EP2239470B1 - Vérin de verrouillage et procédé de verrouillage et de déverrouillage d'un vérin de verrouillage - Google Patents

Vérin de verrouillage et procédé de verrouillage et de déverrouillage d'un vérin de verrouillage Download PDF

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Publication number
EP2239470B1
EP2239470B1 EP10156720.4A EP10156720A EP2239470B1 EP 2239470 B1 EP2239470 B1 EP 2239470B1 EP 10156720 A EP10156720 A EP 10156720A EP 2239470 B1 EP2239470 B1 EP 2239470B1
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EP
European Patent Office
Prior art keywords
locking
cylinder
spindle
fluid
piston
Prior art date
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Application number
EP10156720.4A
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German (de)
English (en)
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EP2239470A3 (fr
EP2239470A2 (fr
Inventor
Walter Neumeister
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Neumeister Hydraulik GmbH
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Neumeister Hydraulik GmbH
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Application filed by Neumeister Hydraulik GmbH filed Critical Neumeister Hydraulik GmbH
Priority to PL10156720T priority Critical patent/PL2239470T3/pl
Priority to EP12197159.2A priority patent/EP2570680B1/fr
Priority to EP12197151.9A priority patent/EP2570679B1/fr
Priority to PL12197151T priority patent/PL2570679T3/pl
Priority to PL12197159T priority patent/PL2570680T3/pl
Publication of EP2239470A2 publication Critical patent/EP2239470A2/fr
Publication of EP2239470A3 publication Critical patent/EP2239470A3/fr
Application granted granted Critical
Publication of EP2239470B1 publication Critical patent/EP2239470B1/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 , of the DE 3629677 A1 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 together with the Spindle are lifted in the axial direction using a practicable via a fluid pressure medium pressure from the other friction ring, so that then the spindle about its axis of rotation relative to the cylinder is rotatable, whereby then the 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 rotating cone with outer cone, which can be braked via a rotatably fixed to the cylinder and used as a lifting brake, axially displaceable against the spring force of a spring, conical brake piston with inner cone.
  • 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 bearing surface can form a fluid fluid pressure applied hydrostatic fluid bearings.
  • 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.
  • a spindle rotatable about a spindle rotation axis carries a conical brake disc which can be braked under the action of the weight of a load to be lifted on a conical brake drum of a cylinder.
  • a pressure medium in a working pressure chamber under a rotatably connected to the spindle via a threaded coupling piston of the cylinder, the piston can be moved in the axial direction.
  • This axial movement of the piston initially achieves limited axial movement of the spindle to lift the brake disk from the brake drum, whereupon continued piston movement in the axial direction merely causes rotation of the spindle due to its threaded coupling with the piston.
  • This construction comprises a separate cylinder release device in the form of a further cylinder and a further piston, which is attached to an end of the spindle projecting downwards out of the cylinder.
  • This cylinder release device serves exclusively to release the brake disk from the brake drum when lowering of the piston with the load is desired in order, under the action of the load, to rotate the spindle while simultaneously reducing the pressure in the cylinder allow, so that the piston can sink under simultaneous rotation of the spindle under the load.
  • This construction is relatively space consuming and their reliability is limited.
  • the invention relates to a locking cylinder having a cylinder and a piston, which by means of a one side of the piston via a working channel or both sides of the piston via these pages associated working channels fluid pressure fluid can be fed 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, forming a non-self-locking thread with a spindle thread of a frictionally, ie non-positively by friction and, preferably exclusively, due to gravity, in particular by a load acting on the piston, automatically or automatically, preferably without drive, in particular without the action or support of energy storage, such as springs, lockable spindle engaged which is rotatable relative to the cylinder about an axis of rotation arranged parallel to the longitudinal axis of the cylinder and preferably axially displaceable relative to the cylinder in the axial direction or parallel to its axis of rotation, at least two locking elements which can be converted into
  • Support body are provided, which are intended to lock the spindle frictionally against rotation about its axis of rotation and to take in the second direction acting on the spindle axial forces, preferably such that the spindle in the locked Z
  • At least one first locking-supporting body of the locking-supporting body rotatably, preferably rigidly connected to the spindle or is attached to the spindle and at least one second locking support body of the locking support body rotationally fixed, preferably rigidly connected to the cylinder or is attached to the cylinder, and wherein the spindle is mounted on at least two, preferably axially spaced, thrust bearings, of which a first Axial bearing is intended to receive in the first direction acting on the spindle axial forces, and of which a second thrust bearing is intended to axial forces acting in the second direction on the spindle and wherein the spindle is connected or formed with a first bearing body, which has a first bearing surface, which is a second bearing surface of a non-rotatable, preferably rigid, connected to
  • 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 cylinder preferably one or the cylinder base of the cylinder, received, on the one hand by a or the cylinder bottom of the cylinder and on the other hand by a, preferably integrally connected to the cylinder or produced, in particular radially and transverse to the longitudinal axis of the cylinder or to the axis of rotation of the spindle extending, is arranged between the first cone-clamping body and the piston approach is limited, still simpler and comparatively space-saving and robust construction an advantageous basis for a particularly preferred regulation or control of the locking and / or lift-off process are created.
