EP3101283B1 - Cylindre de verrouillage a double action et son procede de fonctionnement - Google Patents

Cylindre de verrouillage a double action et son procede de fonctionnement Download PDF

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Publication number
EP3101283B1
EP3101283B1 EP16167012.0A EP16167012A EP3101283B1 EP 3101283 B1 EP3101283 B1 EP 3101283B1 EP 16167012 A EP16167012 A EP 16167012A EP 3101283 B1 EP3101283 B1 EP 3101283B1
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EP
European Patent Office
Prior art keywords
pressure medium
locking
fluid
channel
cone
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EP16167012.0A
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German (de)
English (en)
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EP3101283A1 (fr
Inventor
Walter Neumeister
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Neumeister Hydraulik GmbH
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Neumeister Hydraulik GmbH
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Priority to PL16167012T priority Critical patent/PL3101283T3/pl
Publication of EP3101283A1 publication Critical patent/EP3101283A1/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
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/72—Output members, e.g. hydraulic motors or cylinders or control therefor having locking means

Definitions

  • the invention relates to a fluid operated, double-acting latching cylinder and a method of operating one or the fluid-operated, double-acting latching cylinder.
  • EP 2 570 679 A1 and EP 2 570 680 A1 the applicant are known pressure medium-operated, single-acting locking cylinder and methods for locking and unlocking of fluid-operated, single-acting locking cylinders.
  • These locking cylinders each contain a cylinder and a piston and are only lockable either on train or only on pressure.
  • a rotatable about a rotation axis spindle is provided on the non-rotatably fixed a first locking cone surfaces having, self-locking, first clamping cone body is attached.
  • the spindle comprises a spindle external thread, forming a non-self-locking Thread is engaged with a piston internal thread of the piston.
  • a second locking cone-surfaces exhibiting, non-rotatably, second clamping cone body is attached to this rotatably, which forms a clamping counter-cone body.
  • the first clamping cone body and the second clamping cone body to form a deadlock are self-locking, so frictionally stuck by static friction, so that they are unlocked only under exercise of the clamping solving dissolving forces.
  • a fluid-operated, double-acting locking cylinder solved which comprises a cylinder extending in the direction of a cylinder and a piston which comprises a first working chamber associated with a first piston side and a facing away, a second working chamber associated second piston side and with the aid of one of the first piston side via a in the first Working chamber opening first working channel and the second piston side via an opening into the second working chamber second working channel fluid pressure medium in an axial direction parallel to the cylinder longitudinal axis in a second direction and in a first direction opposite to the second direction relative to the cylinder, preferably linear, movable , but rotatably connected to the cylinder, wherein the piston rotatably connected to a first threaded body (nut or spindle) whose first thread (female thread or spindle thread) with a second thread (spindle thread or female thread) of a r eibschlüssig, ie frictionally
  • the locking cylinder according to the invention may also be referred to as a locking cylinder-piston unit.
  • the flow divider is a flow-controlled and / or pressure-controlled valve. This allows a further simplified, reliable and cost-effective design.
  • the flow divider comprises a housing with a, preferably a circular cylindrical inner circumference having, control piston receptacle in which a, as a pressure compensator and / or slider markable, preferably a circular cylindrical outer circumference exhibiting, control piston with, Preferably, very little play, in particular in or with a clearance fit, guided relative to the control piston receiving slidably mounted in an axial direction, and wherein the control piston extends axially in the direction of a control piston longitudinal axis, has a control piston length and a a first regulating-piston end and a second regulating-piston end extending therefrom in an opposite direction in the axial direction, which has a distance corresponding to the regulating-piston length from the first regulating-piston end, and wherein one in the housing, preferably as a Fixed throttle-shaped, first throttle-containing first inflow channel for a first partial volume flow of the fluid pressure medium and a one, preferably designed
  • such a flow divider can be built very small, so that it takes up relatively little space.
  • a flow divider in a preferably flanged control block, preferably attached to or on the cylinder, in which further or other control and / or regulating elements for controlling and / or regulating the locking cylinder can be accommodated ,
  • control piston in the axial direction pressure and / or flow controlled by the fluid pressure medium into a first shut-off position is displaceable, in which the control piston a first flow path from the first inflow channel to the first Pressure medium discharge channel with respect to a flow through the fluid pressure medium substantially or completely shuts off, while a second flow path from the second inflow channel to the second pressure medium outflow channel with respect to a flow through the fluid pressure medium is open or remains, and that the control piston in the axial direction flow controlled by the fluid pressure medium into a second shut-off position is displaceable, in which the control piston a second flow path from the second inflow channel to the second pressure medium outflow channel with respect Passage of the fluid pressure medium substantially or completely shuts off, while the first flow path from the first inflow channel to the first pressure medium outflow channel with respect to a flow through the fluid pressure medium is open or remains.
  • the locking cylinder when it is locked by jamming, unlock by applying the flow divider with the fluid pressure medium, which in the course of continued loading of the flow divider with the fluid pressure medium, automatically said fluid-dynamic Floating position or the said fluid-dynamic floating state of the first double-cone body can be achieved or is.
  • control piston receptacle when viewed in an imaginary cross-sectional plane formed perpendicular to the control piston longitudinal axis, has an internal cross-section, and that the first control piston end receptacle is in an imaginary first axis perpendicular to the control piston longitudinal axis Viewed cross-sectional plane, having a first inner cross section which is greater than the inner cross section of the control piston receptacle, and wherein the second control piston end receptacle in an imaginary, formed perpendicular to the control piston longitudinal axis second cross-sectional plane, a second inner cross-section has, which is greater than the inner cross section of the control piston receptacle.
  • the first control piston end recording on one of the control piston receiving opposite first side, viewed in the axial direction merges into a third control piston end recording, in which the first pressure fluid discharge channel directly or viewed indirectly and considered in an imaginary, perpendicular to the control piston longitudinal axis and parallel to the first cross-sectional plane formed third cross-sectional plane having a third inner cross-section corresponding to the inner cross-section of the control piston receptacle, so that the first control piston end of the control piston in the third control piston end Receptacle transferred and then there with, preferably very little play, in particular in or with a clearance fit, relative to the third control piston end receptacle in the axial direction slidably mounted and that the second control piston end receptacle on one of the control piston Aufn Aim opposite to the second side, viewed in the axial direction, in a fourth control piston end receptacle, in which the second pressure medium discharge channel opens directly or indirectly, and in an imaginary,
  • control piston receptacle extending along a longitudinal axis and the first and second control piston end receptacle, preferably also the third and fourth control piston end receptacle, symmetrical to an imaginary, perpendicular to the longitudinal axis of the Regelkolben- Receiving trained symmetry plane are designed or that the housing of the flow divider or the flow divider is designed symmetrically to an imaginary, formed perpendicular to the longitudinal axis of the control piston receiving symmetry plane.
  • the flow divider in a arranged in the cylinder or attached to the cylinder, preferably flanged control block together with, preferably substantially all, control elements for controlling the locking cylinder and / or together with, preferably substantially all , Control elements for controlling the locking cylinder is arranged. This allows a particularly compact and safe construction can be achieved.
  • the flow divider may be a gearbox divider which has at least one first gear motor or at least one first gear pump for conveying the first part volume flow and at least one second gear motor or at least one second gear pump for conveying the second partial volume flow, which are coupled to each other via a shaft.
  • first clamping cone body and the second clamping cone body of the first clamping double-cone body are integrally connected and / or made of a part and / or that the third terminal Cone body and the fourth clamping cone body of the second clamping double-cone body are integrally connected and / or made of a part.
  • first clamping double-cone body with its first locking cone surfaces and also the second clamping double-cone body with its third locking cone surfaces in viewed in the first direction, tapering radially to the axis of rotation of the second threaded body and the first clamping double-cone body with its second locking cone surfaces and also the second clamping double-cone body with its fourth locking cone Tapered surfaces, viewed in the second direction, taper radially towards the axis of rotation of the second threaded body.
  • first clamping double-cone body with its first locking cone surfaces and also the second clamping double-cone body with its third locking cone surfaces in the first Direction, extend radially away from the axis of rotation of the second threaded body and the first clamping double-cone body with its second locking cone surfaces and also the second clamping double-cone body with its fourth locking cone Area, viewed in the second direction, expand radially away from the axis of rotation of the second threaded body.
  • first clamping double-cone body with its first and second locking cone surfaces and that the second clamping double-cone body with his third and fourth locking cone surfaces, viewed in the first direction or viewed in the second direction can taper radially towards the axis of rotation of the second threaded body or that the first clamping double-cone body with its first and second locking body Cone surfaces and that the second clamping double-cone body with its third and fourth locking cone surfaces, as viewed in the first direction or viewed in the second direction, can expand radially away from the axis of rotation of the second threaded body.
  • the third locking cone surfaces of the second clamping double-cone locking body and the first locking cone surfaces of the first clamping double-cone locking body face and are the fourth locking cone surfaces of the second clamping double cones locking body and the third locking cone surfaces of the first clamping double-cone locking body.
  • the first clamping double-cone body is at least partially or completely received in a limited by the second clamping double-cone body recess, in particular in a chamber of the cylinder, the Preferably on the one hand by a cylinder bottom of the cylinder and on the other hand, by a, preferably integrally connected to the cylinder or one or the cylinder base, radially and transversely, preferably perpendicular, extending to the cylinder longitudinal axis of the cylinder, between the first clamping double Cone body and the piston arranged, in particular annular, approach is limited, and wherein the first pressure medium inflow channel opens on a first locking cone surfaces associated with the first side of the first clamping double-cone body in the recess, and wherein the second pressure medium inflow channel on a second locking cone Fläc hen associated second side of the first clamping double-cone body opens into the recess, and wherein the recess is sealed by a seal against the second working chamber
  • this can be realized in a particularly simple manner, a sequence control such that, starting from a locking position in which the locking cylinder is locked, automatically first the locking cylinder is unlocked and only then the piston is retracted or extended.
  • the first pressure medium inflow channel is shut off from the first or common pressure fluid discharge channel by means of abutting first and third locking cone surfaces and then when the first clamping double Kegel body and the second clamping double-cone body are lifted from one another in one or the unlocked position, with the first or common pressure fluid discharge channel via a then between the first and third locking cone surfaces formed, preferably annular, first channel is fluidly connected, and that the second pressure medium inflow channel, when the first clamping double-cone body and the second clamping double-cone body locked together in the second locking position and are clamped self-locking to form the deadlock, opposite the first or common pressure medium discharge channel v is closed off by means of the adjoining second and fourth locking cone surfaces and which, when the first clamping double-cone body and the second clamping double-con
  • the invention task is solved in terms of the method by a method for operating, controlling and / or regulating a pressure-medium-operated, double-acting, in particular inventive, locking cylinder, the comprises a cylinder extending in the direction of a cylinder longitudinal axis and a piston which comprises a first piston side associated with a first working chamber and a second piston side thereof facing away from a second working chamber and which by means of one of the first piston side via a first opening into the first working chamber Working channel and the second piston side via an opening into the second working chamber second working channel fluid pressure medium in an axial direction parallel to the cylinder longitudinal axis in a second direction and in a first direction opposite to the second direction relative to the cylinder, preferably linear, movable, but rotationally fixed is connected to the cylinder, wherein the piston rotatably connected to a first threaded body (nut or spindle), the first thread (nut thread or spindle thread) with a second thread (spindle thread or female thread) of a frictionally engaged
  • the said ratio at least during a movement of the piston both in the first direction as well as in the second direction, regardless of the in the first pressure medium inflow and in the second pressure medium inflow channel acting or adjusting pressures or counterpressures of the fluid pressure medium, preferably always, remains substantially constant or is held.
