 (de) 2015-06-03 2016-12-08 Neumeister Hydraulik Gmbh Doppeltwirkender Verriegelungszylinder und Verfahren zum Betreiben eines doppeltwirkenden Verriegelungszylinders
CN108679038A (zh) * 2018-07-13 2018-10-19 武汉科技大学 一种新型机械自锁液压执行器
CN109470442B (zh) * 2018-12-28 2023-11-21 中国地震局工程力学研究所 振动锁紧装置及振动台
CN110356545A (zh) * 2019-08-21 2019-10-22 成都弗格森液压机电有限公司 一种无人机起落架收放用锁紧机构
CN114517809B (zh) * 2022-02-23 2023-09-12 中国工程物理研究院机械制造工艺研究所 一种基于藕状定向多孔节流的气体静压轴承

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DE102010015996A1 (de) 2010-10-14
ES2437762T3 (es) 2014-01-14
EP2570680A1 (fr) 2013-03-20
EP2570680B1 (fr) 2013-09-18
EP2239470A3 (fr) 2012-06-13
EP2570679A1 (fr) 2013-03-20
PL2239470T3 (pl) 2013-11-29
EP2239470A2 (fr) 2010-10-13
EP2239470B1 (fr) 2013-07-03
PL2570680T3 (pl) 2014-02-28
ES2437763T3 (es) 2014-01-14
PL2570679T3 (pl) 2014-02-28
ES2429341T3 (es) 2013-11-14

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