  • first clamping cone body is at least partially in a recess, in particular a chamber
  • the cylinder preferably one or the cylinder base of the cylinder, added, in which first fluid channel opens on a first side of the first clamping cone body, which is associated with its inclined to the rotational axis of the spindle first locking cone surfaces.
  • the 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.
  • the recess is sealed by a seal against the piston or against one or the working chamber, which is formed between the cylinder and the piston and the side facing the first clamping cone body side of the piston, possibly also From the second bearing body and / or from the approach is limited and opens into the working channel, the operability and reliability can be achieved or increased to a particular extent.
  • 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 of the spindle relative to a rotation about its axis of rotation relative to the cylinder achievable or achieved, so even without that driving or load-related forces would be initiated 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.
  • 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 prefferably be designed as a first clamping cone body having self-locking or self-locking acting as a first locking cone surface and for the second locking support body to be formed. 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 is formed with or as an outer cone 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 in the region or on which in the direction of the piston towards or away from the cylinder bottom side facing away are arranged and / or in that the first locking cone surfaces of the first clamping cone body are arranged in the region or on the side thereof pointing in the direction of the piston or away from the cylinder base, and in that the second locking conical surfaces of the second clamping cone Cone body in the region or on which in the direction away from the piston or to the cylinder bottom side facing 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.
  • 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 immediately adjacent to the first locking cone surfaces of the first clamping cone body opens into the recess.
  • 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 operability and the reliability can be further increased to a particular extent when the first fluid channel and / or the second fluid channel with respect to a or the working chamber, which is formed between the cylinder and the piston and 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 in 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.
  • This can be both functional Aspects as well as safety aspects to realize a particularly accurate and particularly secure locking locking cylinder.
  • the first clamping cone body and the second clamping cone body or the at least partially limited by this recess may 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, so in a parallel to the axis of rotation of the spindle extending projection direction, is greater as a spindle surface of the spindle which is located on the side of the seal which is sealed by the seal from the recess at least partially receiving the first clamping cone body and which is in, preferably directly or directly, fluid communication with a working chamber or chambers, is preferably acted upon with the in one or the working chamber pressure medium, which is formed between the cylinder and the piston and of the first clamping cone body facing 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.
  • An axial bearing of the rotatable spindle suitable for many or even all expected operating states, i. H. in any phase and in any position, even in the event of a failure of the hydraulics or in the event of leakage, can be achieved if the fluid sliding bearing during a movement of the piston in both the first direction and in the second direction and / or during a
  • any 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, with the fluid pressure medium is acted upon or is such that the clamping cone body from each other are solved, 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.
  • the first self-locking locked clamping cone body at least so far in the axial direction to solve each other, that in principle a rotation of the spindle relative to the cylinder and thus therefore an unlocking of the spindle can be achieved while still be maintained a frictional connection between the corresponding clamping cone bodies or can be. Consequently, therefore, the friction between the corresponding clamping cone bodies can also be stepped or continuously regulated.
  • a preferred embodiment of the invention can be provided that in a housing, preferably in a in the region of the thrust bearing and / or a 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 regulating devices between connecting lines or holes for an alternate supply or discharge of the pressure medium and fluid passages or conduits to working chambers provided on both sides of the piston and to the fluid slide bearing.
  • 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 limiting the pressure and / or volume flow of the pressure medium via or in a passageway between the first working channel and the second fluid channel depending on the pressure in a second working channel fluidly connected to a second working chamber is arranged, wherein the first working chamber assigned to a first side of the piston, preferably limited 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 considered behind or is arranged after the piston, and wherein the second working chamber associated with, preferably delimited by a second side of the piston and, viewed in the said direction, is arranged in front of the piston.
  • the pressure of the pressure medium in a provided on the other side of the piston working chamber can be controlled or regulated so that always a sufficient back pressure is formed, so that an uncontrolled axial movement, in particular an uncontrolled Voreilen , The piston and consequently the piston rod and the load can be avoided or prevented.
  • the said means may be a lowering brake valve or a load-holding lowering brake valve.
  • This can preferably be coupled or fluid-connected to a control channel which is fluid-connected to the second working chamber for controlling or regulating a counterpressure acting counter to the pressure in the second working chamber in the first working chamber. This can cause an uncontrolled axial movement, in particular, a lead, the piston in one or the, in particular second, direction are avoided or prevented.