  • the said ratio at least during a movement of the piston in both the first direction and in the second direction, regardless of which pressure or back pressure of the fluid pressure medium in the first pressure medium inflow channel acts or is set and regardless of which pressure of the fluid pressure medium in the second pressure medium inflow channel acts or adjusts, preferably always, remains substantially constant or is held.
  • the ratio, at least during a movement of the piston in both the first direction and in the second direction, is essentially 1: 1 or is maintained substantially at 1: 1.
  • the first partial volume flow of the fluid pressure medium and the second partial volume flow of the fluid pressure medium are or remain substantially the same. This may be particularly advantageous when the first clamping double-cone body and / or the second clamping double-cone body are formed substantially symmetrically to an imaginary, arranged perpendicular to the axis of rotation or to the cylinder axis of symmetry ,
  • the flow divider a housing with a, preferably a circular cylindrical inner circumference having, control piston receptacle, in which a, also referred to as a pressure compensator and / or slide, preferably a circular cylindrical outer circumference, having control piston with, preferably very little play, in particular in or with a clearance fit, out relative to the control piston receptacle is slidably mounted in an axial direction, and wherein the control piston extends axially in the direction of a control piston longitudinal axis, has a control piston length and a first control piston end and a thereof away in an opposite direction in the axial direction extending second control piston end having from the first control piston end a the control piston length corresponding distance, and wherein in the housing a one, preferably designed as a fixed throttle, first throttle first inflow channel for a first part-volume flow of the fluid pressure means u nd a, preferably designed as a fixed throttle, second throttle second inflow channel for a
  • the control piston is moved from its basic or middle position in a second shut-off position or held in a second shut-off position in which the second pressure medium outflow channel and therefore also the second pressure medium inflow channel is shut off against the second inflow channel against inflow of the pressure medium, while a first Flow path between a first inflow channel and the first pressure medium outflow channel is open, so that the fluid pressure medium through the first inflow channel in the first pressure medium outflow channel and from there through the first pressure medium inflow channel can either flow to the first clamping double cone Body through a f ortetzten supply of the fluid pressure medium into an unlocking position or flows, so that the first clamping double-cone body is transferred to an unlocked position, and that, when the first clamping double-cone body with the second clamping double cone -
  • the locking cylinder when it is by means of the clamping double-cone body self-locking, so frictionally jammed by static friction, and thus locked, are unlocked particularly easy and effective, what in the course of a continued pressurization of the flow divider is achieved with the fluid pressure medium, automatically said fluid-dynamic floating position or the said fluid-dynamic floating state of the first double-cone body.
  • a flow divider may be provided, which is one or the gearbox divider, the at least one of the first part-volume flow-promoting first gear pump and the second part-volume flow-promoting second Gear pump includes, which are coupled to each other via one or the shaft such that at least during movement of the piston in the first direction and also in the second direction and each effected thereby rotating the second threaded body about its axis of rotation together with the first clamping double-cone body, said ratio of the first part-volume flow of the fluid pressure medium and the second part-volume flow of the fluid pressure medium remains substantially constant.
  • the method it can be provided that either, starting from the first locking position, in which the first clamping double-cone body and the second clamping double-cone body are clamped self-locking, at least first or only the first fluid Axial slide bearing is acted upon by the flow divider and the fluid-connected first pressure medium inflow channel with the fluid pressure medium, or, starting from the second locking position, in which the first clamping double-cone body and the second clamping double cone Body are clamped self-locking, first at least or only the second fluid-axial slide bearing on the flow divider and the fluid-connected second pressure medium inflow channel is acted upon by the fluid pressure medium, either to a lifting of the first clamping double-cone body of the second To effect clamping or double-cone body in a lift-off and unlocking position Lifting the first clamping double-cone body is effected by the second clamping double-cone body in a lift-off and unlocking, in which the first clamping double-cone body and the second
  • the lock cylinder 20 includes a cylinder 21 and a piston 22.
  • the lock cylinder 20 may also be referred to as a lock cylinder-piston unit.
  • the piston 22 is displaceable in the cylinder 21 in an axial direction 23, but rotatably mounted to the cylinder 21.
  • the piston 22 is sealed against a cylinder jacket inner wall 24 of the cylinder 21 by a ring seal 25.
  • the piston 22 is on its in the direction of the cylinder longitudinal axis 26 of the cylinder 21 facing away from each other sides 27.1, 27.2 by a fluid, in particular hydraulic, pressure medium, preferably oil, acted upon to a pressure fluid assisted movement of the piston 22 in a first direction 28.1 and in a second direction 28.2, opposite to the first direction 28.1 to allow.
  • the locking cylinder 20 is a fluid-operated, double-acting Locking cylinder, which can be locked both on train and on pressure.
  • the fluid pressure medium can be supplied via a first working channel 29.1 on the side facing away from a cylinder bottom 30 of the cylinder 21 first side 27.1 of the piston 22 in a first working chamber 31.1 to a movement of the piston 22 along the cylinder 21 and parallel to the cylinder longitudinal axis 26 to reach in the second direction 28.2.
  • the fluid pressure medium via a second working channel 29.2 on the second side 27.2 of the piston 22, which faces away from the first side 27.1 and toward the cylinder bottom 30, are fed into a second working chamber 31.2 to a movement of the piston 22 along the Cylinder 21 and parallel to the cylinder longitudinal axis 26 in the first direction 28.1 reach.
  • the first working chamber 31. 1 is sealed off from the second working chamber 31. 2 via the annular seal 25 of the piston 22.
  • the ring seal 25 is supported in an annular groove 33 of the piston 22 which is open towards the outside of the cylinder jacket inner wall 24.
  • the piston 22 is designed with a tubular hollow body, which is also designated with piston rod 34.
  • the piston 22 forms an annular projection which is non-rotatably connected to the piston rod 34.
  • the piston rod 34 extends from the first side 27.1 of the piston 22 in the axial direction 23 coaxially or parallel to the cylinder longitudinal axis 26 of the cylinder 21.
  • the piston 22 is formed integrally with a designated also with first threaded body nut 35.1.
  • the nut 35.1 has a designated as the first thread and designed as an internal thread nut thread 36.1.
  • the nut thread 36.1 forms in the illustrated embodiment, a piston thread of the piston 22.
  • the nut or piston thread 36.1 is engaged with a designated also with a second thread and designed as an external thread spindle thread 36.2 also referred to as a second threaded body spindle 35.2, on which the piston 22 is guided.
  • the nut or piston thread 36.1 and the spindle thread 36.2 form a non-self-locking thread 37.
  • the non-self-locking thread 37 is designed to be right-handed. But it can also be designed left-handed.
  • the nut or piston thread 36.1 and the spindle thread 36.2 each as a, in particular multi-start, coarse thread, preferably trapezoidal coarse thread designed.
  • an eight-speed coarse thread can be used.
  • the cylinder 21 is closed on one side 38. 1, which is assigned to the end of the spindle 35. 2 facing away from the piston 22, by a cover 39 enclosing the piston rod 34.
  • This can, as shown in the figures, integrally connected to the cylinder 21 and be prepared. However, it can also be connected in several parts with the cylinder.
  • the ring-shaped cover 39 has an open towards the piston rod 34 annular groove 40. In this annular groove 40, a ring seal 41 is supported, which seals the first working chamber 31.1 to the outside.
  • On its other side 38.2 of the cylinder 21 is closed by a cylinder bottom 30 forming the lid or head. This can preferably be connected in several parts with the cylinder 21.
  • the spindle 35.2 is rotatable relative to the cylinder 21 about a rotation axis 43 arranged parallel to the cylinder longitudinal axis 26 of the cylinder 21.
  • the spindle 35.2 is relative to the cylinder 21 in the axial direction 23 and parallel to the cylinder longitudinal axis 26 of the cylinder 21 axially displaceable, and only slightly.
  • the axial displaceability of the spindle 35.2 marked with the double arrow 44 or the axial spindle clearance is only about 1.5 to 2.5 mm.
  • the spindle 35.2 is solely due to gravity, in particular by a force acting on the piston rod 34 and the piston 22 load F, automatically or automatically, drive-free and without the action or support of force accumulators, such as tension or compression springs, against rotation around its axis of rotation 43 relative to the cylinder 21 and against movement or displacement in the axial direction 23, both in the first direction 28.1 and in the second direction 28.2, self-locking, so frictionally by static friction, clamped and locked in this way.
  • force accumulators such as tension or compression springs
  • the lock according to the invention is thus a type of double-self-locking lock.
  • a first clamping double-cone body 45.1 and second clamping double-cone body 45.2 are provided, which acts as a counter-clamping double-cone body with respect to the first clamping double-cone body 45.1 ,
  • the first clamping double-cone body 45.1 is rotatably mounted on the spindle 35.2 and the second clamping double-cone body 45.2 is rotatably attached to the cylinder 21.
  • the first clamp double cone body 45.1 and the second clamp double cone body 45.2 are designed to be coordinated with each other so that the first clamping double-cone body 45.1 with the second clamping double-cone body 45.2 to form a deadlock self-locking, so frictionally by static friction in a first locking position 46.1 (see FIG.
  • the first clamping double cone body 45.1 comprises a first locking cone surfaces 48.1 having frustoconical shaped, self-locking, first clamping cone body 47.1 and a second locking cone surfaces 48.2 having frusto-conically shaped, self-locking, second Clamp cone body 47.2.
  • the first clamping double cone body 45.1 is disc-shaped or designed as a double-cone-stump disc.
  • the first clamp double cone body 45.1 is designed rotationally symmetrical to the rotational axis 43 of the spindle 35.2 or to the cylinder longitudinal axis 26 of the cylinder 21.
  • the second clamping double-cone body 45.2 comprises a third locking cone surfaces 48.3 having, self-locking, third clamping cone body 47.3 and a fourth locking cone surfaces 48.4, self-locking, fourth clamping cone body 47.4 ,
  • the second clamping double-cone body 45.2 is rotationally symmetrical to the cylinder longitudinal axis 26 of the cylinder 21 or to the rotational axis 43 of the spindle 35.2 designed.
  • a recess or chamber 49 accommodating the first clamping double-conical body 45.1 is designed to be rotationally symmetrical with respect to the cylinder longitudinal axis 26 of the cylinder 21 or to the axis of rotation 43 of the spindle 35.2.
  • a recess or chamber 49 in which the first clamping double-cone body 45.1 is slidably received or arranged in the axial direction 23, on the one hand by a cylinder bottom portion 50 of the cylinder bottom 30 of the cylinder 21 and on the other hand limited by an annular projection 51 ,
  • the chamber or recess 49 has, viewed in a cylinder longitudinal axis 26 containing cross section, a T-shaped cross-section.
  • the first clamping double cone body 45.1 tapers with its first locking cone surfaces 48.1, and also the second clamping double cone body 45.2 tapers with its third locking cone opposite the first locking cone surfaces 48.1.
  • the first clamping double-cone body 45.1 tapers with its second Locking-cone surfaces 48.2 and also the second clamping double-cone body 45.2 tapers with its second locking cone surfaces 48.2 opposite fourth locking cone surfaces 48.4, viewed in the second direction 28.2, radially to the Rotation axis 43 of the spindle 35.2 out.
  • the second locking-cone surfaces 48.2 of the first clamping double-cone body 45.1 and the fourth locking-cone surfaces 48.2, 48.4 of the second clamping double-cone body 45.2 close with the axis of rotation 43 of the spindle 35.2 or with the cylinder longitudinal axis 26 of the cylinder 21 a second inclination angle 52.2 a ( Fig. 4 ).
