EP3101283A1 - 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
EP3101283A1
EP3101283A1 EP16167012.0A EP16167012A EP3101283A1 EP 3101283 A1 EP3101283 A1 EP 3101283A1 EP 16167012 A EP16167012 A EP 16167012A EP 3101283 A1 EP3101283 A1 EP 3101283A1
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EP
European Patent Office
Prior art keywords
pressure medium
fluid
locking
channel
cone body
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP16167012.0A
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German (de)
English (en)
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EP3101283B1 (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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Publication of EP3101283B1 publication Critical patent/EP3101283B1/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

  • 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 ,
  • 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,
  • 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 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.
  • 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.
  • 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 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.
  • 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 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 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 in fluid communication with 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 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 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 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.
  • 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 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.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Jigs For Machine Tools (AREA)
  • Actuator (AREA)
  • Fluid-Pressure Circuits (AREA)
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)

Application Number Priority Date Filing Date Title
PL16167012T PL3101283T3 (pl) 2015-06-03 2016-04-26 Siłownik blokujący dwustronnego działania i sposób działania siłownika blokującego dwustronnego działania

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102015108829.0A DE102015108829A1 (de) 2015-06-03 2015-06-03 Doppeltwirkender Verriegelungszylinder und Verfahren zum Betreiben eines doppeltwirkenden Verriegelungszylinders

Publications (2)

Publication Number Publication Date
EP3101283A1 true EP3101283A1 (fr) 2016-12-07
EP3101283B1 EP3101283B1 (fr) 2018-02-28

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EP (1) EP3101283B1 (fr)
DE (1) DE102015108829A1 (fr)
ES (1) ES2664856T3 (fr)
LT (1) LT3101283T (fr)
PL (1) PL3101283T3 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115194942A (zh) * 2022-07-29 2022-10-18 江苏成创工程机械有限公司 一种混凝土外加剂制备及试验设备
CN116398498A (zh) * 2023-03-20 2023-07-07 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
CN117207237A (zh) * 2023-11-09 2023-12-12 之江实验室 关节***及机器人
CN117359141A (zh) * 2023-10-27 2024-01-09 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

Citations (4)

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Publication number Priority date Publication date Assignee Title
DE3629677A1 (de) * 1986-09-01 1988-03-10 Kontec Gmbh Vorrichung zur verriegelung des kolbens einer kolben-zylinderanordnung
DE29714664U1 (de) * 1996-08-19 1998-03-05 Sielemann, Wolfram, 33649 Bielefeld Druckmittelbetriebener Antrieb
DE202006019452U1 (de) * 2006-12-23 2007-03-29 Bümach Engineering International B.V. Druckmittelbetriebene Hubvorrichtung mit selbsthemmender Gewindespindel
EP2239470A2 (fr) 2009-04-09 2010-10-13 Neumeister Hydraulik GmbH Vérin de verrouillage et procédé de verrouillage et de déverrouillage d'un vérin de verrouillage

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3629677A1 (de) * 1986-09-01 1988-03-10 Kontec Gmbh Vorrichung zur verriegelung des kolbens einer kolben-zylinderanordnung
DE29714664U1 (de) * 1996-08-19 1998-03-05 Sielemann, Wolfram, 33649 Bielefeld Druckmittelbetriebener Antrieb
DE202006019452U1 (de) * 2006-12-23 2007-03-29 Bümach Engineering International B.V. Druckmittelbetriebene Hubvorrichtung mit selbsthemmender Gewindespindel
EP2239470A2 (fr) 2009-04-09 2010-10-13 Neumeister Hydraulik GmbH Vérin de verrouillage et procédé de verrouillage et de déverrouillage d'un vérin de verrouillage
DE102010015996A1 (de) 2009-04-09 2010-10-14 Neumeister Hydraulik Gmbh Verriegelungszylinder und Verfahren zur Verriegelung und Entriegelung eines Verriegelungszylinders
EP2570679A1 (fr) 2009-04-09 2013-03-20 Neumeister Hydraulik GmbH Vérin de verrouillage et procédés de verrouillage et de déverrouillage correspondants
EP2570680A1 (fr) 2009-04-09 2013-03-20 Neumeister Hydraulik GmbH Procédé de déverrouillage d'un cylindre de verrouillage

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115194942A (zh) * 2022-07-29 2022-10-18 江苏成创工程机械有限公司 一种混凝土外加剂制备及试验设备
CN116398498A (zh) * 2023-03-20 2023-07-07 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
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
CN117359141A (zh) * 2023-10-27 2024-01-09 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
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
CN117207237A (zh) * 2023-11-09 2023-12-12 之江实验室 关节***及机器人
CN117207237B (zh) * 2023-11-09 2024-02-02 之江实验室 关节***及机器人

Also Published As

Publication number Publication date
LT3101283T (lt) 2018-05-25
EP3101283B1 (fr) 2018-02-28
DE102015108829A1 (de) 2016-12-08
ES2664856T3 (es) 2018-04-23
PL3101283T3 (pl) 2018-07-31

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