  • 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.
  • 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 to 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 features of at least one claim Claims 1 to 7 having locking cylinder against rotation about the axis of rotation relative to the cylinder, wherein at least one of the locking support body from a rotation of the spindle about its axis of rotation relative to the cylinder enabling unlocking position, preferably in one or the axial direction parallel to the axis of rotation of the spindle or transferred to the longitudinal axis of the cylinder, in a locking position, preferably displaced, is in which the locking-support body frictionally locked by friction friction and are clamped together so self-locking that they only under exercise of the Deadlock releasing release forces in the unlocked position can be transferred.
  • a particularly simple and secure locking of the spindle and consequently of the piston relative to the cylinder can be achieved.
  • 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 Unlocking position can be transferred, in which the spindle about its axis of rotation relative to the cylinder is substantially unhindered 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 lockup support body is in the second direction Take on the spindle acting axial forces, preferably such that the spindle is secured in the locked state against movement in the second direction is supported on the cylinder, wherein the locking-supporting body can be converted into an unlocking position in which the spindle about its axis of rotation is rotatable relative to the cylinder, and wherein at least one of the locking-support body from a locking position in which the
  • 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, in a rotation of the spindle about its axis of rotation relative to the cylinder enabling unlocking position to be transferred or transferred to an unlocked position in which the spindle is substantially free to rotate relative to the cylinder.
  • the locking-cone surfaces having locking-support body from 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 medium under increased 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, 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 Lock support body from each other are lifted 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 to effect or whereby a movement of the piston in the axial direction allows, is supported or effected.
  • a procedure has particular advantages when the piston or the piston rod is
  • the fluid sliding bearing can first be provided via a fluid channel or supply channel are acted upon by the pressure means, whereby 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, 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 a passageway or gap between and along the in the off-hook condition lying locking cone surfaces is opened or formed, which is fluidly connected to one or the fluid channel or discharge channel, which is fluidly connected via one or the working channel, with the working chamber or is, so that the piston with the through the fluid or discharge channel is supplied in the working chamber supplied or flowing pressure medium, ent neither to enable nor to cause a 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, or whereby a lifting of the locking-support body
  • 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 attached 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 conical surfaces of the clamping cone body, in particular of the clamping double-cone body, with the axis of rotation of the spindle or with the longitudinal axis of the cylinder may form a different large inclination angle or preferably an equal tilt angle
  • 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 rotationally fixed to the cylinder 21 mounted piston 22.
  • the piston 22 is sealed from the cylinder inner wall of the cylinder 21 by a ring seal 37 and is on its in the direction of the longitudinal axis 25th 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 to allow a pressure fluid assisted movement of the piston 22 in a first direction 31 or in a second direction 32.
  • a fluid, in particular hydraulic, pressure medium preferably oil
  • the pressure medium can via a first Working channel 24.1 on the cylinder bottom 40 facing side 23.1 of the piston 22 are fed into a first working chamber 48 in order to achieve a movement of the piston 22 along the cylinder 21 in the second direction 32 can.
  • 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 coaxially to 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 also has a Piston thread 26 designated internal thread on.
  • 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 off.
  • 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 rotatable about a parallel to the longitudinal axis 25 of the cylinder 21 arranged rotational axis 33 relative to the cylinder 21 and is also only slightly axially displaceable relative to the cylinder 21 in the axial direction 59 and 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 solely by gravity, in particular by acting on the piston 22 load 29, 129, automatically or automatically, without drive and without the action or support of energy stores, such. B. tension or compression springs, lockable.
  • 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 referred to as a second locking cone surface 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 on the opposite, counter-surfaces 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.
  • 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 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 in the axial direction 59 are movable or displaced, that is not in the first direction 31, ie here in one 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 lockable pressure lock cylinder 20 tapers the first clamping cone body 53 conically toward the axis of rotation 33 of the spindle 30 and in the direction away from the piston 22 and to the cylinder bottom 40 of the cylinder 21 out.
  • 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 on page 65 and the second locking-cone surfaces 52 of the rotatably connected to the cylinder 21 second clamping cone body 54 are arranged on its side facing away from the cylinder bottom 40 and toward the piston 66 side 66.
  • 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 of the second bearing body 142 as the, preferably in one piece with the Cylinder 21 is formed or produced, 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 projection 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 to 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 is supplied either first via the first fluid channel 46 and subsequently via the first working channel 24.1 or preferably simultaneously via the first fluid channel 46 and the first working channel 24.1, so that accordingly either first the recess 75 and then the first working chamber 48 is acted upon by pressure medium or by preferably 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 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 drops together with the spindle 30 and rotatably connected to this first clamping cone body 53 due to the gravitational direction, d. H. in the second direction 32, acting load 29 in the second direction 32 from, 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.