  • the first inclination angle 52.1 and the second inclination angle 52.2 are the same size; it is preferably about 6.5 degrees.
  • At these angles of inclination or more generally, at angles of inclination of about 4 to 13 degrees, preferably 4 to 10 degrees, depending on the selected material pairing and other parameters in an axial juxtaposition or nesting of the first clamping double-cone body can be 45.1 and the second clamping double-cone body 45.2 achieve a self-locking in such a way that the first clamping double-cone body 45.1 and the second clamping double-cone body 45.2 both no longer relative to each other about the cylinder longitudinal axis 26 of the cylinder 21 or about the rotational axis 43 of the spindle 35.2 rotatable are as well as no longer movable relative to each other in the axial direction 23 or displaced, so not away from each other in one direction. Because it enters a self-locking by a jamming of the two clamping double-cone body 45.1, 45.2 with each other, in which they are frictionally clamped together by static friction.
  • the first locking conical surfaces 48.1 of the first clamping double-conical body 45.1 are such by an axial movement of the spindle 35.2 in the first direction 28.1 to the third locking conical surfaces 48.4 of the second clamping double-conical body 45.2 of the cylinder 21 can be applied, that in the applied state of the second clamping double-cone body 45.2 can absorb axial forces acting in the first direction 28.1 on the spindle 35.2.
  • the second locking conical surfaces 48.2 of the first clamping double-conical body 45.1 by an axial movement of the spindle 35.2 in the second direction 28.2 on the fourth locking conical surfaces 48.4 of the second clamping double-conical body 45.2 of the cylinder 21st be applied so that in the applied state of the second clamping double-cone body 45.2 can absorb axial forces acting in the second direction 28.2 on the spindle 35.2.
  • the spindle 35.2 is mounted by means of the first clamping double cone body 45.1 on at least two fluid-axial plain bearings 53.1 53.2, of which a first fluid-axial plain bearings 53.1 is intended, in the first direction 28.1 on the spindle 35.2 to absorb acting axial forces, and of which a second fluid-axial sliding bearing 53.2 is intended to absorb in the second direction 28.2 acting on the spindle 35.2 axial forces.
  • the first fluid-axial plain bearing 53.2 is acted upon by the fluid pressure medium via a first pressure-medium inflow channel 54.1 and the second fluid-axial plain bearing 53.2 can be acted upon by the fluid pressure medium via a second pressure medium inflow channel 54.2.
  • the first clamping double-cone body 45.1 is received in the chamber 49 of the cylinder 21 or of the cylinder bottom 30 delimited by the second clamping double-cone body 45.2.
  • the chamber 49 is bounded on the one hand by a cylinder bottom part 50 of the cylinder 21 and on the other hand by the annular projection 51 which, preferably in one piece, is connected or formed with the cylinder 21.
  • the projection 51 extends radially and perpendicular to the cylinder longitudinal axis 26 of the cylinder 21 in the direction of the spindle 35.2.
  • the projection 51 is arranged between the first clamping double-cone body 45.1 and the piston 22.
  • the first pressure-medium inflow channel 54.1 opens into the chamber 49 on a first side 55.1 of the first clamping double-conical body 45.1 assigned to the first interlocking conical surfaces 48.1 of the first clamping double conical body 45.1.
  • the inflow channel 54.2 opens into the chamber 49 on a second side 55.2 of the first clamping double-conical body 45.1 assigned to the second locking-cone surfaces 48.2 of the first clamping double-conical body 45.1.
  • the first clamping double-conical body 45.1 is rotatably attached to a non-threaded second spindle part 56.2 of the spindle 35.2, which in turn is non-rotatably mounted on a spindle thread 36.2 having the first spindle part 56.1 of the spindle 35.2.
  • the first Spindle part 56.1 and the second spindle part 56.2 of the spindle 35.2 integrally connected or made of one piece.
  • the second spindle part 56.2 of the spindle 35.2 which is not provided with a spindle thread, is received in a bore 57 of the annular projection 51 extending radially inwards and transversely to the cylinder longitudinal axis 23 of the cylinder 21.
  • the lug 51 has an open to the unthreaded second spindle part 56.1 of the spindle 35.2 annular groove 58, on the wall, a ring seal 59 is supported.
  • a ring seal 59 is supported.
  • the first pressure-medium inflow channel 54.1 which opens into the chamber 49 is fluid-connected to a first pressure-medium outflow channel 61.1 of a flow divider 60, 60.1, 60.2 and the second pressure-medium inflow channel 54.2, which likewise opens into the chamber 49, is connected to a second pressure-medium outflow channel 61.2 of the flow divider 60, 60.1, 60.2 fluidly connected.
  • the flow divider 60, 60.1, 60.2 comprises a pressure medium main inflow channel 62, which branches into a first inflow channel 62.1 and a second inflow channel 62.2.
  • the flow divider 60; 60.1, 60.2 is used to divide a main volume flow of the fluid pressure medium which can be supplied to the pressure medium main inflow channel 62 into a first partial volume flow of the fluid pressure medium into one of the first pressure medium outflow channel 61.1 and thus to the first pressure medium inflow channel 54.1 and into one second one Pressure medium discharge channel 61.2 and thus the second pressure medium inflow channel 54.2 to be supplied second part-volume flow of the fluid pressure medium.
  • preferred, first embodiment of the flow divider 60; 60.1 is a fluid flow or fluid pressure controlled valve.
  • this valve or this flow divider 60; 60.1 comprises a housing 64 having a circular-cylindrical inner circumference having a circular cylindrical control piston receptacle 65 for a relative to this displaceable control piston 66, which is also denoted by pressure compensator and / or slide.
  • control piston receptacle 65 is the circular cylindrical outer circumference having a circular or cylindrical Regulating piston 66 with very little clearance, in or with a clearance fit, guided relative to the control piston receptacle 65 slidably mounted in an axial direction 67.
  • the control piston 66 is in the control piston receptacle 65 of the housing 64 of the flow divider 60; 60.1.
  • the control piston 66 extends axially in the direction of a control piston longitudinal axis 68.
  • the control piston 66 has a control piston length.
  • the control piston 66 has a first control piston end 70.1 and a second control piston end 70.1 extending away therefrom in an opposite direction in the axial direction 67.
  • the second control piston end 70.2 has a distance corresponding to the control piston length from the first control piston end 70.1.
  • the first inflow channel 62.1 comprises a first fixed throttle 71.1.
  • the second inflow channel 62.2 comprises a second fixed throttle 71.2.
  • the first fixed throttle 71.1 and the second fixed throttle 71.2 are designed identically at least with regard to the throttle cross section and the throttle length.
  • the control piston receptacle 65 has a first receiving end 73.1 and a second receiving end 73.2 extending therefrom in an opposite direction in the axial direction 67.
  • the control piston receptacle 65 has an axial length which is smaller than the control piston length of the control piston 66, so that the control piston 66 with its two facing away from each other control piston ends 70.1, 70.2 can be on both sides on the control piston receptacle 65 addition.
  • the control piston ends 70.1, 70.2 of the control piston 66 with a respective equal part length on the facing away from each other receiving ends 73.1, 73.2 of the control piston receptacle 65 and on the perpendicular to the longitudinal axis 69 of the control piston receptacle 65 formed imaginary plane of symmetry 79 also extend, is the control piston 66 in the in FIG. 5 72 shown.
  • the control piston receptacle 65 is at its first receiving end 73.1, viewed in a first axial direction 67.1, in a circular cylindrical inner cross-section having or circular cylindrical first control piston end receptacle 74.1 for receiving the first control piston end 70.1 of the control piston 66, into which the first inflow channel 62.1 opens.
  • the control piston receptacle 65 is at its second receiving end 73.2, viewed in a second axial direction 67.2, in a circular cylindrical internal cross-section or circular cylindrical second control piston end receptacle 74.2 for receiving the second control piston end 70.2 of the control piston 66, in which the second inflow channel 62.2 opens.
  • the first regulating-piston end receptacle 74.1 forms part of a first regulating throttle 75.1 and the second regulating-piston end receptacle 74.2 forms a component of a second regulating throttle 75.2.
  • the first control piston end receptacle 74.1 is fluidly connected to a first pressure medium outflow channel 61.1 of the flow divider 60
  • the second control piston end receptacle 74.2 is fluidically connected to a second pressure medium outflow channel 61.2 of the flow divider 60.
  • the control piston receptacle 65 has, viewed in an imaginary, perpendicular to the control piston longitudinal axis 68 formed cross-sectional plane, an inner cross-section.
  • the first control piston end receptacle 74.1 viewed in an imaginary, perpendicular to the control piston longitudinal axis 68 formed first cross-sectional plane, a first inner cross-section which is greater than the inner cross-section of the control piston receptacle 65.
  • the second control piston end receptacle 74.2 has an imaginary Viewed perpendicular to the control piston longitudinal axis 68 formed second cross-sectional plane, a second inner cross section, which is also larger than the inner cross section the control piston receptacle 65.
  • the first inner cross section of the first control piston end receptacle 74.1 and the second inner cross section of the second control piston end receptacle 74.2 are the same size.
  • the first regulating-piston end receptacle 74.1 on a first side opposite the control piston receptacle 65, viewed in the first axial direction 67.1, passes into a circular-cylindrical inner circumference or circular-cylindrical, third regulating-piston end receptacle 74.3, into which the first pressure medium Outflow 61.1 opens.
  • the third control piston end receptacle 74.3 has, viewed in an imaginary, perpendicular to the control piston longitudinal axis 68 and parallel to the first cross-sectional plane formed third cross-sectional plane, a third inner cross section corresponding to the inner cross section of the control piston receptacle 65, so that the first control piston end 70.1 of the control piston 66 in the third control piston end receptacle 74.3 convertible and then there with very little play, preferably with a same game as in the control piston receptacle 65, in or with a clearance, relative to the third control piston end receptacle 74.3 in the Axial direction 67 is slidably mounted.
  • the second regulating-piston end receptacle 74.2 on a second side opposite the control piston receptacle 65, viewed in the second axial direction 67.2, passes into a circular-cylindrical inner circumference or circular-cylindrical, fourth regulating-piston end receptacle 74.4, into which the second pressure medium Outflow 61.2 opens.
  • the fourth control piston end receptacle 74.4 has, viewed in an imaginary, perpendicular to the control piston longitudinal axis 68 and parallel to the second cross-sectional plane formed fourth cross-sectional plane, a fourth inner cross section, which corresponds to the inner cross section of the control piston receptacle 65, so that the second control piston end 70.2 of the control piston 66 in the fourth control piston end receptacle 74.4 transferred and then there with very little play, preferably with a same game as in the control piston receptacle 65, in or with a clearance, relative to the fourth control piston end Receptacle 74.4 is slidably mounted in the axial direction 67.
  • the third and fourth regulating-piston end receptacles 74.3, 74.4 are each provided with an annular end wall 77.1, 77.2 of the housing 64 of the flow divider 60 extending radially inwards or to the longitudinal axis 69 of the control piston receptacle 65; 60.1 limited.
  • the first end wall forms a first stop 77.1 for the first regulating-piston end 70.1 of the regulating piston 66.
  • the second end wall forms a second stop 77.2 for the second control piston end 70.2 of the control piston 66.
  • the control piston 66 is pressure-controlled or flow-controlled by the fluid pressure medium in the first axial direction 67.1 displaceable in a first shut-off position in which it abuts with its first control piston end 70.1 on the first stop 77.1 and in which the control piston 66 a first flow path of the first inflow channel 62.1 to the first pressure medium outflow channel 61.1 shuts off with respect to a flow through the fluid pressure medium, while a second flow path from the second inflow channel 62.2 to the second pressure medium outflow channel 61.2 is open or remains with respect to a flow through the fluid pressure medium.
  • control piston 66 is flow-controlled by the fluid pressure medium in the second axial direction 67.2 displaceable in a second shut-off position in which it abuts with its second control piston end 70.2 on the second stop 77.2 and in which the control piston 66 a second flow path from the second inflow channel 62.2 to the second pressure medium outflow channel 61.2 with respect to a flow through the fluid pressure medium, while the first flow path from the first inflow channel 62.2 to the first pressure medium outflow channel 61.1 is open or remains with respect to a flow through the fluid pressure medium.
  • the flow divider 66 containing flow divider 60; 60.1 is designed symmetrically to an imaginary, perpendicular to the control piston longitudinal axis 68 of the control piston 66 formed symmetry plane 79.
  • flow divider 60; 60.1 is a single-acting or acting only in a flow direction flow divider.
  • the most important component of this flow divider 60; 60.1 is also referred to as a pressure compensator or acting as a pressure balance control piston 66.
  • the control piston 66 is in the axial direction 67 and in the longitudinal direction relative to a housing 64 of the flow divider 60; 60.1 displaceable up to the respective stop 77.1, 77.2.
  • a throttle 71.1, 71.2 with preferably exactly the same throttle cross-section (throttle bore and throttle length).
  • the movable control piston 66 or slide moves, depending on the pressure difference in the outgoing lines 61.1, 61.2; 54.1, 54.2, in a first direction of displacement 67.1 or in a second direction of displacement 67.2 to the bore of the control piston receptacle 65 each exactly aligned bore (third and fourth control piston end receptacle 74.3, 74.4) of the same fit and causes there throttling or even a blockage of this channel.
  • the interaction of this three components divides the from the flow divider 60; 60.1 outflowing pressure medium flow of the fluid pressure medium in a ratio of almost exactly 1: 1.
  • the inaccuracy is a maximum of +/- 2 percent, but this does not matter in this application.
  • a tie of this pressure gradient is caused by the two throttles 71.1, 71.2 downstream, axially displaceable, control piston 66 (hence the term “pressure compensator”), by, depending on the pressure ratio in the of the flow divider 60; 60.1 to the locking cylinder or to its chamber 49 for the first clamping double-cone body 45.1 outgoing lines 61.1, 61.2; 54.1, 54.2, the control piston 66 or slide its position relative to the housing 64 of the flow divider 60; 60.1 changes accordingly. Viewed in the flow direction in front of the two throttles 71.1, 71.2 eh equal pressure anyway, because there the pressure chamber is the same.
  • control piston 66 as a pressure compensator: If no fluid pressure fluid can flow out through a tight fit of the first clamping double-conical body 45.1 on the relevant outflow side, the pressure compensator or the control piston 66 closes on the latter due to the pressure accumulation Side of the first clamping double-cone body 45.1 automatically the other side, so that the flow divider 60; 60.1 locks both sides and only opens again when the jammed first clamping double-cone body 45.1 in the cylinder 21 solves or has solved.
  • the flow divider 60; 60.1 thus, it has the property of always dividing the pressure fluid flow of the fluid pressure medium from zero to a maximum almost exactly in a ratio that is substantially 1: 1, because the pressure difference through the pressure compensator or through the control piston 66 is always substantially at the same value ("balanced").
  • the pressure medium flow of the fluid pressure medium can be specified, for example, in liters / minute.
  • FIG. 6 schematically illustrated an alternative embodiment of a flow divider 60, which is a gearbox divider 60.2.
  • This gearbox divider 60; 60.2 comprises a first gear motor or a first gear pump 80.1 for conveying the first part volume flow and a second gear motor or a second gear pump 80.2 for conveying the second part volume flow.
  • the first gear pump 80.1 and the second gear pump 80.2 are forcibly coupled together via a shaft 81.
  • a ratio of the two partial volume flows can be kept essentially constant at approximately 1: 1.
  • a control block 82 is fixed in the region of its cylinder bottom 30, for example, flanged.
  • the control block 82 contains a plurality of control and / or regulating elements for controlling and / or regulating the locking cylinder 20 or for operating the locking cylinder 20.
  • one of these control or regulating elements is one or more than the flow divider 60 according to the invention .
  • annular pressure medium-discharge channel 83 for discharging the first and the second fluid-axial sliding bearing 53.1 53.2 pressurizing fluid pressure medium provided.
  • the pressure medium discharge channel 83 adjoins the first, second, third and fourth locking conical surfaces 48.1, 48.2, 48.3, 48.4 and opens into the chamber 49.
  • the pressure medium discharge channel 83 is when the first clamping double-cone body 45.1 is in its fluid-dynamic floating position 63, with the first and the second fluid-axial slide bearings 52.1, 53.2 both via a then between the first and third locking-cone surfaces 48.1, 48.3 trained, annular, first channel 84.1 fluidly connected and via a then between the second and fourth locking-cone surfaces 48.2, 48.4 formed, annular, second channel 84.2 fluidly connected.
  • first clamping double-cone body 45.1 and the second clamping double-cone body 45.2 locked together in the first locking position 46.1 to form the deadlock self-locking is the first pressure medium inflow channel 54.1 opposite the pressure medium discharge channel 83 by means of the then abutting each other first and third locking cone surfaces 48.1, 48.3 shut off. If, starting from this, the first clamping double cone body 45.1 and the second clamping double cone body 45.2 are lifted apart from one another in an unlocking position 92, then the first pressure medium inflow channel 54.1 is connected to the pressure medium discharge channel 83 via the then between the first and third locking cone surfaces formed, annular, first channel 84.1 fluidly connected.
  • first clamping double-conical body 45.1 and the second clamping double-conical body 45.2 are locked together in the second locking position 46.2 self-locking jamming to form the deadlock, second pressure medium inflow 54.2 opposite to the pressure medium-discharge channel 83 locked by means of the abutting second and fourth locking cone surfaces 48.2, 48.4. If, starting from this, the first clamping double-cone body 45.1 and the second clamping double-cone body 45.2 are lifted apart from one another in an unlocking position 92, then the second pressure-medium inflow channel 54.2 is in communication with the pressure-medium discharge channel 83 between the second and fourth locking-cone surfaces 48.2, 48.4 formed, annular, second channel 84.2 fluidly connected.
  • control unit 85 with a plurality, also referred to fluid channels flow and connection channels and control or Integrated control elements.
  • the control unit is exemplary in FIG. 1 illustrated schematically with broken lines.
  • the control elements are in the FIGS. 1 to 4 and 6 , as usual in such circuit diagrams, drawn with circuit symbols or symbols of fluid technology.
  • connection lines 86 and 87 can be provided for alternating supply and discharge of the fluid pressure medium.
  • a first connecting line 87 and a second connecting line 86 are provided.
  • Each of these connection lines 86 and 87 can thus serve both as a supply line and as a return line.
  • a switching or control valve not shown in the figures can be provided, which is fluid-connected to a supply device for the fluid pressure medium, likewise not shown in the figures.
  • the supply device may include a pump, preferably also a tank, for the fluid pressure medium.
  • the control unit 85 has as essential control or regulation elements at least the flow divider 60, two Umschaltventile88.1, 88.2, in particular in the form of a 2-2-way valve, and two load-holding Senkbrems valves or lowering brake valves 89.1, 89.2 , preferably also two check valves 90.1, 90.2.
  • Each load-holding lowering brake valve or lowering brake valve 89.1, 89.2 has an inlet 95.1, 95.2, an outlet 96.1, 96.2 and a control connection 97.1, 97.2, to which a control line or a control channel 98.1, 98.2 is connected.
  • the inlet 95.1 of the first load-holding Senkbrems valve or lowering brake valve 89.1 is connected to the The first working chamber 31.1 is fluid-connected via the fluid channel 29.1, which is also referred to as the first working channel, and the outlet 96.1 of the first load-holding lowering brake valve or lowering brake valve 89.1 is fluid-connected to the first connecting channel 87.
  • the first control channel 98.1 of the first load-holding Senkbrems valve or lowering brake valve 89.1 is fluidly connected to the second connection channel 86.
  • the second inlet 95.2 of the second load-holding lowering brake valve or lowering brake valve 89.2 is fluid-connected to the second working chamber 31.2 via the fluid channel 29.2, which is also referred to as the second working channel, and the second outlet 96.2 of the second load-holding lowering brake valve or Lowering brake valve 89.2 is fluidly connected to the second connection channel 86.
  • the second control channel 98.2 of the second load-holding Senkbrems valve or lowering brake valve 89.2 is fluidly connected to the first connection channel 87.
  • the respective load-holding Senkbrems valve or the Senkbrems valve 89.1, 89.2 be acted upon by the spring force of a spring 99.1, 99.2, the force that is exerted by the fluid pressure fluid via the respective control channel 98.1, 98.2 , counteracts.
  • the respective passageway between the respective inlet 95.1, 95.2 and the respective outlet 96.1, 96.2 of the respective lowering brake valve 89.1, 89.2 then, when the respective control channel 98.1, 98.2 is not acted upon by fluid pressure medium or is depressurized, so that possibly at the respective inlet 95.1, 95.2 pressure medium under pressure, the respective lowering brake valve 89.1, 89.2 can not happen.
  • the respective lowering brake valve as a load-holding lowering brake valve 89.1, 89.2 are used.
  • the piston 22 can not continue to lower. In this way, if necessary, independently of or in addition to a mechanical locking of the locking cylinder 20, respectively of the piston 22, a fluidic, in particular hydraulic, securing the locking cylinder 20, respectively of the piston 22, can be achieved.
  • the counter-pressure acting in the second working chamber 31.2 is maintained at pressure values with the aid of the second lowering brake valve 89.2 during the application of the fluid to the first working chamber 31.1 and consequently during a movement of the piston 22 in the second direction or in the retraction direction 28.2 are smaller than the working pressure in the first working chamber 31.1, so that during the movement of the piston 22 in the second direction 28.2 a controlled braking of the piston 22 in the second direction 28.2 is effected. As a result, an uncontrolled advance of the piston 22 in the second direction 28.2 can be avoided.
  • first load-holding lowering brake valve or the lowering brake valve 89.1 it can be effected or caused that when the piston 22 is acted upon on its second side 27.2 with the pressure medium located in the second working chamber 31.2 to form a working pressure, causing a displacement of the piston 22 in the first direction or extension direction 28.1, at the same time in the first working chamber 31.1 on the first side 27.1 of the piston 22, a counter pressure exerted by the pressure medium in the first working chamber 31.1 acts.
  • the counterpressure acting in the first working chamber 31.1 is maintained at pressure values, which are always lower than the working pressure in, with the aid of the first counterbalance valve 89.1 during pressurization of the second working chamber 31.2 with pressure medium and consequently during movement of the piston 22 in the first direction 28.1 are the second working chamber 31.2, so that during the movement of the piston 22 in the first direction 28.1 a controlled braking of the piston 22 in the first direction 28.1 is effected. As a result, an uncontrolled advance of the piston 22 in the first direction 28.1 can be avoided.
  • the first connection channel 87 is fluidly connected via the first channel 91. 1 to the pressure medium main inflow channel 62 of the flow divider 60.
  • the first channel 91.1 contains the first check valve 90.1.