  • first connected clamping means Cone body 53 is lifted from the rotatably connected to the cylinder 21 second clamping cone body 54 in a lifting and unlocking position 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 rotate the spindle rotation axis 33 relative to the cylinder 21.
  • 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 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.
  • 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.
  • the piston 22 in the first direction 31 flows pressure fluid 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 to this first clamping cone body 153 decreases due to the gravitational direction, d. H. in the second direction 32, acting load 29 in the second direction 32 from, by the intended small 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 still no jamming of the clamping cone body 153, 154 occurs.
  • 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 non-rotatably connected to the cylinder 21 second clamping cone body 154 in a lifting and unlocking, in of which their locking conical surfaces 151, 152 do not touch, so that then the first clamping cone body 153 and the spindle 30, preferably substantially free, can 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 the spindle 30, together with the first clamping cone, is immediately caused by the acting load 129 Body 153 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 153 at or in the second terminal Cone body 154 self-locking jammed stuck. Then, 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 axial lifting in the axial direction 59, ie in the first direction 31, so that in turn also a double self-inhibition 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 reference may be made in this regard 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 Senkbrems valve or lowering brake valve 90 has an inlet 95, an outlet 96 and a control port on 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, when the control channel 91 is not pressurized, is shut off so that any pressure medium under pressure at the inlet 95 will be the lowering brake 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 with a fluid passage 107 or 207 fluidly connected, which in the case of the pressure-lockable lock cylinder 20 is fluidly connected to the port 86 and which is in the case of the train lockable lock cylinder 120 to the port 87 fluidly connected.
  • 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 in the retraction or lowering movement of the piston 22 in the retraction 32, a controlled braking 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.
  • train lockable locking cylinder 120 can be effected by means of the load-holding lowering brake valve or the Senkbrems valve 90 and is effected when acting on the piston 22 on its first side 23.1 with the in the first working chamber 48 pressure fluid to form a working pressure, which causes a displacement of the piston 22 in the extension direction 32, at the same time in the second working chamber 49 on the second side 23.2 of the piston 22 by a located in the second working chamber 49 Pressure medium applied counter pressure acts.
  • 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 is provided as a means for releasing a first passageway between the first fluid channel 46, 146 and the connection channel 86 and for, preferably substantially simultaneously, shutting off a second passageway between the first fluid channel 46, 146 and the other connection channel 87 or for releasing the second passageway between the first fluid channel 46, 146 and the connection channel 87 and for, preferably substantially simultaneous, blocking of the first passageway between the fluid channel 46, 146 and the connection channel 86 is arranged.
  • the shuttle valve 104 is preferred 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 of the pressure-lockable locking cylinder 20 a means for switching off or releasing a passageway as required or releasable, and forms in Case of train lockable lock cylinder 120 means for throttling or releasing a passageway as required.
  • the respective passageway or the respective valve 98, 198 is in the case of the pressure-lockable locking cylinder 20 between the fluid channel 47 and the fluid channel 103 is arranged, which opens into the second working channel 24.2, and is arranged in the case of train lockable lock cylinder 120 between the fluid channel 147 and the fluid channel 203, 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 in fluid communication with the second working chamber 49, which is arranged between the piston 22 and a cover 40.1 of the cylinder 21 associated with the free end 71 of the spindle 30.
  • 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 can flow via the check valve 93 arranged parallel to the lowering brake valve 90 into the first working channel 24.1 and consequently into the first working chamber 48 formed between the shoulder 72 of the cylinder bottom 20 and the piston 22 can train 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.
  • 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. In this way, when extending the piston rod 22.1 in the extension direction 31 in the Second working chamber 49 located between the piston 22 and the cylinder cover 40.1 pressure fluid via the second working channel 24.2 and viewed in this flow direction before the branch point of the fluid channel 106 of the connection channel 87 check valve 88 flow into and then serve as a return channel connecting channel 87.
  • 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 fluid-connected to the shuttle valve 104, so that thereby or due to pressure, the blocking member 105 of the shuttle valve 104 of 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, ie 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 bodies 53, 54, the pressure medium, here via the second working channel 24.2, in the second working chamber 49 can flow to then cause 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 operating pressure acting in the second working channel 24.2 or in the second working chamber 49, preferably in proportion to the working pressure, so that with increasing working pressure in the second working chamber 49 with the aid 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 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 disc has been lifted off 155, ie the first clamping cone body 153, of the second clamping cone body 154 and a consequent creation of a gap or passageway along the opposing locking cone surfaces 151, 152 of the two clamping cone Body 153, 154, the pressure medium, here via the first working channel 24.1, can flow into the first working chamber 48, to then cause an axial movement of the piston 22 and the piston rod 22.1 in the extension direction 32.