  • the first check valve 90.1 allows a flow of the fluid pressure medium toward the flow divider 60, but blocks in the opposite direction.
  • the second connection channel 86 is fluidly connected via the second channel 91. 2 to the pressure medium main inflow channel 62 of the flow divider 60.
  • the second channel 91.2 contains the second check valve 90.2.
  • the second check valve 90.2 allows a flow of the fluid pressure medium toward the flow divider 60, but blocks in the opposite direction.
  • the first and second check valves 90.1, 90.2 each contain at least one locking member.
  • the locking member may be a ball.
  • the pressure medium discharge channel 83 of the recess or chamber 49 of the cylinder 21 is fluidly connected to the first and second switching valve 88.1, 88.2.
  • These switching valves 88.1, 88.2 are each a 2-way valve.
  • the first switching valve 88.1 is of a in the FIGS. 1 to 4 shown first passage position 100.1, in which the fluid pressure medium from the pressure medium discharge passage 83 of the chamber 49 can flow into the first working chamber 31.1, operable or switchable in a first blocking position, in which the flow path from the pressure medium discharge passage 83 to the first working chamber 31.1 is locked.
  • the second switching valve 88.1 is of a in the FIGS.
  • first passage position 100.1 of the first switching valve 88.1 and also in the second passage position 100.2 of the second switching valve 88.2 is each a basic position in which the switching valves 88.1, 88.2 due to an application of fluid pressure fluid via one fluid-connected to the pressure fluid discharge channel first and second control channel 101.1, 101.2 held or transferred.
  • Each switching valve 88.1, 88.2 thus forms a means for the need or switchable blocking or releasing a passageway.
  • the control for switching the first switching valve 88.1 from its first basic or passage position 100.1 into its first blocking position takes place via a third control channel 101.3, which is fluid-connected to the second connecting channel 86.
  • the control for switching the second switching valve 88.2 from its second basic or passage position 100.2 into its second blocking position takes place via a fourth control channel 101.4, which is fluid-connected to the first connecting channel 87.
  • the second connection channel 86 is acted upon by fluid pressure medium, while the first connection channel 87 by means of a suitable, not shown in the figures means , is depressurized or is.
  • the fluid pressure medium can flow through the second connection channel 86 and, at a branch thereof, out through the second channel 91. 2 with a main volume flow into the pressure medium main inflow channel 62 of the flow divider 60.
  • the pressure compensator or the control piston 66 of the flow divider 60; 60.1 now regulates a first part-volume flow of the main volume flow in the opening into the recess or chamber 49 of the cylinder 21 first pressure medium inflow channel 54.1 and a second part-volume flow of the main volume flow in the recess or chamber 49th the second pressure medium inflow channel 54.2 opening out of the cylinder 21 in such a way that the ratio of the first partial volume flow of the fluid pressure medium flowing through the first fluid-inflow inflow channel 54.1 and that passing through the second pressure medium inflow channel 54.2 passes through the first second fluid-axial sliding bearings 53.2 flowing second volume partial flow of the fluid pressure medium, at least during movement of the piston 22 in the first direction 28.1 and also during movement of the piston 22 in the second direction 28.2, regardless of the in the first pressure medium Inflow channel 54.1 and in the second pressure medium inflow channel 54.2 acting or adjusting pressures or counterpressures of the fluid pressure medium always remains substantially constant.
  • the first clamping double-conical body 45.1 is or remains independent of both by means of the first fluid-axial bearing 53.1 charged with the fluid pressure medium and by means of the second fluid-axial bearing 53.2 acted upon by the fluid pressure medium Size of a force acting on the piston 22 load F (on pressure or train) and thereby required system pressure, always in a fluid-dynamic floating position 63 and in a fluid-dynamic floating state fluidly stored (see FIGS. 1 and 2 ).
  • Said ratio is in the embodiment shown substantially 1: 1, so that therefore the first part-volume flow of the fluid pressure medium and the second part-volume flow of the fluid pressure medium are substantially equal or remain.
  • the first connection channel 87 is subjected to fluid pressure medium, while the second connection channel 86 by means of the means not shown in the figures, depressurized is switched.
  • the fluid pressure medium can flow through the first connection channel 87 and, at a branch thereof, out through the first channel 91.1 with a main volume flow into the pressure medium main inflow channel 62 of the volume distributor 60.
  • the pressure compensator or the control piston 66 of the flow divider 60; 60.1 now controls a first part-volume flow of the main volume flow in the opening into the recess or chamber 49 of the cylinder 21 first pressure medium inflow channel 54.1 and a second part-volume flow of the main volume flow in which in the recess or chamber 49 of the Cylinder 21 opening second pressure medium inflow channel 54.2 such that the said ratio, as already described above, always substantially 1: 1 or remains substantially at 1: 1.
  • the fluid pressure medium in the first working chamber 31.1 is displaced into the first working channel 29.1 and can from there via the first lowering brake valve 89.1 to flow into the first connecting channel 87, which serves here as a reflux channel.
  • the first lowering brake valve 89.1 in the first working chamber 31.1 a working pressure in the second working chamber 31.2 counteracting counter or brake pressure is maintained, which causes the piston 22 and consequently the piston rod 34 is not uncontrolled in the first Move direction or extension direction 28.1, in particular can not lead uncontrolled in the extension direction 28.1.
  • the first lowering brake valve 89.1 is coupled to the second control channel 98.2, which is in fluid communication with the second connection channel 86.
  • the first lowering brake valve 89.1 opens a passageway between the first working channel 29.1 and the first connection channel 87 depending on the operating pressure acting in the second working channel 29.2 or in the second working chamber 31.2, preferably proportional to the working pressure, so that with increasing Working pressure in the second working chamber 31.2 by means of the first lowering brake valve 89.1 a corresponding, preferably proportional, increasing back pressure in the first working chamber 31.1 can be achieved or achieved.
  • the second lowering brake valve 89.2 is coupled to the first control channel 98.1, which is connected to the first Connection channel 87 is fluidly connected.
  • the second lowering brake valve 89.2 opens a passageway between the second working channel 29.2 and the second connecting channel 86 depending on the operating pressure acting in the first working channel 29.1 or in the first working chamber 31.1, preferably proportional to the working pressure, so that with increasing Working pressure in the first working chamber 31.1 by means of the second lowering brake valve 89.2 a corresponding, preferably proportional, increasing back pressure in the second working chamber 31.2 can be achieved or achieved.
  • both Anschluß sakenale 86 and 87 by means of the not shown in the figures Switched by depressurized.
  • a second locking position 46.2 is established, as in FIG FIG. 4 shown.
  • the first clamping double-cone body 45.1 is self-locking, so frictionally jammed by static friction on its second locking-cone surfaces 48.2 with the fourth locking cone surfaces 48.4 of the second clamping double-cone body 45.2 of the cylinder 21 ,
  • the clamping force between the two clamped double-cone bodies 45.1, 45.2 clamped together increases proportionally with increasing load F.
  • an always secure locking of the spindle 35.2 against rotation about its axis of rotation 43 relative to the cylinder 21 can be achieved and, as a result, further movement of the piston 22 and the load F acting thereon via the piston rod 34 can be reliably prevented be, not only in a normal operation of the locking cylinder 20, 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 according to the invention offers a higher locking safety than previously known, locking cylinder which lock by friction friction, but not self-locking, ie frictional by static friction, by jamming.
  • annular, second channel 84.2 is formed between the second locking conical surfaces 48.2 of the first clamping double conical body 45.1 and the fourth locking conical surfaces 48.4 of the second clamping double conical body 45.2 (cf. , FIGS. 1 and 2 ), so that at the same time with the formation of this channel 84.2, the fluid pressure medium from the opening into the recess or chamber 49 second pressure medium inflow channel 54.2 via or through the annular second channel 84.2 in the opening into the recess or chamber 49 pressure medium Abraw channel 83 can flow.
  • the control piston 66 moves, with continued supply of the fluid pressure medium, starting from its first stop and shut-off position in the direction of the second stop 77.2.
  • annular, first channel 84.1 is formed between the first locking conical surfaces 48.1 of the first clamping double conical body 45.1 and the third locking conical surfaces 48.3 of the second clamping double conical body 45.2 (cf. , FIGS. 1 and 2 ), so that at the same time as the formation of this channel 84.1, the fluid pressure medium from the opening into the recess or chamber 49 first pressure medium inflow channel 54.1 via or through the first annular channel 84.1 in the opening into the recess or chamber 49 pressure medium Abraw channel 83 can flow.
  • the control piston 66 moves, with continued supply of the fluid pressure medium, starting from its second stop and shut-off position in the direction of the first stop 77.1.
  • the control piston 66 starting from the respective stop and shut-off position, moves in the direction of the respective other stop 77.2, 77.1 into a basic or middle position 72, in which the pressure difference of the pressure medium in the first pressure medium Outflow channel 61.1 of the flow divider 60; 60.1 and the pressure medium pressure in the second pressure medium outflow 61.2 of the flow part 60; 60.1 or the pressure difference across the two fixed throttles 71.1, 71.2 is approximately or substantially zero, so that then the first part-volume flow in the first pressure medium outflow channel 61.1 of the flow part 60; 60.1 and consequently in the opening into the recess or chamber 49 first pressure medium inflow channel 54.1 and the second part volume flow in the second pressure medium outflow channel 61.2 of the flow part 60; 60.1 and consequently in the opening into the recess or chamber 49 second pressure medium inflow channel 54.2 are substantially equal or are kept or remain.
  • the fluid pressure medium flows from the pressure medium discharge channel 83 either via the first pressure medium channel 102.1 into the first working chamber 33.1, whereby the Piston 22 in the second direction 28.2 and the piston rod 34 is moved in the retraction direction 28.2, or via the second pressure medium channel 102.2 in the second working chamber 31.2, whereby the piston 22 moves in the first direction 28.1 and the piston rod 34 in the extension direction 28.1 becomes.
  • a sequence control is realized such that First, the first clamping double-cone body 45.1 is released from its jamming and only then the piston 22 is acted upon on a piston side 27.1, 27.2 of its two facing away piston sides 27.1, 27.2 with the fluid pressure medium, whereby a movement of the piston 22nd in the axial direction 23 and thereby rotation of the spindle 35.2 is effected together with the first clamping double-cone body 45.1.

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Claims (15)

  1. Vérin de verrouillage (20) à double action, actionné par un agent de pression, qui comprend un cylindre (21) s'étendant dans la direction d'un axe longitudinal de cylindre (26) et un piston (22) qui présente un premier côté de piston (27.1) associé à une première chambre de travail (31.1) et un deuxième côté de piston (27.2) opposé à celui-ci, associé à une deuxième chambre de travail (31.2), et qui, à l'aide d'un agent de pression fluide pouvant être amené au premier côté de piston (27.1) par un premier canal de travail (29.1) débouchant dans la première chambre de travail (31.1) et au deuxième côté de piston (27.2) par un deuxième canal de travail (29.2) débouchant dans la deuxième chambre de travail (31.2), peut être déplacé par rapport au cylindre (21) dans une direction axiale (23) parallèle à l'axe longitudinal de cylindre (26) dans un deuxième sens (28.2) et dans un premier sens (28.1) opposé au deuxième sens (28.2), mais est cependant relié solidaire en rotation au cylindre (21),
    dans lequel le piston (22) est relié solidaire en rotation à un premier corps fileté (35.1), par exemple un écrou ou une broche, dont le premier filetage (36.1), par exemple un filetage d'écrou ou un filetage de broche, est en prise avec un deuxième filetage (36.2), par exemple un filetage d'écrou ou un filetage de broche, d'un deuxième corps fileté (35.2), par exemple un écrou ou une broche, verrouillable automatiquement par friction et par la force de gravité, en formant un filetage (37) non autobloquant,
    et dans lequel le deuxième corps fileté (35.2) peut tourner par rapport au cylindre (21) autour d'un axe de rotation (43) s'étendant parallèlement à l'axe longitudinal de cylindre (26) du cylindre (21) et coulisser axialement dans la direction axiale (23) par rapport au cylindre (21),
    et dans lequel un premier corps à double cône de serrage (45.1) relié solidaire en rotation au deuxième corps fileté (35.2) est prévu, qui présente un premier corps à cône de serrage (47.1) présentant de premières surfaces coniques de verrouillage (48.1) et un deuxième corps à cône de serrage (47.2) présentant de deuxièmes surfaces coniques de verrouillage (48.2),
    et dans lequel un deuxième corps à double cône de serrage (45.2) relié solidaire en rotation au cylindre (21) est prévu, qui présente un troisième corps à cône de serrage (47.3) présentant de troisièmes surfaces coniques de verrouillage (48.3) et un quatrième corps à cône de serrage (47.4) présentant de quatrièmes surfaces coniques de verrouillage (48.4),
    et dans lequel les premières surfaces coniques de verrouillage (48.1) du premier corps à double cône de serrage (45.1) peuvent être appliquées par un déplacement axial du deuxième corps fileté (35.2) dans le premier sens (28.1) contre les troisièmes surfaces coniques de verrouillage (48.3) du deuxième corps à double cône de serrage (45.2) de telle sorte qu'à l'état appliqué le deuxième corps à double cône de serrage (45.2) peut absorber les forces axiales qui agissent dans le premier sens (28.1) sur le deuxième corps fileté (35.2) et les premières surfaces coniques de verrouillage (48.1) et les troisièmes surfaces coniques de verrouillage (48.3), en formant entre elles un blocage dans une première position de verrouillage (46.1), sont bloquées de manière autobloquante aussi bien contre une rotation autour de l'axe de rotation (43) du deuxième corps fileté (35.2) que contre un déplacement les éloignant les unes des autres dans la direction axiale (23),
    et dans lequel les deuxièmes surfaces coniques de verrouillage (48.2) du premier corps à double cône de serrage (45.1) peuvent être appliquées par un déplacement axial du deuxième corps fileté (35.2) dans le deuxième sens (28.2) contre les quatrièmes surfaces coniques de verrouillage (48.4) du deuxième corps à double cône de serrage (45.2) de telle sorte qu'à l'état appliqué le deuxième corps à double cône de serrage (45.2) peut absorber les forces axiales qui agissent dans le deuxième sens (28.2) sur le deuxième corps fileté (35.2) et les deuxièmes surfaces coniques de verrouillage (48.2) et les quatrièmes surfaces coniques de verrouillage (48.4), en formant entre elles un blocage dans une deuxième position de verrouillage (46.2), sont bloquées de manière autobloquante aussi bien contre une rotation autour de l'axe de rotation (43) du deuxième corps fileté (35.2) que contre un déplacement les éloignant les unes des autres dans la direction axiale (23),
    de sorte que le vérin de verrouillage (20) peut être verrouillé aussi bien en traction dans la première position de verrouillage (46.1) qu'en pression dans la deuxième position de verrouillage (46.2) et, à l'état appliqué, est verrouillé dans la position de verrouillage respective (46.1, 46.2) de telle sorte que le premier corps à double cône de serrage (45.1) ne peut être transféré dans une position de déverrouillage (92), dans laquelle le deuxième corps fileté (35.2) peut tourner par rapport au cylindre (21) autour de son axe de rotation (43), qu'en exerçant des forces de desserrage libérant le blocage avec le deuxième corps à double cône de serrage (45.2),
    et dans lequel le deuxième corps fileté (35.2) est monté sur au moins deux paliers lisses axiaux fluides (53.1, 53.2), dont un premier palier lisse axial fluide (53.1) est conçu pour absorber les forces axiales agissant dans le premier sens (28.1) sur le deuxième corps fileté (35.2) et dont un deuxième palier lisse axial fluide (53.2) est conçu pour absorber les forces axiales agissant dans le deuxième sens (28.2) sur le deuxième corps fileté (35.2),
    et dans lequel le premier palier lisse axial fluide (53.1) peut être soumis au ou à un agent de pression fluide par un premier canal d'amenée d'agent de pression fluide (54.1),
    et dans lequel le deuxième palier lisse axial fluide (53.2) peut être soumis au ou à un agent de pression fluide par un deuxième canal d'amenée d'agent de pression fluide (54.2),
    et dans lequel un diviseur de débit (60 ; 60.1, 60.2) comprenant un canal d'amenée principal d'agent de pression et n'agissant que dans un sens d'écoulement pour diviser un débit volumique principal d'agent de pression fluide pouvant être amené au canal d'amenée principal d'agent de pression en un premier débit volumique partiel et en un deuxième débit volumique partiel est prévu, qui comprend un premier canal de sortie d'agent de pression (61.1) pour le premier débit volumique partiel débouchant dans le premier canal d'amenée d'agent de pression fluide (54.1) pour le premier palier lisse axial fluide (53.1) et un deuxième canal de sortie d'agent de pression (61.2) pour le deuxième débit volumique partiel débouchant dans le deuxième canal d'amenée d'agent de pression fluide (54.2) pour le deuxième palier lisse axial fluide (53.2).
  2. Vérin de verrouillage selon la revendication 1,
    caractérisé en ce
    que le diviseur de débit (60 ; 60.1) est une soupape commandée par écoulement et/ou par pression.
  3. Vérin de verrouillage selon la revendication 1 ou 2,
    caractérisé en ce
    que le diviseur de débit (60 ; 60.1) comprend un boîtier (64) avec un logement de piston de réglage (65) dans lequel un piston de réglage (66), guidé avec un faible jeu, est monté coulissant dans une direction axiale (67) par rapport au logement de piston de réglage (65),
    et dans lequel le piston de réglage (66) s'étend axialement dans la direction d'un axe longitudinal de piston de réglage (68) et présente une longueur de piston de réglage ainsi qu'une première extrémité de piston de réglage (70.1) et une deuxième extrémité de piston de réglage (70.2) s'étendant à l'écart de celle-ci dans un sens opposé dans la direction axiale (67), qui présente par rapport à la première extrémité de piston de réglage (70.1) une distance correspondant à la longueur de piston de réglage,
    et dans lequel un premier canal d'amenée (62.1) pour un premier débit volumique partiel d'agent de pression fluide contenant un premier étranglement (71.1) et un deuxième canal d'amenée (62.2) pour un deuxième débit volumique partiel d'agent de pression fluide contenant un deuxième étranglement (71.2) sont disposés dans le boîtier (64),
    et dans lequel le logement de piston de réglage (65) présente une première extrémité de logement (73.1) et une deuxième extrémité de logement (73.2) s'étendant à l'écart de celle-ci dans un sens opposé dans la direction axiale (67), et dans lequel le logement de piston de réglage (65), à sa première extrémité de logement (73.1), vu dans la direction axiale (67), se prolonge en un premier logement d'extrémité de piston de réglage (74.1) pour recevoir la première extrémité de piston de réglage (70.1) du piston de réglage (66), dans lequel débouche le premier canal d'amenée (62.1),
    et dans lequel le logement de piston de réglage (65), à sa deuxième extrémité de logement (73.2), vu dans la direction axiale (67), se prolonge en un deuxième logement d'extrémité de piston de réglage (74.2) pour recevoir la deuxième extrémité de piston de réglage (70.2) du piston de réglage (66), dans lequel débouche le deuxième canal d'amenée (62.2),
    et dans lequel le premier logement d'extrémité de piston de réglage (74.1) forme un premier étranglement de réglage ou une partie d'un premier étranglement de réglage (75.1) et le deuxième logement d'extrémité de piston de réglage (74.2) forme un deuxième étranglement de réglage ou une partie d'un deuxième étranglement de réglage (75.2),
    et dans lequel le premier logement d'extrémité de piston de réglage (74.1) est en liaison fluidique avec le premier canal de sortie d'agent de pression (61.1) et le deuxième logement d'extrémité de piston de réglage (74.2) est en liaison fluidique avec le deuxième canal de sortie d'agent de pression (61.2).
  4. Vérin de verrouillage selon la revendication 3,
    caractérisé en ce
    que le piston de réglage (66), commandé par pression et/ou par écoulement par l'agent de pression fluide, peut coulisser dans la direction axiale (67) dans une première position de fermeture (78.1) dans laquelle le piston de réglage (66) ferme un premier chemin d'écoulement du premier canal d'amenée (62.1) vers le premier canal de sortie d'agent de pression (61.1) en ce qui concerne un passage de l'agent de pression fluide, tandis qu'un deuxième chemin d'écoulement du deuxième canal d'amenée (62.2) vers le deuxième canal de sortie d'agent de pression (61.2) est ou reste ouvert en ce qui concerne un passage de l'agent de pression fluide,
    et
    que le piston de réglage (66), commandé par écoulement par l'agent de pression fluide, peut coulisser dans la direction axiale (67) dans une deuxième position de fermeture (78.2) dans laquelle le piston de réglage (66) ferme un deuxième chemin d'écoulement du deuxième canal d'amenée (62.2) vers le deuxième canal de sortie d'agent de pression (61.2) en ce qui concerne un passage de l'agent de pression fluide, tandis que le premier chemin d'écoulement du premier canal d'amenée (62.1) vers le premier canal de sortie d'agent de pression (61.1) est ou reste ouvert en ce qui concerne un passage de l'agent de pression fluide.
  5. Vérin de verrouillage selon la revendication 1,
    caractérisé en ce
    que le diviseur de débit (60 ; 60.2) est un diviseur de débit à engrenages (60.2) qui comprend au moins un premier moteur à engrenages ou au moins une première pompe à engrenages (80.1) pour transporter le premier débit volumique partiel et au moins un deuxième moteur à engrenages ou au moins une deuxième pompe à engrenages (80.2) pour transporter le deuxième débit volumique partiel, qui sont accouplées par un arbre (81).
  6. Vérin de verrouillage selon l'une des revendications précédentes,
    caractérisé en ce
    que le premier corps à double cône de serrage (45.1) est reçu au moins partiellement ou entièrement dans un logement (49) d'une partie de cylindre du cylindre (21) limité par le deuxième corps à double cône de serrage (45.2), qui est limité par un épaulement (51) s'étendant radialement et transversalement à l'axe longitudinal de cylindre (26) du cylindre (21), disposé entre le premier corps à double cône de serrage (45.1) et le piston (22), et dans lequel le premier canal d'amenée d'agent de pression fluide (54.1) débouche dans le logement (49) sur un premier côté (55.1) du premier corps à double cône de serrage (45.1) associé aux premières surfaces coniques de verrouillage (48.1), et dans lequel le deuxième canal d'amenée d'agent de pression fluide (54.2) débouche dans le logement (49) sur un deuxième côté (55.2) du premier corps à double cône de serrage (45.1) associé aux deuxièmes surfaces coniques de verrouillage (48.2), et dans lequel le logement (49) est rendu étanche par rapport à la deuxième chambre de travail (31.2) par un joint (59).