  • valve throttle / passage changeover or changeover valve 198 in the 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.
  • This causes a rotation of the spindle 30 about its axis of rotation 33 relative to the cylinder 21, so that conditionally then the piston rod 22.1 can extend 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 from there via the lowering brake valve 90 in the here serving as a return flow channel Outlet port 87 flow.
  • 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 due to pressure, the passage path to the fluid bearing 145 fluidly connected to the fluid passage 146 releases while substantially simultaneously by the locking member 105 of the shuttle valve 104, the passage to the fluid passage 206 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 working pressure acting simultaneously in the second working chamber 49, the spindle 30 can rotate, so that 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 is in engagement with a spindle thread 28 of a spindle 30, which is rotatable about an axis of rotation 33 relative to the cylinder 21 and displaceable 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 avec un piston (23) adapté pour être déplacé, moyennant un fluide de pression pouvant être amené à un côté (23.1) du piston (22) par un canal (24.1) ou aux deux côtés (23.1, 23.2) du piston (22) par des canaux (24.1, 24.2) associés à ces côtés (23.1, 23.2), dans une première direction (31) parallèle à l'axe longitudinal (25) du cylindre (21) et dans une seconde direction (32) opposée à la première direction (31), et qui est pourvu d'un filetage de piston (26) engrenant, tout en formant un filetage (27) non autobloquant, avec un filetage de broche (28) d'une broche (30) qui est autobloquante par friction et par gravité et 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 déplaçable axialement par rapport au cylindre (21) en direction axiale (59), où sont prévus au moins deux corps de soutien de verrouillage (35, 36 ; 135, 136) adaptés pour pouvoir être engagés l'un avec l'autre par friction et destinés à verrouiller la broche (30) par friction contre une rotation autour de son axe de rotation (33) et à recevoir des contraintes axiales agissant dans la seconde direction sur la broche (30), au moins un premier corps de soutien de verrouillage (35 ; 135) des corps de soutien de verrouillage (35, 36 ;135, 136) étant solidaire en rotation avec la broche (30) et au moins un deuxième corps de soutien de verrouillage (36 ; 136) des corps de soutien de verrouillage (35, 36 ; 135, 136) étant solidaire en rotation avec le cylindre (21), et la broche (30) étant supportée par au moins deux paliers axiaux (38, 39 ; 38, 139) dont un premier palier axial (38 ; 138) est destiné à recevoir des contraintes axiales agissant sur la broche (30) dans la première direction (31) et dont un deuxième palier axial (39 ; 139) est destiné à recevoir des contraintes axiales agissant sur la broche (30) dans la seconde direction (32), la broche (30) étant liée à, ou formée avec, un premier corps de palier (41 ; 141) présentant une première surface de palier (43 ; 143) disposée en regard à une seconde surface de palier (44 ; 144) d'un second corps de palier (42 ; 142) qui est solidaire en rotation avec le cylindre (21), la première surface de palier (43 ; 143) du premier corps de palier (41 ; 141) et la seconde surface de palier (44 ; 144) du second corps de palier (42 ; 142) formant le second palier axial (39 ; 139) qui se présente sous la forme d'un palier à glissement à fluide (45 ; 145) sur lequel peut agir un fluide sous pression amené par un premier canal de fluide (46 ; 146),
    caractérisé en ce que le premier corps de soutien de verrouillage (35 ; 135) est formé comme un premier corps conique de serrage (53 ; 153) présentant des premières surfaces obliques de serrage (51 ; 151) autobloquantes et en ce que le second corps de soutien de verrouillage (36 ; 136) est formé comme un second corps conique de serrage (54 ; 154) présentant des secondes surfaces obliques de serrage (52 ; 152), les surfaces obliques de serrage (51, 52 ; 151, 152) des corps coniques de serrage (53, 54 ; 153, 154) étant adaptées pour pouvoir être serrées l'une contre l'autre de manière autobloquante, le premier corps oblique de serrage (53 ; 153) étant au moins partiellement logé dans un évidement (75 ; 175) du cylindre (21), l'évidement (75 ; 175) étant délimité d'une part par un fond (40) du cylindre (21) et d'autre part par une saillie (72 ; 172) s'étendant radialement et transversalement par rapport à l'axe longitudinal (25) du cylindre (21) et disposée entre le premier corps conique de serrage (53 ; 153) et le piston (22), le premier canal de fluide (46 ; 146) débouchant dans l'évidement (75 ; 175) sur un premier côté (65 ; 165) du premier corps oblique de serrage (53 ; 153), qui est associée aux surfaces obliques de serrage (51 ; 151) inclinées vers l'axe de rotation (33) de la broche (30), et l'évidement (75 ; 175) étant rendu étanche par rapport au piston (22) ou par rapport à une chambre de travail (48) par un joint d'étanchéité (76), la chambre de travail (48) étant formée entre le cylindre (21) et le piston (22) et délimitée par le côté (23.1) du piston (22) orienté vers le corps conique de serrage (53 ; 153) et dans laquelle débouche le canal de travail (24.1).