  7. Vérin de verrouillage selon la revendication 6,
    caractérisé en ce
    que dans une zone située entre le troisième corps à cône de serrage (47.3) et le quatrième corps à cône de serrage (47.4) du deuxième corps à double cône de serrage (45.2),
    soit
    un premier canal d'évacuation d'agent de pression pour évacuer l'agent de pression fluide passant à travers le premier palier lisse axial fluide est prévu, qui, dans une position de déverrouillage du premier corps à double cône de serrage, est en liaison fluidique avec le premier palier lisse axial fluide et débouche dans le logement
    et
    un deuxième canal d'évacuation d'agent de pression pour évacuer l'agent de pression fluide passant à travers le deuxième palier lisse axial fluide est prévu, qui, dans une position de déverrouillage du premier corps à double cône de serrage, est en liaison fluidique avec le deuxième palier lisse axial fluide et débouche dans le logement,
    soit
    un canal d'évacuation d'agent de pression commun (83) pour évacuer l'agent de pression fluide passant à travers le premier et le deuxième palier lisse axial fluide (53.1, 53.2) est prévu, qui, dans une position de déverrouillage (92) du premier corps à double cône de serrage (45.1), est en liaison fluidique avec le premier et le deuxième palier lisse axial fluide (53.1, 53.2) et débouche dans le logement (49).
  8. Vérin de verrouillage selon la revendication 7,
    caractérisé en ce
    que le premier canal d'amenée d'agent de pression fluide (54.1), lorsque le premier corps à double cône de serrage (45.1) et le deuxième corps à double cône de serrage (45.2) sont verrouillés ensemble dans la première position de verrouillage (46.1) et sont bloqués de manière autobloquante en formant le blocage, est fermé par rapport au premier canal d'évacuation d'agent de pression ou au canal d'évacuation d'agent de pression commun (83) par l'intermédiaire des premières et troisièmes surfaces coniques de verrouillage (48.1, 48.3) appliquées les unes contre les autres et qui, lorsque le premier corps à double cône de serrage (45.1) et le deuxième corps à double cône de serrage (45.2) sont décollés l'un de l'autre dans une ou la position de déverrouillage (92), est en liaison fluidique avec le premier canal d'évacuation d'agent de pression ou le canal d'évacuation d'agent de pression commun (83) par un premier canal (84.1) alors formé entre les premières et troisièmes surfaces coniques de verrouillage (48.1, 48.3), et
    que le deuxième canal d'amenée d'agent de pression fluide (54.2), lorsque le premier corps à double cône de serrage (45.1) et le deuxième corps à double cône de serrage (45.2) sont verrouillés ensemble dans la deuxième position de verrouillage (46.2) et sont bloqués de manière autobloquante en formant le blocage, est fermé par rapport au premier canal d'évacuation d'agent de pression ou au canal d'évacuation d'agent de pression commun (83) par l'intermédiaire des deuxièmes et quatrièmes surfaces coniques de verrouillage (48.2, 48.4) appliquées les unes contre les autres et qui, lorsque le premier corps à double cône de serrage (45.1) et le deuxième corps à double cône de serrage (45.2) sont décollés l'un de l'autre dans une ou la position de déverrouillage (92), est en liaison fluidique avec le deuxième canal d'évacuation d'agent de pression ou le canal d'évacuation d'agent de pression commun 83 par un deuxième canal (84.2) alors formé entre les deuxièmes et quatrièmes surfaces coniques de verrouillage (48.2, 48.4).
  9. Procédé de fonctionnement d'un vérin de verrouillage (20) à double action, actionné par un agent de pression, en particulier selon l'une des revendications précédentes, qui comprend un cylindre (21) s'étendant dans la direction d'un axe longitudinal de cylindre (26) et un piston (22) qui présente un premier côté de piston (27.1) associé à une première chambre de travail (31.1) et un deuxième côté de piston (27.2) opposé à celui-ci, associé à une deuxième chambre de travail (31.2), et qui, à l'aide d'un agent de pression fluide pouvant être amené au premier côté de piston (27.1) par un premier canal de travail (29.1) débouchant dans la première chambre de travail (31.1) et au deuxième côté de piston (27.2) par un deuxième canal de travail (29.2) débouchant dans la deuxième chambre de travail (31.2), peut être déplacé par rapport au cylindre (21) dans une direction axiale (23) parallèle à l'axe longitudinal de cylindre (26) dans un deuxième sens (28.2) et dans un premier sens (28.1) opposé au deuxième sens (28.2), mais est cependant relié solidaire en rotation au cylindre (21),
    dans lequel le piston (22) est relié solidaire en rotation à un premier corps fileté (35.1), par exemple un écrou ou une broche, dont le premier filetage (36.1), par exemple un filetage d'écrou ou un filetage de broche, est en prise avec un deuxième filetage (36.2), par exemple un filetage d'écrou ou un filetage de broche, d'un deuxième corps fileté (35.2), par exemple un écrou ou une broche, verrouillable automatiquement par friction et par la force de gravité, en formant un filetage (37) non autobloquant,
    et dans lequel le deuxième corps fileté (35.2) peut tourner par rapport au cylindre (21) autour d'un axe de rotation (43) s'étendant parallèlement à l'axe longitudinal de cylindre (26) du cylindre (21) et coulisser axialement dans la direction axiale (23) par rapport au cylindre (21),
    et dans lequel un premier corps à double cône de serrage (45.1) relié solidaire en rotation au deuxième corps fileté (35.2) est prévu, qui présente un premier corps à cône de serrage (47.1) présentant de premières surfaces coniques de verrouillage (48.1) et un deuxième corps à cône de serrage (47.2) présentant de deuxièmes surfaces coniques de verrouillage (48.2),
    et dans lequel un deuxième corps à double cône de serrage (45.2) relié solidaire en rotation au cylindre (21) est prévu, qui présente un troisième corps à cône de serrage (47.3) présentant de troisièmes surfaces coniques de verrouillage (48.3) et un quatrième corps à cône de serrage (47.4) présentant de quatrièmes surfaces coniques de verrouillage (48.4),
    et dans lequel les premières surfaces coniques de verrouillage (48.1) du premier corps à double cône de serrage (45.1) peuvent être appliquées par un déplacement axial du deuxième corps fileté (35.2) dans le premier sens (28.1) contre les troisièmes surfaces coniques de verrouillage (48.3) du deuxième corps à double cône de serrage (45.2) de telle sorte qu'à l'état appliqué le deuxième corps à double cône de serrage (45.2) peut absorber les forces axiales qui agissent dans le premier sens (28.1) sur le deuxième corps fileté (35.2) et les premières surfaces coniques de verrouillage (48.1) et les troisièmes surfaces coniques de verrouillage (48.3), en formant entre elles un blocage dans une première position de verrouillage (46.1), sont bloquées de manière autobloquante aussi bien contre une rotation autour de l'axe de rotation (43) du deuxième corps fileté (35.2) que contre un déplacement les éloignant les unes des autres dans la direction axiale (23),
    et dans lequel les deuxièmes surfaces coniques de verrouillage (48.2) du premier corps à double cône de serrage (45.1) peuvent être appliquées par un déplacement axial du deuxième corps fileté (35.2) dans le deuxième sens (28.2) contre les quatrièmes surfaces coniques de verrouillage (48.4) du deuxième corps à double cône de serrage (45.2) de telle sorte qu'à l'état appliqué le deuxième corps à double cône de serrage (45.2) peut absorber les forces axiales qui agissent dans le deuxième sens (28.2) sur le deuxième corps fileté (35.2) et les deuxièmes surfaces coniques de verrouillage (48.2) et les quatrièmes surfaces coniques de verrouillage (48.4), en formant entre elles un blocage dans une deuxième position de verrouillage (46.2), sont bloquées de manière autobloquante aussi bien contre une rotation autour de l'axe de rotation (43) du deuxième corps fileté (35.2) que contre un déplacement les éloignant les unes des autres dans la direction axiale (23),
    de sorte que le vérin de verrouillage (20) peut être verrouillé aussi bien en traction dans la première position de verrouillage (46.1) qu'en pression dans la deuxième position de verrouillage (46.2) et, à l'état appliqué, est verrouillé dans la position de verrouillage respective (46.1, 46.2) de telle sorte que le premier corps à double cône de serrage (45.1) ne peut être transféré dans une position de déverrouillage (92), dans laquelle le deuxième corps fileté (35.2) peut tourner par rapport au cylindre (21) autour de son axe de rotation (43), qu'en exerçant des forces de desserrage libérant le blocage avec le deuxième corps à double cône de serrage (45.2),
    et dans lequel le deuxième corps fileté (35.2) est monté sur au moins deux paliers lisses axiaux fluides (53.1, 53.2), dont un premier palier lisse axial fluide (53.1) est conçu pour absorber les forces axiales agissant dans le premier sens (28.1) sur le deuxième corps fileté (35.2) et dont un deuxième palier lisse axial fluide (53.2) est conçu pour absorber les forces axiales agissant dans le deuxième sens (28.2) sur le deuxième corps fileté (35.2),
    et dans lequel le premier palier lisse axial fluide (53.1) peut être soumis au ou à un agent de pression fluide par un premier canal d'amenée d'agent de pression fluide (54.1),
    et dans lequel le deuxième palier lisse axial fluide (53.2) peut être soumis au ou à un agent de pression fluide par un deuxième canal d'amenée d'agent de pression fluide (54.2),
    et dans lequel un diviseur de débit (60 ; 60.1, 60.2) comprenant un canal d'amenée principal d'agent de pression et n'agissant que dans un sens d'écoulement pour diviser un débit volumique principal d'agent de pression fluide pouvant être amené au canal d'amenée principal d'agent de pression en un premier débit volumique partiel et en un deuxième débit volumique partiel est prévu, qui comprend un premier canal de sortie d'agent de pression (61.1) pour le premier débit volumique partiel débouchant dans le premier canal d'amenée d'agent de pression fluide (54.1) pour le premier palier lisse axial fluide (53.1) et un deuxième canal de sortie d'agent de pression (61.2) pour le deuxième débit volumique partiel débouchant dans le deuxième canal d'amenée d'agent de pression fluide (54.2) pour le deuxième palier lisse axial fluide (53.2),
    et dans lequel, à l'aide du diviseur de débit (60 ; 60.1, 60.2), au moins pendant un déplacement du piston (22) dans le premier sens (28.1) et aussi pendant un déplacement du piston (22) dans le deuxième sens (28.2) et une rotation ainsi produite à chaque fois du deuxième corps fileté 35.2 autour de son axe de rotation (43) conjointement avec le premier corps à double cône de serrage (45.1), un débit volumique principal d'agent de pression fluide est divisé en un premier débit volumique partiel et en un deuxième débit volumique partiel de telle sorte qu'un rapport du premier débit volumique partiel d'agent de pression fluide amené au premier palier lisse axial fluide (53.1) à travers le premier canal d'amenée d'agent de pression fluide (54.1) et du deuxième débit volumique partiel d'agent de pression fluide amené au deuxième palier lisse axial fluide (53.2) à travers le deuxième canal d'amenée d'agent de pression fluide (54.2) reste sensiblement constant, de sorte que le premier corps à double cône de serrage (45.1) aussi bien par l'intermédiaire du premier palier lisse axial fluide (53.1) soumis à l'agent de pression fluide que par l'intermédiaire du deuxième palier lisse axial fluide (53.2) soumis à l'agent de pression fluide est et/ou reste supporté par fluide dans une position flottante fluido-dynamique (63).
  10. Procédé selon la revendication 9,
    caractérisé en ce
    que le rapport, au moins pendant un déplacement du piston (22) aussi bien dans le premier sens (28.1) que dans le deuxième sens (28.2), reste ou est maintenu sensiblement constant indépendamment des pressions de l'agent de pression fluide agissant dans le premier canal d'amenée d'agent de pression fluide (54.1) et dans le deuxième canal d'amenée d'agent de pression fluide (54.2).
  11. Procédé selon la revendication 9 ou 10,
    caractérisé en ce
    que le rapport est sensiblement de 1:1.
  12. Procédé selon l'une des revendications 9 à 11,
    caractérisé en ce
    que le diviseur de débit (60 ; 60.1) comprend un boîtier (64) avec un logement de piston de réglage (65) dans lequel un piston de réglage (66), guidé avec un faible jeu, est monté coulissant dans une direction axiale (67) par rapport au logement de piston de réglage (65),
    et dans lequel le piston de réglage (66) s'étend axialement dans la direction d'un axe longitudinal de piston de réglage (68), présente une longueur de piston de réglage ainsi qu'une première extrémité de piston de réglage (70.1) et une deuxième extrémité de piston de réglage (70.2) s'étendant à l'écart de celle-ci dans un sens opposé dans la direction axiale (67), qui présente par rapport à la première extrémité de piston de réglage (70.1) une distance correspondant à la longueur de piston de réglage,
    et dans lequel un premier canal d'amenée (62.1) pour un premier débit volumique partiel d'agent de pression fluide contenant un premier étranglement (71.1) et un deuxième canal d'amenée (62.2) pour un deuxième débit volumique partiel d'agent de pression fluide contenant un deuxième étranglement (71.2) sont disposés dans le boîtier (64),
    et dans lequel le logement de piston de réglage (65) se prolonge par une première extrémité en un premier logement d'extrémité de piston de réglage (74.1) pour recevoir la première extrémité de piston de réglage (70.1) du piston de réglage (66), dans lequel débouche le premier canal d'amenée (62.1), et dans lequel le logement de piston de réglage (65) se prolonge par une deuxième extrémité en un deuxième logement d'extrémité de piston de réglage (74.2) pour recevoir la deuxième extrémité de piston de réglage (70.2) du piston de réglage (66), dans lequel débouche le deuxième canal d'amenée (62.2),
    et dans lequel le premier logement d'extrémité de piston de réglage (74.1) forme un premier étranglement de réglage ou une partie d'un premier étranglement de réglage (75.1) et le deuxième logement d'extrémité de piston de réglage (74.2) forme un deuxième étranglement de réglage ou une partie d'un deuxième étranglement de réglage (75.2),
    de sorte que le piston de réglage (66), lorsqu'une première pression d'agent de pression, qui se forme dans le premier canal de sortie d'agent de pression (61.1) pendant que le premier canal de sortie d'agent de pression (61.1) est traversé par le premier débit volumique partiel d'agent de pression fluide, et une deuxième pression d'agent de pression, qui se forme dans le deuxième canal de sortie d'agent de pression (61.2) pendant que le deuxième canal de sortie d'agent de pression (61.2) est traversé par le deuxième débit volumique partiel d'agent de pression fluide, sont identiques, se trouve dans une position de base ou médiane (72) et que le piston de réglage (66), lorsqu'une première pression d'agent de pression, qui se forme dans le premier canal de sortie d'agent de pression (61.1) pendant que le premier canal de sortie d'agent de pression (61.1) est traversé par un premier débit volumique partiel d'agent de pression fluide, diffère d'une deuxième pression d'agent de pression, qui se forme dans le deuxième canal de sortie d'agent de pression (61.2) pendant que le deuxième canal de sortie d'agent de pression (61.2) est traversé par un deuxième débit volumique partiel d'agent de pression fluide, de sorte que la première pression d'agent de pression et la deuxième pression d'agent de pression diffèrent entre elles d'une différence de pression non nulle, se déplace, simultanément à la formation de la différence de pression, dans la direction axiale (67) dans le sens de la pression d'agent de pression plus basse dans une position différente de la position de base ou médiane (72).
  13. Procédé selon la revendication 12,
    caractérisé en ce
    que lorsque le premier corps à double cône de serrage (45.1) est bloqué de manière autobloquante avec le deuxième corps à double cône de serrage (45.2) dans la première position de verrouillage (46.1) et lorsque l'agent de pression fluide est amené au premier canal d'amenée (62.1), le piston de réglage (66) est déplacé de sa position de base ou médiane (72) dans une deuxième position de fermeture (78.2) ou est maintenu dans une deuxième position de fermeture (78.2) dans laquelle le deuxième canal de sortie d'agent de pression (61.2) et le deuxième canal d'amenée d'agent de pression fluide (54.2) sont fermés par rapport au deuxième canal d'amenée (62.2) contre une amenée de l'agent de pression, tandis qu'un premier chemin d'écoulement entre un premier canal d'amenée (62.1) et le premier canal de sortie d'agent de pression (61.1) est ouvert, de sorte que l'agent de pression fluide
    soit
    peut s'écouler, pour transférer le premier corps à double cône de serrage (45.1) dans une position de déverrouillage (92) par une amenée continue d'agent de pression fluide,
    soit
    s'écoule, de sorte que le premier corps à double cône de serrage (45.1) est transféré dans une position de déverrouillage (92),
    à travers le premier canal d'amenée (62.1) dans le premier canal de sortie d'agent de pression (61.1) et de là à travers le premier canal d'amenée d'agent de pression fluide (54.1)
    et
    que lorsque le premier corps à double cône de serrage (45.1) est bloqué de manière autobloquante avec le deuxième corps à double cône de serrage (45.2) dans la deuxième position de verrouillage (46.2) et lorsque l'agent de pression fluide est amené au deuxième canal d'amenée (62.2), le piston de réglage (66) est déplacé de sa position de base ou médiane (72) dans une première position de fermeture ou est maintenu dans une première position de fermeture dans laquelle le premier canal de sortie d'agent de pression (61.1) et le premier canal d'amenée d'agent de pression fluide (54.1) sont fermés contre une amenée d'agent de pression, tandis qu'un deuxième chemin d'écoulement entre le deuxième canal d'amenée (62.2) et le deuxième canal de sortie d'agent de pression (61.2) est ouvert, de sorte que l'agent de pression fluide
    soit
    peut s'écouler, pour transférer le premier corps à double cône de serrage (45.1) dans une position de déverrouillage (92) par une amenée continue d'agent de pression fluide,
    soit
    s'écoule, de sorte que le premier corps à double cône de serrage (45.1) est transféré dans une position de déverrouillage (92),
    à travers le deuxième canal d'amenée (62.2) dans le deuxième canal de sortie d'agent de pression (61.2) et de là à travers le deuxième canal d'amenée d'agent de pression fluide 54.2.
  14. Procédé selon l'une des revendications 9 à 11,
    caractérisé en ce
    que le diviseur de débit (60 ; 60.1) est un diviseur de débit à engrenages (60.1) qui comprend au moins une première pompe à engrenages (80.1) transportant le premier débit volumique partiel et une deuxième pompe à engrenages (80.1) transportant le deuxième débit volumique partiel, qui sont accouplées par un arbre ou par l'arbre (81) de telle sorte qu'au moins pendant le déplacement du piston (22) dans le premier sens (28.1) et aussi dans le deuxième sens (28.2) et une rotation ainsi produite à chaque fois du deuxième corps fileté (35.2) autour de son axe de rotation (43) conjointement avec le premier corps à double cône de serrage (45.1), ledit rapport du premier débit volumique partiel d'agent de pression fluide et du deuxième débit volumique partiel d'agent de pression fluide reste sensiblement constant.
  15. Procédé selon l'une des revendications 9 à 14,
    caractérisé en ce que
    soit
    à partir de la première position de verrouillage (46.1) dans laquelle le premier corps à double cône de serrage (45.1) et le deuxième corps à double cône de serrage (45.2) sont bloqués de manière autobloquante,
    d'abord
    au moins ou seulement le premier palier lisse axial fluide (53.1) est soumis à l'agent de pression fluide par le diviseur de débit (60 ; 60.1, 60.2) et le premier canal d'amenée d'agent de pression fluide (54.1) en liaison fluidique avec lui ou à partir de la deuxième position de verrouillage (46.2) dans laquelle le premier corps à double cône de serrage (45.1) et le deuxième corps à double cône de serrage 45.2 sont bloqués de manière autobloquante,
    d'abord
    au moins ou seulement le deuxième palier lisse axial fluide (53.2) est soumis à l'agent de pression fluide par le diviseur de débit (60 ; 60.1, 60.2) et le deuxième canal d'amenée d'agent de pression fluide (54.2) en liaison fluidique avec lui,
    soit
    pour produire un décollement du premier corps à double cône de serrage (45.1) du deuxième corps à double cône de serrage (45.2) dans une position de décollement et de déverrouillage (92),
    soit
    moyennant quoi un décollement du premier corps à double cône de serrage (45.1) du deuxième corps à double cône de serrage (45.2) dans une position de décollement et de déverrouillage (92) est produit,
    dans laquelle le premier corps à double cône de serrage (45.1) et le deuxième corps à double cône de serrage (45.2)
    soit
    sont au moins partiellement décollés l'un de l'autre de sorte que leurs surfaces coniques de verrouillage (48.1, 48.2 ; 48.3, 48.4) ne se touchent plus au moins partiellement,
    soit
    sont complètement décollés l'un de l'autre de sorte que leur surfaces coniques de verrouillage (48.1, 48.2 ; 48.3, 48.4) ne se touchent plus,
    et que seulement ensuite
    l'agent de pression est amené à la première ou la deuxième chambre de travail (31.1, 31.2),
    soit
    pour permettre, soutenir et/ou produire un déplacement du piston (22) dans la direction axiale (23),
    soit
    moyennant quoi le piston (22) est déplacé dans la direction axiale (23).
EP16167012.0A 2015-06-03 2016-04-26 Cylindre de verrouillage a double action et son procede de fonctionnement Active EP3101283B1 (fr)

Priority Applications (1)

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PL16167012T PL3101283T3 (pl) 2015-06-03 2016-04-26 Siłownik blokujący dwustronnego działania i sposób działania siłownika blokującego dwustronnego działania

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DE102015108829.0A DE102015108829A1 (de) 2015-06-03 2015-06-03 Doppeltwirkender Verriegelungszylinder und Verfahren zum Betreiben eines doppeltwirkenden Verriegelungszylinders

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CN116398498B (zh) * 2023-03-20 2024-05-14 浙江路帆智能装备科技有限公司 高负载缸内自锁液压油缸
CN117359141B (zh) * 2023-10-27 2024-05-10 江苏铭利达科技有限公司 一种连续举升上下料的自动机器人焊接工作站
CN117207237B (zh) * 2023-11-09 2024-02-02 之江实验室 关节***及机器人

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DE3629677A1 (de) * 1986-09-01 1988-03-10 Kontec Gmbh Vorrichung zur verriegelung des kolbens einer kolben-zylinderanordnung
DE19633412A1 (de) * 1996-08-19 1998-03-05 Wolfram Sielemann Druckmittelbetriebener Antrieb
DE202006019452U1 (de) * 2006-12-23 2007-03-29 Bümach Engineering International B.V. Druckmittelbetriebene Hubvorrichtung mit selbsthemmender Gewindespindel
EP2570679B1 (fr) 2009-04-09 2013-09-18 Neumeister Hydraulik GmbH Vérin de verrouillage et procédés de verrouillage et de déverrouillage correspondants

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PL3101283T3 (pl) 2018-07-31
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EP3101283A1 (fr) 2016-12-07
LT3101283T (lt) 2018-05-25

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