  2. Vérin de verrouillage selon la revendication 1, caractérisé en ce que le palier à glissement à fluide (45 ; 145) est soumis à l'action du fluide sous pression, lors d'un déplacement du piston (22) aussi bien dans la première direction (31) que dans la seconde direction (32) et/ou lors d'une rotation de la poche (30) autour de son axe de rotation (33), de préférence également lors de la mise en arrêt ou lors de l'arrêt du piston (22), plus particulièrement aussi dans une position d'arrêt du piston (22), de telle sorte que les corps coniques de serrage (53, 54 ; 153, 154) sont desserrés l'un de l'autre, plus particulièrement sont tellement éloignés l'un de l'autre que leur surfaces obliques de serrage (51, 52 ; 151, 152) ne se touchent pas.
  3. Vérin de verrouillage selon la revendication 1 ou 2, caractérisé en ce que des canaux de fluide (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) formant une unité de commande (85, 185) située entre des conduits de raccordement ou de perçage (86, 87) pour une amenée ou un départ en alternance du fluide de pression et des canaux de fluide (24.1, 24.2) vers des chambres de travail (48, 49) situés des deux côtés du piston (22) et vers le palier de glissement à fluide (45, 145) sont disposés dans un boîtier, de préférence dans un boîtier extérieur prévu à proximité des paliers axiaux (38, 39 ; 138, 139) et/ou d'un fond de cylindre (40) du cylindre (21) ou dans le fond de cylindre (40).
  4. Vérin de verrouillage selon l'une des revendications précédentes, caractérisé en ce qu'un moyen (90) pour limiter la pression et/ou le flux du fluide de pression sur ou par un chemin de passage entre le premier canal de travail (24.1, 24.2) et le second canal de fluide (107, 86 ; 207, 87) en fonction de la pression dans un second canal de travail (24.2, 24.1) relié par le fluide à une seconde chambre de travail (49, 48) et disposée entre
    un premier canal de travail (24.1, 24.2) relié par fluide à une première chambre de travail (48, 49) et un second canal de fluide (107, 86 ; 207, 87), plus particulièrement un ou le canal de départ (86, 87), la première chambre de travail (48, 49) étant attribuée à un premier côté (23.1, 23.2) du piston (22), de préférence délimité par celui-ci et disposé dans la direction (32) d'un déplacement axial du piston (22) parallèlement à l'axe longitudinal (25) du cylindre (21) ou parallèlement à l'axe de rotation (33) de la broche (30) considérée derrière ou après le piston (22), et la seconde chambre de travail (49, 48) étant attribuée à un second côté (23.2 ; 23.1) du piston (22), de préférence délimitée par celui-ci, et est disposée dans ladite direction (32) avant le piston (22).
  5. Vérin de verrouillage selon la revendication 4, caractérisé en ce que le moyen (90) se présente sous la forme d'une valve de descente freinée ou d'une valve de descente freinée et de blocage de charge (90) reliée à un canal de commande (91) en communication fluide avec la seconde chambre de travail (49, 48) pour la commande ou la régulation d'une pression opposée à la pression dans la seconde chambre de travail (49, 48) et dans la première chambre de travail (48, 49).
  6. Vérin de verrouillage selon l'une des revendications précédentes, caractérisé en ce que, entre un canal de fluide (46, 146) en communication de fluide avec le palier à glissement à fluide (45, 145) et deux canaux de raccordement (86, 87) servant alternativement comme canal d'arrivée ou comme canal de retour, est disposé un moyen (104) pour, de préférence simultanément, libérer un premier passage entre le canal de fluide (46, 146) et un premier canal de raccordement (86) des canaux de raccordement (86, 87) et bloquer un second passage entre le canal de fluide (46, 146) et un second canal de raccordement (87) des canaux de raccordement (86, 87) ou pour libérer le second passage entre le canal de fluide (46, 146) et le second canal de raccordement (87) et pour bloquer, de préférence essentiellement simultanément, le premier passage 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 soutien de verrouillage (35, 36 ; 135, 136) ou les corps obliques de serrage (53, 54 ; 153, 154) sont engagés l'un dans l'autre, est verrouillé par rapport au canal de fluide (46, 146) en communication fluide avec le palier à glissement à fluide (45, 145), et qui, lorsque les corps de soutien de verrouillage (35, 36 ; 135, 136) ou les corps obliques de serrage (53, 54 ; 153, 154) sont détachés l'un de l'autre, communique en fluide avec le canal de fluide (46, 146), et un second canal de fluide (103, 24.2 ; 203, 24.1) relié en communication de fluide avec une ou la chambre de travail (49, 48), est disposé un moyen (98, 98' ; 198) pour bloquer ou libérer ou pour étrangler ou libérer, en tant que de besoin, un passage entre le premier canal de fluide (47, 147) et le second canal de fluide (103, 24.2 ; 203, 24.1).
  8. Procédé de verrouillage en friction et solidaire en rotation de la broche (30) rotative autour de son axe de rotation (33) du vérin de verrouillage (20, 120) ayant les caractéristiques selon au moins une 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 soutien de verrouillage (35 ; 135) est transféré d'une position de déverrouillage rendant possible une rotation de la broche (30) autour de son axe de rotation (33) par rapport au cylindre (21) vers une position de verrouillage dans laquelle les corps de soutien de verrouillage (35, 36 ; 135, 136) sont en lien l'un avec l'autre par friction et en rotation d'une telle façon qu'elles ne peuvent être transférées dans la position de déverrouillage que par application de forces de déverrouillage débloquant ce lien.
  9. Procédé de déverrouillage de la broche (30) verrouillée par friction et par gravité et verrouillée en rotation contre une rotation autour de son axe de rotation (33) par rapport au cylindre (21) du cylindre de verrouillage (20, 120) ayant des caractéristiques d'au moins une des revendications 1 à 7, la broche (30) étant verrouillée dans l'état verrouillé moyennant les corps de soutien de verrouillage (35, 36 ; 135, 136) par friction contre une rotation autour de son axe (33) par rapport au cylindre (21), les corps de soutien de verrouillage (35, 36 ; 135, 136) recevant des contraintes axiales agissant dans la seconde direction sur la broche (30), et les corps de soutien de verrouillage (35, 36 ; 135, 136) pouvant être déplacés dans une position de déverrouillage dans laquelle la broche peut être mise en rotation autour de son axe de rotation (33) par rapport au cylindre (21), caractérisé par le fait qu'au moins un des corps de soutien de verrouillage (35, 135) est déplacé d'une position de verrouillage dans laquelle les corps de soutien de verrouillage (35, 36 ; 135, 136) sont verrouillés en rotation et de manière autobloquante de façon qu'ils ne peuvent être déplacés vers une position de déverrouillage rendant possible une rotation de la broche (30) autour de son axe de rotation (33) par rapport au cylindre (21) par des forces de déverrouillage débloquant le blocage, vers la position de déverrouillage.
  10. Procédé selon la revendication 9, caractérisé en ce que les corps de soutien de verrouillage (35, 36 ; 135, 136) sont déplacés de la position de verrouillage dans laquelle ils sont bloqués l'un contre l'autre par friction et de manière autobloquante vers une position rendant possible les déblocages par action du fluide sous pression sur le palier de glissage à fluide (45, 145) mettant en rotation la broche (30) autour de son axe de rotation (33) par rapport au cylindre (21) ou dans une position de déverrouillage dans laquelle la broche (30) est libre en rotation par rapport au cylindre (21).
  11. Procédé selon la revendication 10, caractérisé en ce que les corps de soutien de verrouillage (35, 36 ; 135, 136) présentant des surfaces obliques de verrouillage (51, 52 ; 151, 152) sont déplacés de la position de verrouillage vers laquelle ils sont bloqués par friction, dans une position de déverrouillage et de séparation par action du palier à glissement à fluide hydrostatique (45, 145) position dans laquelle les corps de soutien de verrouillage (35, 36 ; 135, 136) sont éloignés l'un de l'autre de façon que leur surface oblique 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), est soumis au fluide de pression d'abord le palier à glissement à fluide (45, 145) afin de rendre possible la rotation de la broche (30) autour de son axe de rotation (33) par rapport au cylindre (21) et/ou pour obtenir un détachement des corps de soutien de verrouillage (35, 36 ; 135, 136) ou des corps coniques de serrage (53, 54 ; 153, 154) de la position de verrouillage dans laquelle ils sont bloqués l'un contre l'autre par friction, dans une position de déverrouillage et de détachement dans laquelle les corps de soutien de verrouillage (35, 36 ; 135, 136) ou les corps coniques de serrage (53, 54 ; 153, 154) sont détachés l'un de l'autre de façon que leur surface oblique de verrouillage (51, 52) ne se touchent plus au moins partiellement et que seulement ensuite le fluide de pression est amené
    vers une chambre de travail (48, 49) associée à un côté (23.1, 23.2) du piston (22) et est de préférence délimité par celui-ci, afin d'obtenir un déplacement du piston (21) dans une direction axiale (59) parallèle à l'axe longitudinal (25) du cylindre (21) ou parallèlement à l'axe de rotation (33) de la broche (30) ou de rendre celui-ci possible ou de le supporter.
  13. Procédé selon la revendication 12, caractérisé en ce que le moyen de pression agit d'abord sur le palier à glissement à fluide (45, 145) à travers un ou le canal de fluide (46, 146), ou un détachement des corps de soutien de verrouillage (35, 36 ; 135, 136) ou des corps coniques de serrage (53, 54 ; 153, 154) de la position de verrouillage dans laquelle ils sont bloqués l'un contre l'autre par friction, dans une position de déverrouillage et de détachement dans laquelle les corps de soutien de verrouillage (35, 36 ; 135, 136) ou les corps coniques de serrage (53, 54 ; 153, 154) sont au moins partiellement détachés l'un de l'autre afin que leurs surfaces obliques de verrouillage (51, 52) ne se touchent au moins partiellement plus et que par cela un passage est formé entre et le long des surfaces obliques de verrouillage (51, 52) étant en regard et détachées l'une de l'autre, le passage étant en communication de fluide avec un ou le canal de fluide (47, 147) qui, lui, communique en fluide avec la chambre de travail (48, 49) ou est rendu communiquant en fluide de façon que le piston (22) est soumis au fluide de pression passant par le canal de fluide (47, 147) dans la chambre de travail (48, 49) pour obtenir un mouvement du piston (22) dans une direction axiale (59) parallèle à l'axe longitudinal (25) du cylindre (21) ou parallèlement à l'axe de rotation (33) de la broche (30) ou de rendre cela possible ou de le supporter.
EP10156720.4A 2009-04-09 2010-03-17 Vérin de verrouillage et procédé de verrouillage et de déverrouillage d'un vérin de verrouillage Active EP2239470B1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
PL10156720T PL2239470T3 (pl) 2009-04-09 2010-03-17 Jednostka tłokowo-cylindrowa z ryglowaniem oraz sposób ryglowania i odryglowywania jednostki tłokowo-cylindrowej
EP12197159.2A EP2570680B1 (fr) 2009-04-09 2010-03-17 Procédé de déverrouillage d'un cylindre de verrouillage
EP12197151.9A EP2570679B1 (fr) 2009-04-09 2010-03-17 Vérin de verrouillage et procédés de verrouillage et de déverrouillage correspondants
PL12197151T PL2570679T3 (pl) 2009-04-09 2010-03-17 Cylinder ryglujący i sposób ryglowania i odryglowywania cylindra ryglującego
PL12197159T PL2570680T3 (pl) 2009-04-09 2010-03-17 Sposób odryglowywania jednostki tłokowo-cylindrowej

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DE102009017212 2009-04-09

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EP12197159.2 Division-Into 2012-12-14
EP12197151.9 Division-Into 2012-12-14

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EP2239470A2 EP2239470A2 (fr) 2010-10-13
EP2239470A3 EP2239470A3 (fr) 2012-06-13
EP2239470B1 true EP2239470B1 (fr) 2013-07-03

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EP12197151.9A Active EP2570679B1 (fr) 2009-04-09 2010-03-17 Vérin de verrouillage et procédés de verrouillage et de déverrouillage correspondants
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
EP12197159.2A Active EP2570680B1 (fr) 2009-04-09 2010-03-17 Procédé de déverrouillage d'un cylindre de verrouillage

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DE (1) DE102010015996A1 (fr)
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DE19633412A1 (de) 1996-08-19 1998-03-05 Wolfram Sielemann Druckmittelbetriebener Antrieb
DE29720838U1 (de) 1997-11-25 1998-02-26 Andexser, Lucie, 32584 Löhne Arbeitszylinder mit integrierter Hubbremse
SE521461C2 (sv) 1999-03-26 2003-11-04 Parker Hannifin Ab Kolv- cylinderanordning med kolvstångslåsning
DE102007024736B3 (de) 2007-05-25 2008-06-12 Neumeister Hydraulik Gmbh Verriegelungszylinder mit Fluidgleitlagerung

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Publication number Publication date
EP2239470A3 (fr) 2012-06-13
EP2570679A1 (fr) 2013-03-20
DE102010015996A1 (de) 2010-10-14
ES2429341T3 (es) 2013-11-14
ES2437762T3 (es) 2014-01-14
EP2570679B1 (fr) 2013-09-18
EP2570680B1 (fr) 2013-09-18
PL2239470T3 (pl) 2013-11-29
ES2437763T3 (es) 2014-01-14
EP2570680A1 (fr) 2013-03-20
EP2239470A2 (fr) 2010-10-13
PL2570679T3 (pl) 2014-02-28
PL2570680T3 (pl) 2014-02-28

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